EP0699292A1 - Heat exchanger - Google Patents

Heat exchanger

Info

Publication number
EP0699292A1
EP0699292A1 EP94911228A EP94911228A EP0699292A1 EP 0699292 A1 EP0699292 A1 EP 0699292A1 EP 94911228 A EP94911228 A EP 94911228A EP 94911228 A EP94911228 A EP 94911228A EP 0699292 A1 EP0699292 A1 EP 0699292A1
Authority
EP
European Patent Office
Prior art keywords
plates
plate
heat exchanger
dimples
stack
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94911228A
Other languages
German (de)
French (fr)
Other versions
EP0699292B1 (en
Inventor
John Edwin 5 Blyth Way Bowman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bowman Ej (birmingham) Ltd
Original Assignee
Bowman Ej (birmingham) Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GB939311198A external-priority patent/GB9311198D0/en
Application filed by Bowman Ej (birmingham) Ltd filed Critical Bowman Ej (birmingham) Ltd
Publication of EP0699292A1 publication Critical patent/EP0699292A1/en
Application granted granted Critical
Publication of EP0699292B1 publication Critical patent/EP0699292B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00Making other particular articles
    • B21D53/02Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/04Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of sheet metal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00Reinforcing means
    • F28F2225/02Reinforcing means for casings

Definitions

  • This invention relates to heat exchangers of the kind comprising a stack of plates which are in sealed engagement one with another to provide spaces between the plates for the flow of two separate fluid streams which are to undergo heat exchange.
  • a known arrangement in widespread use has each plate provided with four ports, one at each corner of a rectangular shape. Two ports are used as inlets for the respective fluids and the other two are as outlets for the same. Each fluid divides into a plurality of streams equal in number to half of the total interplate spaces and each part of the stream flows individually through a different one of the interplate spaces on its way from the one inlet port to the corresponding outlet port. Such an arrangement may be considered as involving parallel streams flow.
  • the heat exchanger of the mentioned prior patent is assembled by making the upwardly extending part of different diameter to the downwardly extending one, telescoping each two connected parts and flaring the smaller one outwardly. This is to fix the parts together both axially and angularly.
  • the assembly is built one plate at a time and a flaring operation to complete the joint is necessary before adding another plate, and so on; moreover (after the first operation) only one end of the part to be flared is available for access by a forming tool, which may dictate the use of ductile material and even then places technical limitations on the design.
  • the object of the present invention is to provide an improved heat exchanger of this kind.
  • the plates polygonal with equal angles and equal sides. This ensures perfect angular alignment between one stub tube and the next without needing to secure them together by means of a flaring operation. This also enables the stub tubes to make end-to- end contact if desired being later sealingly connected together by furnace brazing; although in order to have faces in contact rather than edges, it is preferred that the one is of a smaller diameter than the other so that they are telescoped together.
  • the location of the stub tubes depends upon the shape of the plates and is such that when one plate is turned relative to the next so that the edges still coincide, then one e.g. upwardly extending stub tube of one plate is aligned with the downwardly extending tube of the next plate and so on.
  • the polygon is a square.
  • the individual plates have a continuous peripheral flange which is substantially but not quite normal to the plane of the plate and the angle of the flange has some effect on the degree of nesting of one plate within the next.
  • the flange has an outward extension and a downward terminal portion: or it is outwardly rolled. The significance of this is explained hereinafter.
  • the plates have dimples formed on their faces extending in opposite directions and arranged so that in the required angular relationship, the upwardly extending dimples of one plate are aligned with the downwardly extending dimples of the next plate.
  • the assembly may be made, and then the stack of plates compressed to take the dimples into face to face contact thus controlling the extent of the axial compression and ensuring that the flanges are in tight contact one with another along the lengths of the respective flanges, prior to furnace brazing or another sealing operation.
  • the telescoping connection of the stub tubes may be particularly convenient to permit this.
  • the dimples may be conical or hemi-spherical , but truncated cones are preferred.
  • the plates except the end plates are identical to one another and the number of plates (including those end plates) is equal to xn + 1 where x is equal to the sides of the polygon and n is any desired whole number.
  • xn + 1 where x is equal to the sides of the polygon and n is any desired whole number.
  • the heat exchanger of the invention can be inserted into a pair of parallel pipes carrying the heat exchange fluid pair merely by cutting and connecting the ends of the respective parts without needing any additional pipework.
  • a three-plate, two-space heat exchanger will be useful for some purposes, and this will not have co-axial inlets and outlets.
  • each of the end plates is reinforced by a thicker planar cap plate, and the adjacent end plate is identical to the intermediate plates except that it has dimples only on the face adjacent the next intermediate plate and not on the face adjacent the cap plate. The significance of this is described later herein.
  • Figure 1 is an underneath plan view of an intermediate plate
  • Figure 2 is a side elevation of the same
  • Figure 3 is a section on the line A-A of Figure 1;
  • Figure 4 is an exploded diagrammatic perspective view of a heat exchanger including the plates of Figures 1-3 to show the angular relationship;
  • Figure 5 is a section through part of the length of a heat exchanger on the line B-B of Figures 1, 6 and 7;
  • Figure 6 is a view similar to Figure 1 showing one end plate
  • Figure 7 is a view similar to Figure 1 showing the other end plate.
  • Figure 8 is a fragmentary sectional view showing a modification.
  • FIG. 1 a square intermediate plate 10 is shown in Figure 1 therein having, in this case, nineteen rows of dimple-like projections arranged with projections extending to one or other of the opposite faces of the plate.
  • the dimples are pitched apart at equal intervals in regular pattern, and the rows of dimples are staggered at half pitch intervals.
  • the plate is provided with a pair of apertures 50,52 symmetrically related to a perpendicular bisecting the length dimension and at a like spacing from a second perpendicular at right angles to the first and bisecting the transverse dimension.
  • Two areas of the plate have dimples which are all upwardly directed (the area around point 6) or downwardly directed (around point 8) and these are arranged according to the direction through which the plates are turned in making the assembly, so that dimples are directed away from a port 50, 52 aligned therewith.
  • one of the projections is in the form of a stub tube or collar 54 projecting in one direction and the second 56 in the opposite direction.
  • the stub tubes are designed so that they can be sealably joined to the next, for example by furnace brazing and for this purpose the stub tubes may be telescopically engaged, or abutted end-to-end as mentioned.
  • non-circular plates are particularly convenient since the edges of the plates hold the tubes in exact angular alignment with no risk of the stub tubes becoming non-coaxial which would at least open up gaps preventing their sealing by furnace brazing and which could make the heat exchanger useless by allowing mixing of the fluids involved in heat exchange if such a heat exchanger were put into use.
  • Each plate has an upstanding peripheral edge 30 which is slightly inclined so that the next plate may be partially nested.
  • Figure 4 The arrangement of these intermediate plates according to Figure 1 in a typical heat exchanger is shown in Figure 4.
  • the number of spaces will always be a multiple of 4, and the number of plates will be a like multiple plus 1 so as to provide e.g. 5, 9, 13 ... plates.
  • Figure 4 shows five plates, and hence four inter-plate spaces.
  • the stack of plates includes both intermediate plates and two end plates 70,72.
  • Plate 70 is shown in Figure 6. This plate as illustrated has dimples 42 extending only in a downward direction as seen in Figure 4, and these dimples are located in exactly the same positions as the downwardly directed dimples in Figure 1, when the plate is in the same angular position as in Figure 1.
  • plate 72 has dimples 42 extending only in a upwards direction but located in exactly the same positions as the upward dimples in Figure 1 subject to the same angular position.
  • These plates are simple to manufacture since one and the same set of pressing tools can be used to make all of the intermediate plates and all the end plates.
  • the forming dies, upper and lower ones respectively, are provided with inserted pins to form the dimples, and the pins are simply omitted where dimples are not required and included where they are required.
  • the arrangement of dimple-like projections in each row is such that the face 40 of each dimple 42 contacts the similar face of the aligned dimple on the next plate 10, 70, or 72 as the case may be so as to assist in controlling the spacing of the plates when the latter are subject to compression in assembly prior to brazing or otherwise joining together, and the dimples are intended to become brazed together to provide great structural strength.
  • the effect of the dimples is also to provide a plurality of flow paths across the plates leading to turbulence and mixing, and provide additional surface for heat exchange from fluid to plate and plate to fluid.
  • the brazing essentially joins the edges of the plates together and the stub tubes together and desirably the dimples together.
  • reinforcement cap plates 20 which are relatively thick and solid plates, apertured to allow connection tubes 14, 16 to be added the assembly and located immediately next to the end plates 70, 72.
  • the cap plates are substantially identical to one another and are dimensioned to fit within the peripheral edge 30.
  • the absence of dimples projecting towards the cap plate from the adjacent end plates 70, 72 enables the cap to become brazed in face- to-face contact over substantially its entire area with the adjacent end plate. This contributes greatly to the pressure capability of the complete heat exchanger.
  • Figure 5 shows a fragmentary section through a nine plate assembly according to the invention, this comprising seven intermediate plates 10 1 , 10 , 10 ...10 .
  • the sectional drawing is made through three of the downwardly directed dimples in one row of plate 10 1 ( Figure 1) on the lefthand side of Figure 5, and then through three upwardly directed dimples in the adjacent row, on the righthand side of Figure 5.
  • This illustrates the alternating dimension axially of the stack of the inter-plate spaces which improves flow therein, reduces film effects and thus improves heat exchange.
  • one fluid of the heat exchange pair flows through spaces 90, 92, 94, 96 in series (or in the reverse order), whilst the other flows through spaces 98, 100, 102, 104 in series (or in the reverse order).
  • the assembly is made by arranging the plates in a stack with each turned 90°, always in the same direction, relative to the next plate.
  • the arrangement of the dimples is such that each downwardly directed dimple then becomes aligned with an upwardly directed dimple (and vice versa).
  • the dimples With the end plates 70, 72 the dimples are directed inwardly of the stack and essentially planar faces are disposed towards the reinforcing cap plates.
  • a modification in Figure 8 also contributes to the pressure capability.
  • the edge 30 is rolled at 80.
  • the rolling can be through less than 180° or more than 180°.
  • the equivalent can be formed by a series of angularly related planar portions namely an outwardly projecting flange and then at least a downwardly projecting flange. The result is to stiffen each plate and there may also be some advantage in providing a natural groove between each two plates when assembled together, extending about their periphery, which will accommodate a fillet of the brazing material used in completing the assembly.
  • Short lengths of tube may be fixed to the stub tubes 50,52 which project from opposite ends of the complete assembly and may be connected by the furnace brazing or like operation which seals all of the parts of the assembly.
  • These tubes may for example be internally screw threaded so as to connect existing pipes to the heat exchanger. It will be appreciated that one of the tubes at one end is to open to the interplate space between the first pair of plates 10 and the other at the same end to the second interplate space between the second and third plates 10, and similary at the other end .
  • Figure 5 shows clearances between the parts, prior to pressure clamping and brazing or other sealing to complete the manufacturing process.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

A heat exchanger comprises a plurality of substantially similar plates 10, with a pair of ports. Each plate is turned 90 DEG in the same direction relative to the adjacent one so that the ports align to provide a pair of separate series flow paths which are interleaved between the plates. The angular alignment of the ports is controlled by the regular polygon shape of the plates. The plates are clamped together and sealed for example by furnace brazing. The ports are defined by oppositely extending stub tubes 54, 56. The plates preferably have dimples or other projections in opposite directions from both faces. Also disclosed is a method of producing substantially identical heat exchanger plates which have different patterns of projections (42, figure 1). The different patterns being obtained by locating or not locating projection forming punches in recesses in the dies used to form the plates. <IMAGE>

Description

HEAT EXCHANGER
This invention relates to heat exchangers of the kind comprising a stack of plates which are in sealed engagement one with another to provide spaces between the plates for the flow of two separate fluid streams which are to undergo heat exchange.
A known arrangement in widespread use has each plate provided with four ports, one at each corner of a rectangular shape. Two ports are used as inlets for the respective fluids and the other two are as outlets for the same. Each fluid divides into a plurality of streams equal in number to half of the total interplate spaces and each part of the stream flows individually through a different one of the interplate spaces on its way from the one inlet port to the corresponding outlet port. Such an arrangement may be considered as involving parallel streams flow.
A rather different flow pattern, which may be called serial streams flow results from use of the arrange"ment described in U.K. Patent 1430491, although as far is known to the applicants this is a paper proposal which has not been manufactured. In this, a series of identical circular plates each have two axially short stub tubes opening from the plate in opposite directions. The plates are assembled together by engaging the upwardly directed tube on the one plate to the downwardly directed tube on the next, which automatically ensures that each upwardly extending one is angularly shifted, relative to the axis of the circular plate, and two interleaved sets of spaces ensue. Fluid is led (countercurrent according to the patent) through the two sets to effect heat exchange. The first fluid flows through the odd numbered spaces and the second one through the even numbered spaces.
The heat exchanger of the mentioned prior patent is assembled by making the upwardly extending part of different diameter to the downwardly extending one, telescoping each two connected parts and flaring the smaller one outwardly. This is to fix the parts together both axially and angularly. The assembly is built one plate at a time and a flaring operation to complete the joint is necessary before adding another plate, and so on; moreover (after the first operation) only one end of the part to be flared is available for access by a forming tool, which may dictate the use of ductile material and even then places technical limitations on the design.
The object of the present invention is to provide an improved heat exchanger of this kind.
According to the invention we make the plates . polygonal with equal angles and equal sides. This ensures perfect angular alignment between one stub tube and the next without needing to secure them together by means of a flaring operation. This also enables the stub tubes to make end-to- end contact if desired being later sealingly connected together by furnace brazing; although in order to have faces in contact rather than edges, it is preferred that the one is of a smaller diameter than the other so that they are telescoped together.
The location of the stub tubes depends upon the shape of the plates and is such that when one plate is turned relative to the next so that the edges still coincide, then one e.g. upwardly extending stub tube of one plate is aligned with the downwardly extending tube of the next plate and so on.
Conveniently and preferably the polygon is a square.
Preferably the individual plates have a continuous peripheral flange which is substantially but not quite normal to the plane of the plate and the angle of the flange has some effect on the degree of nesting of one plate within the next.
According to an important, albeit optional feature of the invention, the flange has an outward extension and a downward terminal portion: or it is outwardly rolled. The significance of this is explained hereinafter.
Preferably also the plates have dimples formed on their faces extending in opposite directions and arranged so that in the required angular relationship, the upwardly extending dimples of one plate are aligned with the downwardly extending dimples of the next plate. When these features are combined, the assembly may be made, and then the stack of plates compressed to take the dimples into face to face contact thus controlling the extent of the axial compression and ensuring that the flanges are in tight contact one with another along the lengths of the respective flanges, prior to furnace brazing or another sealing operation. The telescoping connection of the stub tubes may be particularly convenient to permit this.
The dimples may be conical or hemi-spherical , but truncated cones are preferred.
Preferably all of the plates except the end plates (i.e. all of the intermediate plates) are identical to one another and the number of plates (including those end plates) is equal to xn + 1 where x is equal to the sides of the polygon and n is any desired whole number. This brings the inlet and outlet of one series stream co¬ axial, and the inlet and outlet of the other likewise. Hence the heat exchanger of the invention can be inserted into a pair of parallel pipes carrying the heat exchange fluid pair merely by cutting and connecting the ends of the respective parts without needing any additional pipework. However, a three-plate, two-space heat exchanger will be useful for some purposes, and this will not have co-axial inlets and outlets.
According to another optional but important feature, each of the end plates is reinforced by a thicker planar cap plate, and the adjacent end plate is identical to the intermediate plates except that it has dimples only on the face adjacent the next intermediate plate and not on the face adjacent the cap plate. The significance of this is described later herein.
An embodiment of the invention is now more particularly described with reference to the accompanying drawings wherein:-
Figure 1 is an underneath plan view of an intermediate plate;
Figure 2 is a side elevation of the same;
Figure 3 is a section on the line A-A of Figure 1;
Figure 4 is an exploded diagrammatic perspective view of a heat exchanger including the plates of Figures 1-3 to show the angular relationship;
Figure 5 is a section through part of the length of a heat exchanger on the line B-B of Figures 1, 6 and 7;
Figure 6 is a view similar to Figure 1 showing one end plate;
Figure 7 is a view similar to Figure 1 showing the other end plate; and
Figure 8 is a fragmentary sectional view showing a modification.
Turning now to the drawing a square intermediate plate 10 is shown in Figure 1 therein having, in this case, nineteen rows of dimple-like projections arranged with projections extending to one or other of the opposite faces of the plate. The dimples are pitched apart at equal intervals in regular pattern, and the rows of dimples are staggered at half pitch intervals. The plate is provided with a pair of apertures 50,52 symmetrically related to a perpendicular bisecting the length dimension and at a like spacing from a second perpendicular at right angles to the first and bisecting the transverse dimension. Two areas of the plate have dimples which are all upwardly directed (the area around point 6) or downwardly directed (around point 8) and these are arranged according to the direction through which the plates are turned in making the assembly, so that dimples are directed away from a port 50, 52 aligned therewith. As seen in Figure 3, one of the projections is in the form of a stub tube or collar 54 projecting in one direction and the second 56 in the opposite direction. The stub tubes are designed so that they can be sealably joined to the next, for example by furnace brazing and for this purpose the stub tubes may be telescopically engaged, or abutted end-to-end as mentioned. The use of non-circular plates is particularly convenient since the edges of the plates hold the tubes in exact angular alignment with no risk of the stub tubes becoming non-coaxial which would at least open up gaps preventing their sealing by furnace brazing and which could make the heat exchanger useless by allowing mixing of the fluids involved in heat exchange if such a heat exchanger were put into use.
Each plate has an upstanding peripheral edge 30 which is slightly inclined so that the next plate may be partially nested.
The arrangement of these intermediate plates according to Figure 1 in a typical heat exchanger is shown in Figure 4. In order to have inlet and outlets aligned axially so that the heat exchanger can be installed in a pair of parallel pipelines the number of spaces will always be a multiple of 4, and the number of plates will be a like multiple plus 1 so as to provide e.g. 5, 9, 13 ... plates. Figure 4 shows five plates, and hence four inter-plate spaces.
It should be understood that with square plates it is not necessary to provide a number of plates which is a multiple of 4 plus 1, providing non-aligned inlet and outlet tubes can be accepted. One possibility which is particularly useful where a small number of plates is required for example has four plates providing three spaces of which the first and third will form a series connected flow path for one fluid while the second is for flow of the other fluid . In another similar arrangement, six plates may be used to provide five spaces of which the first third and fifth are serially connected for flow of a first fluid and the second and fourth for a second fluid. It will be understood by those skilled in the art that flow through any space results in a pressure drop, and the greater the thermal length (all other things being equal) the greater the pressure drop. Hence, in the first mentioned instance here, using three spaces, the fluid flowing through two of the spaces will undergo a substantially greater pressure drop than that flowing through the single space: the heat exchanger design according to the invention may be tailored to utilise these factors according to the surrounding parameters.
In any case in the preferred embodiments the stack of plates includes both intermediate plates and two end plates 70,72. Plate 70 is shown in Figure 6. This plate as illustrated has dimples 42 extending only in a downward direction as seen in Figure 4, and these dimples are located in exactly the same positions as the downwardly directed dimples in Figure 1, when the plate is in the same angular position as in Figure 1. Likewise, plate 72 has dimples 42 extending only in a upwards direction but located in exactly the same positions as the upward dimples in Figure 1 subject to the same angular position. These plates are simple to manufacture since one and the same set of pressing tools can be used to make all of the intermediate plates and all the end plates. The forming dies, upper and lower ones respectively, are provided with inserted pins to form the dimples, and the pins are simply omitted where dimples are not required and included where they are required.
The arrangement of dimple-like projections in each row is such that the face 40 of each dimple 42 contacts the similar face of the aligned dimple on the next plate 10, 70, or 72 as the case may be so as to assist in controlling the spacing of the plates when the latter are subject to compression in assembly prior to brazing or otherwise joining together, and the dimples are intended to become brazed together to provide great structural strength. However, the effect of the dimples is also to provide a plurality of flow paths across the plates leading to turbulence and mixing, and provide additional surface for heat exchange from fluid to plate and plate to fluid. The brazing essentially joins the edges of the plates together and the stub tubes together and desirably the dimples together.
In Figure 1 upward projections (convex) are shown as plain circles, and downward projections (concave) are marked with a cross, which is purely diagrammatic and for illustration only - that is to say the cross appears in the drawing but not on the dimples themselves.
The arrangement is completed with reinforcement cap plates 20 which are relatively thick and solid plates, apertured to allow connection tubes 14, 16 to be added the assembly and located immediately next to the end plates 70, 72. Again, the cap plates are substantially identical to one another and are dimensioned to fit within the peripheral edge 30. The absence of dimples projecting towards the cap plate from the adjacent end plates 70, 72 enables the cap to become brazed in face- to-face contact over substantially its entire area with the adjacent end plate. This contributes greatly to the pressure capability of the complete heat exchanger.
Figure 5 shows a fragmentary section through a nine plate assembly according to the invention, this comprising seven intermediate plates 101 , 10 , 10 ...10 . The sectional drawing is made through three of the downwardly directed dimples in one row of plate 101 (Figure 1) on the lefthand side of Figure 5, and then through three upwardly directed dimples in the adjacent row, on the righthand side of Figure 5. This illustrates the alternating dimension axially of the stack of the inter-plate spaces which improves flow therein, reduces film effects and thus improves heat exchange. In use, one fluid of the heat exchange pair flows through spaces 90, 92, 94, 96 in series (or in the reverse order), whilst the other flows through spaces 98, 100, 102, 104 in series (or in the reverse order).
The assembly is made by arranging the plates in a stack with each turned 90°, always in the same direction, relative to the next plate. The arrangement of the dimples is such that each downwardly directed dimple then becomes aligned with an upwardly directed dimple (and vice versa). With the end plates 70, 72 the dimples are directed inwardly of the stack and essentially planar faces are disposed towards the reinforcing cap plates.
A modification in Figure 8 also contributes to the pressure capability. In this modification the edge 30 is rolled at 80. The rolling can be through less than 180° or more than 180°. Alternatively, the equivalent can be formed by a series of angularly related planar portions namely an outwardly projecting flange and then at least a downwardly projecting flange. The result is to stiffen each plate and there may also be some advantage in providing a natural groove between each two plates when assembled together, extending about their periphery, which will accommodate a fillet of the brazing material used in completing the assembly.
Short lengths of tube may be fixed to the stub tubes 50,52 which project from opposite ends of the complete assembly and may be connected by the furnace brazing or like operation which seals all of the parts of the assembly. These tubes may for example be internally screw threaded so as to connect existing pipes to the heat exchanger. It will be appreciated that one of the tubes at one end is to open to the interplate space between the first pair of plates 10 and the other at the same end to the second interplate space between the second and third plates 10, and similary at the other end .
It will be understood that Figure 5 shows clearances between the parts, prior to pressure clamping and brazing or other sealing to complete the manufacturing process.

Claims

1. A series flow heat exchanger of the kind comprising a stack of substantially identical plates each with two spaced ports, each plate being angularly turned in the same direction with respect to the adjacent plate so that the first port on one plate registers with the second port on the next plate and so to provide two interleaved sets of spaces for the flow of two fluids of the heat exchange pair, the ports being defined by oppositely extending stub tubes, characterised in that the plates are regular polygons.
2. A heat exchanger as claimed in Claim 1 wherein the plates are square and have a peripheral flange which is substantially but not quite normal to the plane of a plate.
3. A heat exchanger as claimed in Claim 2 wherein the flange is outwardly rolled.
4. A heat exchanger as claimed in any preceding claim wherein the plates are dimpled and arranged so that the dimples on each plate contact dimples on the next plate(s) in the stack.
5. A heat exchanger as claimed in any preceding claim wherein intermediate plates in the stack are provided with dimples extending in both directions along the stack.
6. A heat exchanger as claimed in any preceding claim wherein each end plate in the stack is provided with dimples on one face only and adjacent the next plate in the stack.
7. A heat exchanger as claimed in any preceding claim wherein planar reinforcing cap plates are provided at ends of the stack.
8. A heat exchanger as claimed in Claim 4 alone or together with either or both of Claims 5 and 6 wherein the dimples are arranged so that ones opposite each port extend away from that port.
9. A heat exchanger as claimed in Claim 4 alone or together with any preceding claim wherein each dimple comprises a truncated conical shape.
10. A method of making a heat exchanger comprising pressing a shallow tray-like plate with a pair of ports and a regular pattern of projections extending from either one of or both generally planar faces of the tray including the step of locating individual projection forming punches in recesses in one of a pair of dies forming the pressing, or not according to whether a projection in a particular direction is desired or not, and subsequently assembling a plurality of the plates into a stack, with each plate turned at an angle relative to the adjacent plate, clamping the plates together and making sealing engagement therebetween.
EP94911228A 1993-05-29 1994-03-25 Heat exchanger Expired - Lifetime EP0699292B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
GB9311198 1993-05-29
GB939311198A GB9311198D0 (en) 1993-05-29 1993-05-29 Heat exchanger
GB9325148 1993-12-08
GB939325148A GB9325148D0 (en) 1993-05-29 1993-12-08 Heat exchanger
PCT/GB1994/000632 WO1994028367A1 (en) 1993-05-29 1994-03-25 Heat exchanger

Publications (2)

Publication Number Publication Date
EP0699292A1 true EP0699292A1 (en) 1996-03-06
EP0699292B1 EP0699292B1 (en) 1998-06-10

Family

ID=26302980

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94911228A Expired - Lifetime EP0699292B1 (en) 1993-05-29 1994-03-25 Heat exchanger

Country Status (8)

Country Link
EP (1) EP0699292B1 (en)
AT (1) ATE167284T1 (en)
AU (1) AU6379894A (en)
DE (1) DE69411007T2 (en)
DK (1) DK0699292T3 (en)
ES (1) ES2120027T3 (en)
GB (1) GB2278430B (en)
WO (1) WO1994028367A1 (en)

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CN101387480B (en) * 2008-09-05 2010-06-09 山东北辰压力容器有限公司 Round point width flow passage fully-soldering heat exchange plate

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AUPP410598A0 (en) 1998-06-15 1998-07-09 Aos Pty Ltd Heat exchangers
FR2795167B1 (en) * 1999-06-21 2001-09-14 Valeo Thermique Moteur Sa PLATE HEAT EXCHANGER, PARTICULARLY FOR COOLING AN OIL OF A MOTOR VEHICLE
US6364006B1 (en) * 1999-12-23 2002-04-02 Visteon Global Technologies, Inc. Beaded plate for a heat exchanger and method of making same
DE10153877A1 (en) * 2001-11-02 2003-05-15 Behr Gmbh & Co Heat exchanger
RU2462677C1 (en) * 2011-04-13 2012-09-27 ГОСУДАРСТВЕННОЕ ОБРАЗОВАТЕЛЬНОЕ УЧРЕЖДЕНИЕ ВЫСШЕГО ПРОФЕССИОНАЛЬНОГО ОБРАЗОВАНИЯ "Брянский государственный технический университет" Plate-type heat exchanger matrix
CN105556231B (en) * 2013-09-17 2018-08-17 舒瑞普国际股份公司 Heat-exchangers of the plate type with intensifier
FR3086377A1 (en) * 2018-09-25 2020-03-27 Valeo Systemes Thermiques PLATE CONSTITUTING A HEAT EXCHANGER AND HEAT EXCHANGER COMPRISING AT LEAST ONE SUCH PLATE

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DE3415733A1 (en) * 1984-04-27 1985-10-31 Fischbach GmbH & Co KG Verwaltungsgesellschaft, 5908 Neunkirchen METHOD FOR PRODUCING THE PLATES OF A PLATE HEAT EXCHANGER AND HEAT EXCHANGERS MADE FROM THE PLATES
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CN101387480B (en) * 2008-09-05 2010-06-09 山东北辰压力容器有限公司 Round point width flow passage fully-soldering heat exchange plate

Also Published As

Publication number Publication date
DE69411007T2 (en) 1998-10-22
GB2278430A (en) 1994-11-30
AU6379894A (en) 1994-12-20
GB2278430B (en) 1997-04-23
EP0699292B1 (en) 1998-06-10
ES2120027T3 (en) 1998-10-16
ATE167284T1 (en) 1998-06-15
WO1994028367A1 (en) 1994-12-08
DE69411007D1 (en) 1998-07-16
GB9406020D0 (en) 1994-05-11
DK0699292T3 (en) 1999-03-22

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