EP2236969A2 - Plate Heat exchanger for high exposure from thermal cycling - Google Patents

Plate Heat exchanger for high exposure from thermal cycling Download PDF

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Publication number
EP2236969A2
EP2236969A2 EP10155227A EP10155227A EP2236969A2 EP 2236969 A2 EP2236969 A2 EP 2236969A2 EP 10155227 A EP10155227 A EP 10155227A EP 10155227 A EP10155227 A EP 10155227A EP 2236969 A2 EP2236969 A2 EP 2236969A2
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EP
European Patent Office
Prior art keywords
heat exchanger
discs
fluid
end plate
exchanger according
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
EP10155227A
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German (de)
French (fr)
Other versions
EP2236969A3 (en
EP2236969B1 (en
Inventor
Christian Saumweber
Friedrich Brotz
Arthur Strehlau
Frank von Lützau
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.)
Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2236969A2 publication Critical patent/EP2236969A2/en
Publication of EP2236969A3 publication Critical patent/EP2236969A3/en
Application granted granted Critical
Publication of EP2236969B1 publication Critical patent/EP2236969B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1 and an internal combustion engine according to the preamble of claim 15.
  • Heat exchangers are used in various technical applications for the transfer of heat from one fluid to another fluid.
  • heat exchangers are used as charge air coolers to cool the air compressed by a compressor before it is fed into the internal combustion engine.
  • the charge air to be cooled and a cooling liquid are passed through the heat exchanger.
  • the cooling liquid absorbs heat from the charge air and thus cools the charge air.
  • Such heat exchangers are exposed to high thermal cycling stresses, because during operation of the motor vehicle temperature fluctuations occur and also at each start of the internal combustion engine, the heat exchanger is initially cold.
  • heat exchangers are often used in disc design. Many discs are stacked on top of each other. Due to the geometry of the discs, channels or fluid channels for the charge air and the cooling fluid form between the discs. At the stack ends, an end plate is arranged in each case. The disks and the end plates are generally bonded together by means of soldering. The thickness of the end plates is substantially greater than the thickness of the disks. Due to the thermal cycling and / or an inhomogeneous temperature distribution within the heat exchanger, stresses occur within the heat exchanger. The tensions result in particular from the greater thermal inertia of the end plates relative to the discs. The end plates have a greater thickness and thus a larger mass, so that the end plates heat much slower or cool than the discs.
  • the rigidity of the end plates parallel to a plate plane is greater than the rigidity of the plates parallel to a disc plane. This difference in stiffness between the end plates and the discs can cause damage and has a life-limiting effect on the heat exchanger.
  • the change in size of the end plate with temperature changes parallel to the plane of the plate differs from the change in size with temperature changes of the disc on the end plate parallel to the plane of the disc.
  • the object of the present invention is to provide a heat exchanger and an internal combustion engine with the heat exchanger available, which has a long life even with high thermal cycling in a structurally simple structure.
  • the heat exchanger should be inexpensive to manufacture and work reliably in operation.
  • a heat exchanger in disk construction comprising a plurality of stacked disks, at least one first fluid channel for passing a first fluid, at least one second fluid channel for passing a second fluid, wherein the at least one first and the at least one second fluid channel are at least partially formed between the discs by means of the discs due to the geometry of the discs, one end plate at two Stack ends of the discs of the heat exchanger, at least one inlet port for lancing the first fluid, at least one outlet port for discharging the first fluid, at least one inlet port for introducing the second fluid, at least one outlet port for expanding the second fluid, at least one end plate having at least one strain region , preferably a bead or material shaft or a, in particular slot-shaped, recess for reducing the rigidity, preferably parallel to a plate plane of the at least one end plate is provided
  • the continuity refers to the entire at least one end plate and not only to the material of the at least one end plate from which the at least one end plate is made. With the same force acting on the at least one end plate, preferably parallel to the plane of the plate, greater elongation occurs in the heat exchanger according to the invention at the at least one end plate.
  • the recess in the at least one end plate advantageously reduces the rigidity of the at least one end plate parallel or in the direction of the plate plane of the end plate. As a result, the difference in the continuity between the discs and the end plates is less or there is no difference, thereby significantly lower tensions and stresses occur between the end plates and the discs and thus the life of the heat exchanger is significantly extended.
  • the at least one recess has only the function of reducing the rigidity of the at least one end plate and / or reducing the mass of the at least one end plate.
  • the recess has no further function on such. Example, the function of an inlet opening or an outlet opening for introducing or dispensing a fluid or as a means for securing the heat exchanger.
  • the discs have openings for forming the at least one first fluid channel and / or the at least one second fluid channel.
  • the discs are arranged one above the other in a stack so that the openings form a fluid channel perpendicular to the plate plane or the disc plane.
  • the fluid channels forming between the disks are aligned parallel to the disk plane or the disk plane.
  • a reinforcing disk is arranged between the end plate and the disk.
  • the reinforcing disk serves to reduce the stiffness jump between the end plate and the disk.
  • the reinforcing disc has a thickness which is between the thickness of the end plate and the thickness of the disc.
  • the reinforcing disk can also be understood as an end plate and be formed with at least one recess for reducing the rigidity of the at least one Verstarkungsscale analogous to the at least one end plate.
  • the at least one recess is designed as a longitudinal slot and / or as a transverse slot and / or the at least one recess serves exclusively to reduce the rigidity of the at least one end plate, in particular parallel to the plane of the plate at least one end plate, and / or the at least one recess serves aussch manlien to reduce the mass and thus thermal inertia of at least one end plate.
  • two regions of the at least one end plate which are divided off from the at least one recess are connected to one another by means of at least one expansion bead.
  • an end plate is formed as a connection plate or as a cover plate with at least one inlet opening for the first and / or second fluid and with at least one outlet opening for the first and / or second fluid.
  • connection plate parallel to the plane of the plate is greater than the extent of the plates parallel to a disc plane, so that the connection plate has a projection with respect to the discs and at least one device for fastening the heat exchanger is formed on the projection.
  • the at least one device is at least one bore and / or at least one screw.
  • the at least one recess for reducing the rigidity of the at least one end plate is formed in addition to the at least one bore and / or the at least one inlet opening and / or the at least one outlet opening in the at least one end plate.
  • the thickness of the at least one end plate is greater than the thickness of the discs.
  • the thickness of the disc is the material thickness of the disc, so that geometric expansions to form the fluid channels are not taken into account for the expansion of the disc perpendicular to the plane of the plane.
  • the thickness of the at least one end plate is at least 1.5 or 2, preferably at least 3 or 4, times greater than the thickness of at least one disc.
  • the material thicknesses of the panes are essentially very large, in particular the thicknesses of the panes have a difference of less than 30% or 20% or 10%.
  • the end plates and / or the discs are at least partially made of metal, for. As steel or aluminum.
  • the at least one recess of the at least one end plate is perpendicular to the plate plane, the at least one end plate is formed and the at least one recess pierces the at least one end plate completely.
  • the at least one recess of the at least one end plate is formed perpendicular to the plate plane of the at least one end plate and the at least one recess extends only partially through the at least one end plate.
  • the discs are cohesively connected to each other, in particular soldered, and / or the at least one end plate is materially connected to the disc, in particular soldered.
  • a turbulence insert is arranged in the at least one first fluid channel and / or the at least one second fluid channel, and in particular the turbulence insert is attached to two discs, preferably by means of soldering.
  • the turbulence can be used in the at least one first fluid channel and in the at least one second fluid channel a To generate turbulent flow to improve the heat transfer from the first fluid to the second fluid or vice versa.
  • the discs have indentations, so that the at least one first fluid channel and the at least one second fluid channel, which form between two discs, at the boundaries of the fluid channels have either knobs or indentations, thereby increasing the surface for heat transfer and in addition a turbulent flow can be favored.
  • an internal combustion engine with a compressor, for.
  • a turbocharger or a compressor provided for compressing the charge air to be supplied to the engine and a heat exchanger for cooling the compressed air from the compressor charge air, through the heat exchanger, the compressed charge air and a cooling fluid is istleitbar for transferring heat from the compressed charge air to the Cooling fluid, wherein the heat exchanger is designed according to a heat exchanger described in this patent application.
  • FIGS. 1 to 3 a heat exchanger 1 known from the prior art is shown.
  • the heat exchanger 1 has a plurality of discs 2, which are stacked one above the other arranged in a stack. At the stack ends of the stack, an end plate 5 is arranged in each case.
  • a first end plate 5 is designed as a connection plate 6.
  • the connection plate 6 has a large inlet opening 8 for introducing a first fluid, ie charge air.
  • the connecting plate 6 is provided with a large outlet opening 9 for discharging the Lsdeluft from the heat exchanger 1.
  • Two small inlet openings 10 in the connection plate 6 serve to introduce cooling liquid as a second flow and two outlet openings 11 serve to expand the cooling liquid as the second fluid.
  • a rectangular coordinate system having an X, Y and Z axis of the heat exchanger 1 is aligned with the terminal plate 6 so that the X and Y axes rest on the surface of the flat terminal plate 6 and the Z axis is perpendicular thereto the surface of the connection plate 6 is aligned ( Fig. 2 ).
  • the X and Y axes of the coordinate system lie within a plane of the terminal plate 6 and end plate 5.
  • the connection plate 6 Parallel to the plane of the plate plate 6 and in the direction of the X and / or Y-axis, the connection plate 6 has a greater extent than the discs 2 in the direction of the X and Y-axis, so that on the connecting plate 6, a projection 15 to the stack of the discs 2 is formed ( Fig.
  • bores 17 are formed as means 16 for fixing the heat exchanger 1.
  • holes 17 for example, screws or bolts are introduced, by means of which the heat exchanger 1 to another part, for.
  • an end plate 5 designed as a cover plate 7 is present ( Fig. 1 ).
  • the cover plate 7 has two calottes 19.
  • the identically formed discs 2 have openings 20 for forming a first fluid channel 3 and a second fluid channel 4.
  • the openings 20 of the discs 2 are not shown to form the four in this mecanicsbeisplel four second fluid channels 4 in the Z-axis direction.
  • the openings 20 of the disks 2 are viewed in the direction of the Z axis formed on the disks 2 in the same manner as on the connection plate 6.
  • Fig. 3 is a section A-A accordingly Fig. 2 represented by the second fluid channel 4 for the cooling liquid
  • the cooling liquid flows as shown in FIG Fig. 3 through the circular openings in the disks 2 in the direction of the Z-axis and from this flow in the direction of the Z-axis are correspondingly smaller flow rates in the second fluid channels 4 for the cooling liquid, which are aligned in the direction of the X and / or Y-axis , passed through.
  • These second fluid channels, which are aligned in the direction of the X and / or Y axis, thereby form between each two disks 2.
  • the charge air is passed through two large first fluid channels 3 in the direction of the Z axis and from this flow in the Z-axis with charge air subsets of charge air to the aligned in the direction of the X and / or Y axis first fluid channels for the charge air introduced (not shown).
  • Fig. 3 are just these in the direction of the X and / or Y axis aligned first fluid channels 3 shown.
  • the extent of the first fluid channels 3 between two discs 2 in the direction of the Z-axis is greater than the extent of the second fluid channels 4 zwisehen two discs in the Z-axis direction.
  • turbulence inserts 18 are present in the first and second fluid channels 3, 4, between two disks 2 in the direction of the X and in addition.
  • the turbulence inserts 18 are in Fig. 3 not shown and in Fig. 1 only simplified disc-shaped shown.
  • the turbulence inserts 18 have a zigzag-shaped geometry in cross-section and serve to form a turbulent flow in the first and second fluid channels 3, 4, which are aligned in the direction of the X and / or Y axis.
  • the disc plane of the discs 2 is parallel to the plane of the plates of the end plates 5 in the stacked superimposed arrangement of the discs 2 and the end plates 5 in the stack.
  • the end plates 5 have a much greater extent in the X and Y axis than in the Z axis. Because of this greater extent in the X and V axes, the disk plane is defined.
  • the X and Y axes lie within the disk plane. In an analogous manner, the extent of the disks 2 in the X and Y axes is substantially greater than in the Z axis.
  • the X and Y axes define the slice plane of the slices 2.
  • the two end plates are connected to each other by means of a screw, so that the cover plate also has a screw hole for carrying a bolt or a threaded rod.
  • a first embodiment of the heat exchanger 1 according to the invention is shown.
  • the cover plate 7 as an end plate 5 has two recesses 23 formed as transverse slots 13.
  • the transverse slots 13 thus divide the cover plate into three regions 24 in the longitudinal direction or in the Y direction of the cover plate 7. These regions 24 of the cover plate 7 are connected to one another by means of a stretch bead 14.
  • the stiffness of the cover plate 7 parallel to the plane of the plate or in the direction of the X and / or Y-axis is thus substantially lower than the rigidity of the known from the prior art cover plate 7 as shown in the Fig, 1 and 2 ,
  • the stiffness of the cover plate 7 parallel to the plane of the plate or in the direction of the X and / or Y-axis is thus substantially lower than the rigidity of the known from the prior art cover plate 7 as shown in the Fig, 1 and 2 .
  • the stresses can be reduced by providing a backing disk or reinforcing disk between the cover plate and the disks.
  • a support or reinforcing disc is thicker than one of the discs, but thinner than the cover plate.
  • the cover plate 7 four longitudinal slots 12 as recesses 23 and two transverse slots 13. At the transverse slots 13 are similar to the first embodiment strain beads 14 available. As a result, in an analogous manner to the first embodiment, the rigidity of the cover plate 7 in the direction of the X and Y axis can be reduced and thereby the life of the heat exchanger 1 can be substantially increased.
  • the discs 2 and the end plates 5 of the heat exchanger 1 are at least partially made of aluminum and are stoop connected by soldering together.
  • the rigidity of the end plates 5 parallel to the plane of the plate is substantially reduced due to the formation of recesses 23, thereby decreasing the stresses between the end plates 5 and the discs 2 and thereby preventing damage.
  • the recesses 23 can be cut out of the blanks for the production of the end plates 5 in a simple manner, for example by means of a punching or milling process, a water jet or laser cutting. As a result, the costs for producing the heat exchanger 1 increase only very slightly and in return, the life of the heat exchanger 1 is substantially increased.

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

Abstract

The exchanger has two fluid channels conveying two different fluids and placed between multiple disks (2) that are stacked one above the other. An end plate (5) is placed at ends of the disks, and two inlet openings are provided for supplying two different fluids, respectively. Two outlet openings are provided for discharging the fluids, respectively, and the end plate is provided with an expansion region. The expansion region is designed as a recess (23), a slot or a reinforcing fin. An independent claim is also included for an internal combustion engine comprising a compressor.

Description

Die Erfindung betrifft einen Wärmeübertrager gemäß dem Oberbegriff des Anspruches 1 und einen Verbrennungsmotor gemäß dem Oberbegriff des Anspruches 15.The invention relates to a heat exchanger according to the preamble of claim 1 and an internal combustion engine according to the preamble of claim 15.

Wärmeübertrager werden in verschiedenen technischen Anwendungen zur Übertragung von Wärme von einem Fluid auf ein anderes Fluid eingesetzt Insbesondere in Kraftfahrzeugen werden Wärmeübertrager als Ladeluftkühler eingesetzt, um die von einem Verdichter verdichtete Luft vor der Zuführung in den Verbrennungsmotor zu kühlen. Hierbei werden durch den Wärmeübertrager die zu kühlende ladeluft und eine Kühlflüssigkeit durchgeleitet. Die Kühlflüssigkeit nimmt Wärme von der Ladeluft auf und kühlt damit die Ladeluft, Derartige Wärmeübertrager sind hohen Temperaturwechseibeanspruchungen ausgesetzt, well im Betrieb des Kraftfahrzeuges Temperaturschwankungen auftreten und außerdem bei jedem Start des Verbrennungsmotors der Wärmeübertrager zunächst kalt ist.Heat exchangers are used in various technical applications for the transfer of heat from one fluid to another fluid. Especially in motor vehicles, heat exchangers are used as charge air coolers to cool the air compressed by a compressor before it is fed into the internal combustion engine. In this case, the charge air to be cooled and a cooling liquid are passed through the heat exchanger. The cooling liquid absorbs heat from the charge air and thus cools the charge air. Such heat exchangers are exposed to high thermal cycling stresses, because during operation of the motor vehicle temperature fluctuations occur and also at each start of the internal combustion engine, the heat exchanger is initially cold.

Für Ladeluftkühler werden häufig Wärmeübertrager in Scheibenbauweise eingesetzt. Dabei sind viele Scheiben übereinander gestapelt. Aufgrund der Geometrie der Scheiben bilden sich zwischen den Scheiben Kanäle bzw. Fluidkanäle für die Ladeluft und die Kühlflüssigkeit aus. An den Stapelenden ist jeweils eine Endplatte angeordnet. Die Scheiben und die Endplatten sind im Allgemeinen stoffschlüssig mittels Löten miteinander verbunden, Die Dicke der Endplatten ist dabei wesentlich größer als die Dicke der Scheiben. Aufgrund der Temperaturwechselbeanspruchung und/odef einer inhomogenen Temperaturverteilung innerhalb des Wärmeübertragers kommt es zu Verspannungen innerhalb des Wärmeübertragers. Die Verspannungen resultieren insbesondere aus der größeren thermischen Trägheit der Endplatten gegenüber den Scheiben. Die Endplatten weisen eine größere Dicke und damit eine größere Masse auf, so dass sich die Endplatten wesentlich langsamer erwärmen oder abkühlen als die Scheiben. Außerdem ist die Steifigkeit der Endplatten parallel zu einer Plattenebene größer als die Steifigkeit der Scheiben parallel zu einer Scheibenebene. Dieser Unterschied in der Steifigkeit zwischen den Endplatten und den Scheiben kann zu Schäden führen und wirkt sich lebensdauerbegrenzend für den Wärmeübertrager aus. Die Größenänderung der Endplatte bei Temperaturänderungen parallel zu der Plattenebene unterscheidet sich von der Größenänderung bei Temperaturänderungen der Scheibe an der Endplatte parallel zu der Scheibenebene.For intercoolers heat exchangers are often used in disc design. Many discs are stacked on top of each other. Due to the geometry of the discs, channels or fluid channels for the charge air and the cooling fluid form between the discs. At the stack ends, an end plate is arranged in each case. The disks and the end plates are generally bonded together by means of soldering. The thickness of the end plates is substantially greater than the thickness of the disks. Due to the thermal cycling and / or an inhomogeneous temperature distribution within the heat exchanger, stresses occur within the heat exchanger. The tensions result in particular from the greater thermal inertia of the end plates relative to the discs. The end plates have a greater thickness and thus a larger mass, so that the end plates heat much slower or cool than the discs. In addition, the rigidity of the end plates parallel to a plate plane is greater than the rigidity of the plates parallel to a disc plane. This difference in stiffness between the end plates and the discs can cause damage and has a life-limiting effect on the heat exchanger. The change in size of the end plate with temperature changes parallel to the plane of the plate differs from the change in size with temperature changes of the disc on the end plate parallel to the plane of the disc.

Die Aufgabe der vorliegenden Erfindung besteht deshalb darin, einen Wärmeübertrager und einen Verbrennungsmotor mit dem Wärmeübertrager zur Verfügung zu stellen, der bei einem konstruktiv einfachen Aufbau eine lange Lebensdauer auch bei hohen Temperaturwechselbeanspruchungen aufweist. Der Warmeübertrager soll in der Herstellung preiswert sein und zuverlässig im Betrieb arbeiten.The object of the present invention is to provide a heat exchanger and an internal combustion engine with the heat exchanger available, which has a long life even with high thermal cycling in a structurally simple structure. The heat exchanger should be inexpensive to manufacture and work reliably in operation.

Diese Aufgabe wird gelöst mit einem Wärmeüberträger in Scheibenbauweise, umfassend mehrere Übereinander gestapelte Scheiben, wenigstens einen ersten Fluidkanal zum Durchleiten eines ersten Fluides, wenigstens einen zweiten Fluidkanal zum Durchleiten eines zweiten Fluides, wobei der wenigstens eine erste und der wenigstens eine zweite Fluidkanal wenigstens teilweise zwischen den Scheiben mittels der Scheiben aufgrund der Geometrie der Scheiben ausgebildet sind, jeweils eine Endplatte an zwei Stapelenden der Scheiben des Wärmeübertragers, wenigstens eine Einlassöffnung zum Einlesten des ersten Fluides, wenigstens eine Auslassöffnung zum Ausleiten des ersten Fluides, wenigstens eine EinlassÖffnung zum Einleiten des zweiten Fluides, wenigstens eine Auslassöffnung zum Ausweiten des zweiten Fluides, wobei wenigstens eine Endplatte mit wenigstens einem Dehnungsbereich, bevorzugt einer Sicke oder Materialwelle oder einer, insbesondere schlitzförmigen, Ausnehmung zur Verringerung der Steifigkeit, vorzugsweise parallel zu einer Plattenebene der wenigstens einen Endplatte, versehen ist,This object is achieved with a heat exchanger in disk construction, comprising a plurality of stacked disks, at least one first fluid channel for passing a first fluid, at least one second fluid channel for passing a second fluid, wherein the at least one first and the at least one second fluid channel are at least partially formed between the discs by means of the discs due to the geometry of the discs, one end plate at two Stack ends of the discs of the heat exchanger, at least one inlet port for lancing the first fluid, at least one outlet port for discharging the first fluid, at least one inlet port for introducing the second fluid, at least one outlet port for expanding the second fluid, at least one end plate having at least one strain region , preferably a bead or material shaft or a, in particular slot-shaped, recess for reducing the rigidity, preferably parallel to a plate plane of the at least one end plate is provided

Die Stetigkeit bezieht sich auf die gesamte wenigstens eine Endplatte und nicht lediglich auf das Material der wenigstens einen Endplatte, aus welcher die wenigstens eine Endplatte hergestellt ist. Bei der gleichen Kraft, die auf die wenigstens eine Endplatte wirkt, vorzugsweise parallel zu der Plattenebene, tritt bei dem erfindungsgemäßen Wärmeübertrager an der wenigstens einen Endplatte eine größere Dehnung auf.The continuity refers to the entire at least one end plate and not only to the material of the at least one end plate from which the at least one end plate is made. With the same force acting on the at least one end plate, preferably parallel to the plane of the plate, greater elongation occurs in the heat exchanger according to the invention at the at least one end plate.

Die Ausnehmung in der wenigstens einen Endplatte verringert in vorteilhafter Weise die Steifigkeit der wenigstens einen Endplatte parallel bzw. in Richtung der Plattenebene der Endplatte. Dadurch ist der Unterschied in der Stetigkeit zwischen den Scheiben und den Endplatten geringer oder es ist kein Unterschied mehr vorhanden, so dass dadurch zwischen den Endplatten und den Scheiben wesentlich geringere Verspannungen und Spannungen auftreten und somit die Lebensdauer des Wärmeübertragers wesentlich verlängert wird. Die wenigstens eine Ausnehmung hat nur die Funktion, die Steifigkeit der wenigstens einen Endplatte zu verringern und/oder die Masse der wenigstens einen Endplatte zu verringern. Die Ausnehmung weist keine weitere Funktion auf wie z. B. die Funktion einer Einlassöffnung oder einer Auslassöffnung zum Einleiten oder Austeilen eines Fluides oder als Einrichtung zum Befestigen des Wärmeübertragers.The recess in the at least one end plate advantageously reduces the rigidity of the at least one end plate parallel or in the direction of the plate plane of the end plate. As a result, the difference in the continuity between the discs and the end plates is less or there is no difference, thereby significantly lower tensions and stresses occur between the end plates and the discs and thus the life of the heat exchanger is significantly extended. The at least one recess has only the function of reducing the rigidity of the at least one end plate and / or reducing the mass of the at least one end plate. The recess has no further function on such. Example, the function of an inlet opening or an outlet opening for introducing or dispensing a fluid or as a means for securing the heat exchanger.

In einer weiteren Ausgestaltung weisen die Scheiben Öffnungen zur Ausbildung des wenigstens einen ersten Fluidkanales und/oder des wenigstens einen zweiten Fluidkanales auf, Die Scheiben sind übereinander angeordnet in einem Stapel, so dass dadurch die Öffnungen einen Fluidkanal sendrecht zu der Plattenebene oder der Scheibenebene ausbilden. Die sich zwischen den Scheiben ausbildenden Fluidkanäle sind parallel zu der Scheibenebene oder der Plattenebene ausgerichtet.In a further embodiment, the discs have openings for forming the at least one first fluid channel and / or the at least one second fluid channel. The discs are arranged one above the other in a stack so that the openings form a fluid channel perpendicular to the plate plane or the disc plane. The fluid channels forming between the disks are aligned parallel to the disk plane or the disk plane.

In einer weiteren Ausgestaltung ist zwischen der Endplatte und der Scheibe eine Verstärkungsscheibe angeordnet. Die Verstärkungsscheibe dient dazu, den Steifigkeitssprung zwischen der Endplatte und der Scheibe zu verringern. Dabei weist vorzugsweise die Verstärkungsscheibe eine Dicke auf, die zwischen der Dicke der Endplatte und der Dicke der Scheibe liegt. Die Verstärkungsscheibe kann auch als Endplatte aufgefasst werden und mit wenigstens einer Ausnehmung zur Verringerung der Steifigkeit der wenigstens einen Verstarkungsscheibe ausgebildet werden analog wie die wenigstens eine Endplatte.In a further embodiment, a reinforcing disk is arranged between the end plate and the disk. The reinforcing disk serves to reduce the stiffness jump between the end plate and the disk. In this case, preferably, the reinforcing disc has a thickness which is between the thickness of the end plate and the thickness of the disc. The reinforcing disk can also be understood as an end plate and be formed with at least one recess for reducing the rigidity of the at least one Verstarkungsscheibe analogous to the at least one end plate.

Insbesondere ist die wenigstens eine Ausnehmung als Längsschlitz und/oder als Querschlitz ausgebildet und/oder die wenigstens eine Ausnehmung dient ausschließlich zur Verringerung der Steifigkeit der wenigstens einen Endplatte, insbesondere parallel zu der Plattenebene der wenigstens einen Endplatte, und/oder die wenigstens eine Ausnehmung dient ausschießlien zur Verringerung der Masse und damit thermischen Trägheit der wenigstens einen Endplatte.In particular, the at least one recess is designed as a longitudinal slot and / or as a transverse slot and / or the at least one recess serves exclusively to reduce the rigidity of the at least one end plate, in particular parallel to the plane of the plate at least one end plate, and / or the at least one recess serves ausschießlien to reduce the mass and thus thermal inertia of at least one end plate.

In einer weiteren Ausgestaltung sind zwei von der wenigstens einen Ausnehmung abgeteilten Bereiche der wenigstens einen Endplatte mittels wenigstens einer Dehnsicke miteinander verbunden.In a further embodiment, two regions of the at least one end plate which are divided off from the at least one recess are connected to one another by means of at least one expansion bead.

In eine ergänzenden Ausführungsform ist eine Endplatte als Anschlussplatte oder als Abdeckplatte mit wenigstens einer Einlassöffnung für das erste und/oder zweite Fluid und mit wenigstens einer Auslassöffnung für das erste und/oder zweite Fluid ausgebildet.In an additional embodiment, an end plate is formed as a connection plate or as a cover plate with at least one inlet opening for the first and / or second fluid and with at least one outlet opening for the first and / or second fluid.

Vorzugsweise ist die Ausdehnung der Anschlussplatte parallel der Plattenebene größer als die Ausdehnung der Scheiben parallel zu einer Scheibenebene, so dass die Anschlussplatte einen Überstand gegenüber den Scheiben aufweist und an dem Überstand wenigstens eine Einrichtung zum Befestigen des Wärmeübertragers ausgebildet ist.Preferably, the extension of the connection plate parallel to the plane of the plate is greater than the extent of the plates parallel to a disc plane, so that the connection plate has a projection with respect to the discs and at least one device for fastening the heat exchanger is formed on the projection.

In einer Variante ist die wenigstens eine Einrichtung wenigstens eine Bohrung und/oder wenigstens eine Schraube.In a variant, the at least one device is at least one bore and / or at least one screw.

Zweckmäßig ist die wenigstens eine Ausnehmung zur Verringerung der Steifigkeit der wenigstens einen Endplatte zusätzlich zu der wenigstens einen Bohrung und/oder der wenigstens einen Einlassöffnung und/oder der wenigstens einen Auslassöffnung in der wenigstens einen Endplatte ausgebildet.Suitably, the at least one recess for reducing the rigidity of the at least one end plate is formed in addition to the at least one bore and / or the at least one inlet opening and / or the at least one outlet opening in the at least one end plate.

In einer weiteren Ausführungsform ist die Dicke der wenigstens einen Endplatte größer als die Dicke der Scheiben. Die Dicke der Scheibe ist die Materialdicke der Scheibe, so dass für die Ausdehnung der Scheibe senkrecht zu der Scneibenebene geometrische Ausformungen zur Ausbildung der Fluidkanäle nicht berücksichtigt werden.In a further embodiment, the thickness of the at least one end plate is greater than the thickness of the discs. The thickness of the disc is the material thickness of the disc, so that geometric expansions to form the fluid channels are not taken into account for the expansion of the disc perpendicular to the plane of the plane.

Insbesondere ist die Dicke der wenigstens einen Endplatte um das wenigstens 1,5- oder 2-, vorzugsweise wenigstens 3- oder 4-, fache größer als die Dicke wenigstens einer Scheibe.In particular, the thickness of the at least one end plate is at least 1.5 or 2, preferably at least 3 or 4, times greater than the thickness of at least one disc.

In einer weiteren Ausgestaltung sind die Materiaidicken der Scheiben im Wesentlichen glesch groß, insbesondere weisen die Dicken der Scheiben einen Unterschied von weniger als 30% oder 20% oder 10% auf.In a further embodiment, the material thicknesses of the panes are essentially very large, in particular the thicknesses of the panes have a difference of less than 30% or 20% or 10%.

In ergänzender Variante bestehen die Endplatten und/oder die Scheiben wenigstens teilweise aus Metall, z. B. Stahl oder Aluminium.In a complementary variant, the end plates and / or the discs are at least partially made of metal, for. As steel or aluminum.

In einer weiteren Variante ist die wenigstens eine Ausnehmung der wenigstens einen Endplatte senkrecht zu der Plattenebene, der wenigstens einen Endplatte ausgebildet und die wenigstens eine Ausnehmung durchstößt die wenigstens eine Endplatte vollständig.In a further variant, the at least one recess of the at least one end plate is perpendicular to the plate plane, the at least one end plate is formed and the at least one recess pierces the at least one end plate completely.

In einer weiteren Variante ist die wenigstens eine Ausnehmung der wenigstens einen Endplatte senkrecht zu der Plattenebene der wenigstens einen Endplatte ausgebildet und die wenigstens eine Ausnehmung erstreckt sich nur teilweise durch die wenigstens eine Endplatte.In a further variant, the at least one recess of the at least one end plate is formed perpendicular to the plate plane of the at least one end plate and the at least one recess extends only partially through the at least one end plate.

In einer weiteren Ausgestaltung sind die Scheiben stoffschlüssig miteinander verbunden, insbesondere verlötet, und/oder die wenigstens eine Endplatte ist mit der Scheibe stoffschlüssig verbunden, insbesondere angelötet.In a further embodiment, the discs are cohesively connected to each other, in particular soldered, and / or the at least one end plate is materially connected to the disc, in particular soldered.

Insbesondere ist in dem wenigstens einen ersten Fluidkanal und/oder dem wenigstens einen zweiten Fluidkanal eine Turbulenzeinlage angeordnet und insbesondere ist die Turbulenzeinlage an zwei Scheiben, vorzugsweise mittels Löten, befestigt. Die Turbulenzeiniage dient dazu, in dem wenigstens einen ersten Fluidkanal und in dem wenigstens einen zweiten Fluidkanal eine turbulente Strömung zu erzeugen zur Verbesserung der Wärmeübertragung von dem ersten Fluid auf das zweite Fluid oder umgekehrt.In particular, a turbulence insert is arranged in the at least one first fluid channel and / or the at least one second fluid channel, and in particular the turbulence insert is attached to two discs, preferably by means of soldering. The turbulence can be used in the at least one first fluid channel and in the at least one second fluid channel a To generate turbulent flow to improve the heat transfer from the first fluid to the second fluid or vice versa.

In einer weiteren Ausgestaltung weisen die Scheiben Einprägungen auf, so dass der wenigstens eine erste Fluidkanal und der wenigstens eine zweite Fluidkanal, welche sich zwischen zwei Scheiben ausbilden, an den Begrenzungen der Fluidkanäle entweder Noppen oder Einprägungen aufweisen, so dass dadurch die Oberfläche zur Wärmeübertragung erhöht wird und außerdem eine turbulente Strömung begünstigt werden kann.In a further embodiment, the discs have indentations, so that the at least one first fluid channel and the at least one second fluid channel, which form between two discs, at the boundaries of the fluid channels have either knobs or indentations, thereby increasing the surface for heat transfer and in addition a turbulent flow can be favored.

Vorteilhaft ist auch ein Verbrennungsmotor mit einem Verdichter, z. B. einem Turbolader oder einem Kompressor, zum Verdichten der dem Verbrennungsmotor zuzuführenden Ladeluft und einem Wärmeübertrager zur Kühlung der von dem Verdichter verdichteten Ladeluft versehen, wobei durch den Wärmeübertrager die verdichtete Ladeluft und ein Kühlfluid durchleitbar ist zur Übertragung von Wärme von der verdichteten Ladeluft zu dem Kühlfluid, wobei der Wärmeübertrager gemäß einem in dieser Schutzrechtsanmeldung beschriebenen Wärmeübertrager ausgebildet ist.Also advantageous is an internal combustion engine with a compressor, for. As a turbocharger or a compressor, provided for compressing the charge air to be supplied to the engine and a heat exchanger for cooling the compressed air from the compressor charge air, through the heat exchanger, the compressed charge air and a cooling fluid is durchleitbar for transferring heat from the compressed charge air to the Cooling fluid, wherein the heat exchanger is designed according to a heat exchanger described in this patent application.

Im Nachfolgenden werden Ausführungsbeispiele der Erfindung unter Bezugnahme auf die beigefügten Zeichnungen näher beschrieben. Es zeigt:

Fig. 1
eines Explosionsdarstellung eines aus dem Stand der Technik bekannten Wärmeübertragers,
Fig. 2
eine Ansicht des Wärmeübertragers gemäß Fig. 1,
Fig. 3
einen Schnitt A-A des Wärmeübertragers gemäß Fig. 1,
Fig. 4
eine Ansicht eines erfindungsgemäßen Wärmeübertragers in einem ersten Ausführungsbeispiel,
Fig. 5
eine Draufsicht auf eine Abdeckplatte des Wärmeübertragers gemäß Fig. 4 und
Fig. 6
eine perspektivische Ansicht der Abdeckplatte des erfindungsgemäßen Wärmeübertragers in einem zweiten Ausführungsbeispiel.
Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. It shows:
Fig. 1
an exploded view of a known from the prior art heat exchanger,
Fig. 2
a view of the heat exchanger according to Fig. 1 .
Fig. 3
a section AA of the heat exchanger according to Fig. 1 .
Fig. 4
a view of a heat exchanger according to the invention in a first embodiment,
Fig. 5
a plan view of a cover plate of the heat exchanger according to Fig. 4 and
Fig. 6
a perspective view of the cover plate of the heat exchanger according to the invention in a second embodiment.

In den Fig, 1 bis 3 ist ein aus dem Stand der Technik bekannter Wärmeübertrager 1 dargestellt. Der Wärmeübertrager 1 weist eine Vielzahl von Scheiben 2 auf, die übereinander gestapelt zu einem Stapel angeordnet sind. An den Stapelenden des Stapels ist jeweils eine Endplatte 5 angeordnet. Eine erste Endplatte 5 ist als Anschlussplatte 6 ausgebildet, Die Anschlussplatte 6 weist eine große Einlassöffnung 8 zum Einleiten eines ersten Fluides, d. h. Ladeluft, auf. Außerdem ist die Anschlussplatte 6 mit einer großen Auslassöffnung 9 zum Ausleiten der Lsdeluft aus dem Wärmeübertrager 1 versehen. Zwei kleine Einlassöffnungen 10 in der Anschlussplatte 6 dienen zum Einleiten von Kühlflüssigkeit als zweites Flusd und zwei Auslassöffnungen 11 dienen zum Ausweiten der Kühlflüssigkeit als dem zweiten Fluid. Ein rechtwinkliges Koordinatensystem mit einer X-, Y- und Z-Achse des Wärmeübertragers 1 befindet sich dahingehend zu der Anschlussplatte 6 ausgerichtet, dass die X- und Y-Achse auf der Oberfläche der ebenen Anschlussplatte 6 aufliegen und die Z-Achse damit senkrecht auf der Oberfläche der Ahschlussplatte 6 ausgerichtet ist (Fig. 2). Die X- und Y-Achse des Koordinatensystems liegen innerhalb einer Plattenebene der Anschlussplatte 6 bzw. Endplatte 5. Parallel zu der Plattenebene der Anschlussplatte 6 bzw. in Richtung der X- und/oder Y-Achse weist die Anschlussplatte 6 eine größere Ausdehnung auf als die Scheiben 2 in Richtung der X- und Y-Achse, so dass sich an der Anschlussplatte 6 ein Überstand 15 zu dem Stapel aus den Scheiben 2 ausbildet (Fig. 2). An dem Überstand 15 sind Bohrungen 17 als Einrichtungen 16 zum Befestigen des Wärmeübertragers 1 ausgebildet. In die Bohrungen 17 können beispielsweise Schrauben oder Bolzen eingeführt werden, mittels denen der Wärmeübertrager 1 an einem anderen Teil, z. B. einer Komponente eines Kraftfahrzeuges mit entsprechenden Anschlussleitungen für die Kühlflüssigkeit oder die Ladeluft, befestigt werden.In the FIGS. 1 to 3 a heat exchanger 1 known from the prior art is shown. The heat exchanger 1 has a plurality of discs 2, which are stacked one above the other arranged in a stack. At the stack ends of the stack, an end plate 5 is arranged in each case. A first end plate 5 is designed as a connection plate 6. The connection plate 6 has a large inlet opening 8 for introducing a first fluid, ie charge air. In addition, the connecting plate 6 is provided with a large outlet opening 9 for discharging the Lsdeluft from the heat exchanger 1. Two small inlet openings 10 in the connection plate 6 serve to introduce cooling liquid as a second flow and two outlet openings 11 serve to expand the cooling liquid as the second fluid. A rectangular coordinate system having an X, Y and Z axis of the heat exchanger 1 is aligned with the terminal plate 6 so that the X and Y axes rest on the surface of the flat terminal plate 6 and the Z axis is perpendicular thereto the surface of the connection plate 6 is aligned ( Fig. 2 ). The X and Y axes of the coordinate system lie within a plane of the terminal plate 6 and end plate 5. Parallel to the plane of the plate plate 6 and in the direction of the X and / or Y-axis, the connection plate 6 has a greater extent than the discs 2 in the direction of the X and Y-axis, so that on the connecting plate 6, a projection 15 to the stack of the discs 2 is formed ( Fig. 2 ). At the supernatant 15 bores 17 are formed as means 16 for fixing the heat exchanger 1. In the holes 17, for example, screws or bolts are introduced, by means of which the heat exchanger 1 to another part, for. As a component of a motor vehicle with corresponding connection lines for the cooling liquid or the charge air, are attached.

An einem zweiten Stapelende des Stapel ist eine als Abdeckplatte 7 ausgebildete Endplatte 5 vorhanden (Fig. 1). Die Abdeckplatte 7 weist zwei Kalotten 19 auf. Die identisch ausgebildeten Scheiben 2 weisen Öffnungen 20 zur Ausbildung eines ersten Fluidkanales 3 und eines zweiten Fluidkanales 4 auf. In Fig. 1 sind die Öffnungen 20 der Scheiben 2 zur Ausbildung der in diesem Ausführungsbeisplel vier zweiten Fluidkanäle 4 in Richtung der Z-Achse nicht dargestellt. Die Öffnungen 20 der Scheiben 2 sind dabei in Richtung der Z-Achse betrachtet an den Scheiben 2 in gleicher Weise ausgebildet wie an der Anschlussplatte 6. Dadurch bilden sich in Richtung der Z-Achse des Wärmeübertrages 1 in den Scheiben 2 zwei große erste Fluidkanäle 3 zum Durchleiten der Ladeluft und vier kleine zweite Fluidkanäle 4 zum Durchreiten der Kühlflüssigkeit in Richtung der Z-Achse aus.At a second stack end of the stack, an end plate 5 designed as a cover plate 7 is present ( Fig. 1 ). The cover plate 7 has two calottes 19. The identically formed discs 2 have openings 20 for forming a first fluid channel 3 and a second fluid channel 4. In Fig. 1 the openings 20 of the discs 2 are not shown to form the four in this Ausführungsbeisplel four second fluid channels 4 in the Z-axis direction. The openings 20 of the disks 2 are viewed in the direction of the Z axis formed on the disks 2 in the same manner as on the connection plate 6. Thus, in the direction of the Z axis of the heat transfer 1 in the disks 2, two large first fluid channels. 3 for passing the charge air and four small second fluid channels 4 for passing the cooling liquid in the Z-axis direction.

In Fig. 3 ist ein Schnitt A-Agemäß Fig. 2 durch den zweiten Fluidkanal 4 für die Kühlflüssigkeit dargestellt Die Kühlflüssigkeit strömt dabei gemäß der Darstellung in Fig. 3 durch die kreisförmigen Öffnungen in den Scheiben 2 in Richtung der Z-Achse und aus diesem Strom in Richtung der Z-Achse werden entsprechend kleinere Strömungsmengen in zweite Fluidkanäle 4 für die Kühlflüssigkeit, die in Richtung der X- und/oder Y-Achse ausgerichtet sind, durchgeleitet. Diese zweiten Fluidkanäle, die in Richtung der X- und/oder Y-Achse ausgerichtet sind, bilden sich dabei zwischen je zwei Scheiben 2 aus. In analoger Weise wird auch die Ladeluft durch zwei große erste Fluidkanäle 3 in Richtung der Z-Achse geleitet und aus diesem Strom in Richtung der Z-Achse mit Ladeluft werden Teilmengen an Ladeluft zu den in Richtung der X- und/oder Y-Achse ausgerichteten ersten Fluidkanäle für die Ladeluft eingeleitet (nicht dargestellt). In Fig. 3 sind lediglich diese in Richtung der X-und/oder Y-Achse ausgerichteten ersten Fluidkanäle 3 abgebildet. Die Ausdehnung der ersten Fluidkanäle 3 zwischen zwei Scheiben 2 in Richtung der Z-Achse ist dabei größer als die Ausdehnung der zweiten Fluidkanäle 4 zwisehen zwei Scheiben in Richtung der Z-Achse. Dies ist erforderlich, weil für die Ladeluft ein größeres Volumen bzw. ein größerer Strömungsquerschnitt erforderlich ist als für die Kühlflüssigkeit in den zweiten Fluidkanälen 4. In den ersten und zweiten Fluidkanälen 3, 4, die zwischen je zwei Scheiben 2 in Richtung der X- und/oder Y-Achse ausgerichtet sind, sind außerdem Turbulenzeinlagen 18 vorhanden. Die Turbulenzeinlagen 18 sind in Fig. 3 nicht dargestellt und in Fig. 1 lediglich vereinfacht scheibenförmig abgebildet. Die Turbulenzeinlagen 18 weisen im Querschnitt einen zickzackförmige Geometrie auf und dienen zur Ausbildung einer turbulenten Strömung in den ersten und zweiten Fluidkanälen 3, 4, welcher in Richtung der X- und/oder Y-Achse ausgerichtet sind.In Fig. 3 is a section A-A accordingly Fig. 2 represented by the second fluid channel 4 for the cooling liquid, the cooling liquid flows as shown in FIG Fig. 3 through the circular openings in the disks 2 in the direction of the Z-axis and from this flow in the direction of the Z-axis are correspondingly smaller flow rates in the second fluid channels 4 for the cooling liquid, which are aligned in the direction of the X and / or Y-axis , passed through. These second fluid channels, which are aligned in the direction of the X and / or Y axis, thereby form between each two disks 2. In an analogous manner, the charge air is passed through two large first fluid channels 3 in the direction of the Z axis and from this flow in the Z-axis with charge air subsets of charge air to the aligned in the direction of the X and / or Y axis first fluid channels for the charge air introduced (not shown). In Fig. 3 are just these in the direction of the X and / or Y axis aligned first fluid channels 3 shown. The extent of the first fluid channels 3 between two discs 2 in the direction of the Z-axis is greater than the extent of the second fluid channels 4 zwisehen two discs in the Z-axis direction. This is necessary because for the charge air, a larger volume or a larger flow cross-section is required than for the cooling liquid in the second fluid channels 4. In the first and second fluid channels 3, 4, between two disks 2 in the direction of the X and In addition, turbulence inserts 18 are present. The turbulence inserts 18 are in Fig. 3 not shown and in Fig. 1 only simplified disc-shaped shown. The turbulence inserts 18 have a zigzag-shaped geometry in cross-section and serve to form a turbulent flow in the first and second fluid channels 3, 4, which are aligned in the direction of the X and / or Y axis.

Die Scheibenebene der Scheiben 2 ist parallel zur Plattenebene der Endplatten 5 bei der gestapelten übereinander liegenden Anordnung der Scheiben 2 und der Endplatten 5 in dem Stapel. Die Endplatten 5 weisen in der X- und Y-Achse eine wesentlich größere Ausdehnung auf als in der Z-Achse. Aufgrund dieser größeren Ausdehnung in der X- und V-Achse ist die Plattenebene definiert. Die X- und Y-Achse liegt innerhalb der Plattenebene. In analoger Weise ist die Ausdehnung der Scheiben 2 in der X- und Y-Achse wesentlich größer als in der Z-Achse. Die X-und Y-Achse definiert die Scheibenebene der Scheiben 2.The disc plane of the discs 2 is parallel to the plane of the plates of the end plates 5 in the stacked superimposed arrangement of the discs 2 and the end plates 5 in the stack. The end plates 5 have a much greater extent in the X and Y axis than in the Z axis. Because of this greater extent in the X and V axes, the disk plane is defined. The X and Y axes lie within the disk plane. In an analogous manner, the extent of the disks 2 in the X and Y axes is substantially greater than in the Z axis. The X and Y axes define the slice plane of the slices 2.

Die Scheiben 2 und die Endplatten 5 sind miteinander verlötet. Dies gilt auch für die Turbulenzeinlagen 18. Zusätzlich ist eine der beiden Endplatten 5 noch mit einer Ablassschraube 21 (Fig. 1) versehen. Kalotten 19 der Abdeckplatte 7 verschließen die beiden großen Öffnungen 20 der Scheibe 2 an der Abdeckplatte 7 (Fig. 1).The discs 2 and the end plates 5 are soldered together. This also applies to the turbulence inserts 18. In addition, one of the two end plates 5 is still provided with a drain plug 21 (FIG. Fig. 1 ) Mistake. Calottes 19 of the cover plate 7 close the two large openings 20 of the disc 2 on the cover plate 7 (FIG. Fig. 1 ).

Gemäß einem nicht gezeigten Ausführungsbeispiel sind die beiden Endplatten mittels einer Verschraubung miteinander verbunden, so dass die Abdeckplatte auch eine Verschraubungsbohrung zur Durchführung eines Bolzens oder einer Gewindestange aufweist.According to an embodiment, not shown, the two end plates are connected to each other by means of a screw, so that the cover plate also has a screw hole for carrying a bolt or a threaded rod.

In Fig. 4 und 5 ist ein erstes Ausführungsbeispiel des erfindungsgemäßen Wärmeübertragers 1 dargestellt. Im Nachfolgenden werden bei dem erfindungsgemäßen Wärmeübertrager 1 im Wesentlichen nur die Unterschiede zu dem aus dem Stand der Technik bekannten Wärmeübertrager 1 aus den Fig. 1 bis 3 beschrieben. Die Abdeckplatte 7 als Endplatte 5 weist zwei als Querschlitze 13 ausgebildete Ausnehmungen 23 auf. Die Querschlitze 13 unterteilen damit die Abdeckplatte in drei Bereiche 24 in Längsrichtung bzw. in Y-Richtung der Abdeckplatte 7. Diese Bereiche 24 der Abdeckplatte 7 sind mittels einer Dehnsicke 14 miteinander verbunden. Die Steifigkeit der Abdeckplatte 7 parallel zu der Plattenebene bzw. in Richtung der X- und/oder Y-Achse ist damit wesentlich geringer als die Steifigkeit der aus dem Stand der Technik bekannten Abdeckplatte 7 gemäß der Darstellung in den Fig, 1 und 2. Dadurch treten in vorteilhafter Weise bei einer inhomogenen Temperaturverteilung innerhalb des Wärmeübertragers 1 oder bei Temperaturwechselbeanspruchungen wesentlich geringer Verspannungen zwischen der Abdeckplatte 7 und der Scheibe 2 an der Abdeckplatte 7 auf. Dadurch können Schäden, z. B. Undichtigkeiten, zwischen der Abdeckplatte 7 und der Scheibe 2 vermieden und dadurch die Lebensdauer des Wärmeübertragers 1 wesentlich verlängert werden. Die Plattenebene der Abdeckplatte 7 entspricht der Zeichenebene gemäß der Darstellung in Fig. 5.In Fig. 4 and 5 a first embodiment of the heat exchanger 1 according to the invention is shown. In the following, in the heat exchanger 1 according to the invention essentially only the differences from the known from the prior art heat exchanger 1 from the Fig. 1 to 3 described. The cover plate 7 as an end plate 5 has two recesses 23 formed as transverse slots 13. The transverse slots 13 thus divide the cover plate into three regions 24 in the longitudinal direction or in the Y direction of the cover plate 7. These regions 24 of the cover plate 7 are connected to one another by means of a stretch bead 14. The stiffness of the cover plate 7 parallel to the plane of the plate or in the direction of the X and / or Y-axis is thus substantially lower than the rigidity of the known from the prior art cover plate 7 as shown in the Fig, 1 and 2 , As a result, in an inhomogeneous temperature distribution within the heat exchanger 1 or in thermal cycling significantly lower stresses between the cover plate 7 and the disc 2 on the cover plate 7 occur in an advantageous manner. This can damage, z. B. leaks, avoided between the cover plate 7 and the disc 2 and thereby the life of the heat exchanger 1 are substantially extended. The plate plane of the cover plate 7 corresponds to the plane of the drawing as shown in FIG Fig. 5 ,

Zusätzlich können die Spannungen durch das Vorsehen einer Stützscheibe oder Verstärkungsscheibe zwischen der Abdeckplatte und den Scheiben verringert werden. Insbesondere vorteilhaft ist eine solche Stütz- oder Verstärkungsscheibe dicker als eine der Scheiben, aber dünner als die Abdeckplatte.In addition, the stresses can be reduced by providing a backing disk or reinforcing disk between the cover plate and the disks. Particularly advantageously, such a support or reinforcing disc is thicker than one of the discs, but thinner than the cover plate.

In dem in Fig. 6 dargestellten zweiten Ausführungsbeispiel weist die Abdeckplatte 7 vier Längsschlitze 12 als Ausnehmungen 23 und zwei Querschlitze 13 auf. An den Querschlitzen 13 sind analog zu dem ersten Ausführungsbeispiel Dehnsicken 14 vorhanden. Dadurch kann in analoger Weise zu dem ersten Ausführungsbeispiel die Steifigkeit der Abdeckplatte 7 in Richtung der X- und Y-Achse verringert und dadurch die Lebensdauer des Wärmeübertragers 1 wesentlich erhöht werden.In the in Fig. 6 illustrated second embodiment, the cover plate 7 four longitudinal slots 12 as recesses 23 and two transverse slots 13. At the transverse slots 13 are similar to the first embodiment strain beads 14 available. As a result, in an analogous manner to the first embodiment, the rigidity of the cover plate 7 in the direction of the X and Y axis can be reduced and thereby the life of the heat exchanger 1 can be substantially increased.

Die Scheiben 2 und die Endplatten 5 des Wärmeübertragers 1 bestehen wenigstens teilweise aus Aluminium und sind stotfschlüssig mittels einer Verlötung miteinander verbunden.The discs 2 and the end plates 5 of the heat exchanger 1 are at least partially made of aluminum and are stoop connected by soldering together.

Insgesamt betrachtet sind mit dem erfindungsgemäßen Wärmeübertrager 1 wesentliche Vorteile verbunden. Die Steifigkeit der Endplatten 5 parallel zu der Plattenebene ist wesentlich aufgrund der Ausbildung von Ausnehmungen 23 verringert, so dass dadurch die Spannungen zwischen den Endplatten 5 und den Scheiben 2 abnehmen und dadurch Schäden vermieden werden können. Dadurch wird die Lebensdauer des Wärmeübertragers 1 in vorteilhafter Weise mit einem geringen technischen Aufwand vergrößert. Die Ausnehmungen 23 können auf einfache Art und Weise, beispielsweise mittels eines Stanz- oder Fräsvorganges, eines Wasserstrahl- oder Laserschneidens, aus den Rohlingen zur Herstellung der Endplatten 5 ausgeschnitten werden. Dadurch erhöhen sich die Kosten zur Herstellung des Wärmeübertragers 1 nur sehr geringfügig und im Gegenzug wird die Lebensdauer des Wärmeübertragers 1 wesentlich erhöht.Overall, significant advantages are associated with the heat exchanger 1 according to the invention. The rigidity of the end plates 5 parallel to the plane of the plate is substantially reduced due to the formation of recesses 23, thereby decreasing the stresses between the end plates 5 and the discs 2 and thereby preventing damage. As a result, the life of the heat exchanger 1 is advantageously increased with little technical effort. The recesses 23 can be cut out of the blanks for the production of the end plates 5 in a simple manner, for example by means of a punching or milling process, a water jet or laser cutting. As a result, the costs for producing the heat exchanger 1 increase only very slightly and in return, the life of the heat exchanger 1 is substantially increased.

Claims (15)

Wärmeübertrager (1) in Scheibenbauweise, umfassend - mehrere übereinander gestapelte Scheiben (2), - wenigstens einen ersten Fluidkanal (3) zum Durchleiten eines ersten Fluides, - wenigstens einen zweiten Fluidkanal (4) zum Durchleiten eines zweiten Fluides, - wobei der wenigstens eine erste und wenigstens eine zweite Fluidkanal (3, 4) wenigstens teilweise zwischen den Scheiben (2) mittels der Scheiben (2) aufgrund der Geometrie der Scheiben (2) ausgebildet sind, - eine Endplatte (5) an einem oder zwei Stapelenden der Scheiben (2), - wenigstens eine Einlassöffnung (8) zum Einleiten des ersten Fluides, - wenigstens eine Auslassöffnung (9) zum Ausleiten des ersten Fluides, - wenigstens eine Einlassöffnung (10) zum Einleiten des zweiten Fluides, - wenigstens eine Auslassöffnung (11) zum Ausleiten des zweiten Fluides, dadurch gekennzeichnet, dass
die Endplatte (5) mit wenigstens einem insbesondere einen Schlitz oder eine Sicke aufweisenden Dehnungsbereich, insbesondere einer Ausnehmung (23) zur Verringerung der Steifigkeit, versehen ist.Heat exchanger (1) in disk construction, comprising - several stacked discs (2), at least one first fluid channel (3) for passing a first fluid, at least one second fluid channel (4) for passing a second fluid, - wherein the at least one first and at least one second fluid channel (3, 4) are formed at least partially between the discs (2) by means of the discs (2) due to the geometry of the discs (2), an end plate (5) at one or two stack ends of the discs (2), at least one inlet opening (8) for introducing the first fluid, at least one outlet opening (9) for discharging the first fluid, at least one inlet opening (10) for introducing the second fluid, at least one outlet opening (11) for discharging the second fluid, characterized in that
the end plate (5) is provided with at least one expansion region, in particular a recess (23) for reducing the rigidity, in particular having a slot or a bead. Wärmeübertrager nach Anspruch 1 oder 2,
dadurch gekennzeichnet, dass
zwei von der wenigstens einen Ausnehmung (23) abgeteilte Bereiche (24) der wenigstens einen Endplatte (5) mittels wenigstens einem Steg, insbesondere einer Dehnsicke (14) miteinander verbunden sind.Heat exchanger according to claim 1 or 2,
characterized in that
two of the at least one recess (23) divided regions (24) of the at least one end plate (5) by means of at least one web, in particular a Dehnsicke (14) are interconnected. Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
eine Endplatte (5) als Anschlussplatte (6) oder als Abdeckplatte (7) mit wenigstens einer Einlassöffnung (8, 10) für das erste und/oder zweite Fluid und mit wenigstens einer Auslassöffnung (9, 11) für das erste und/oder zweite Fluid ausgebildet ist.Heat exchanger according to one or more of the preceding claims,
characterized in that
an end plate (5) as a connection plate (6) or as a cover plate (7) with at least one inlet opening (8, 10) for the first and / or second fluid and with at least one outlet opening (9, 11) for the first and / or second Fluid is formed. Wärmeübertrager nach Anspruch 4,
dadurch gekennzeichnet, dass
die Ausdehnung der Anschlussplatte (6) parallel der Plattenebene größer ist als die Ausdehnung der Scheiben (2) parallel zu einer Scheibenebene, so dass die Anschlussplatte (6) einen Überstand (15) gegenüber den Scheiben (2) aufweist und an dem Überstand (15) wenigstens eine Einrichtung (16) zum Befestigen des Wärmeübertragers (1) ausgebildet ist.Heat exchanger according to claim 4,
characterized in that
the extension of the connecting plate (6) parallel to the plane of the plate is greater than the extent of the discs (2) parallel to a plane of the disc, so that the connecting plate (6) has a projection (15) opposite the discs (2) and on the projection (15 ) at least one means (16) for fixing the heat exchanger (1) is formed. Wärmeübertrager nach Anspruch 5,
dadurch gekennzeichnet, dass
die wenigstens eine Einrichtung (16) wenigstens eine Bohrung (17) ist.Heat exchanger according to claim 5,
characterized in that
the at least one device (16) is at least one bore (17). Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
die wenigstens eine Ausnehmung (23) zur Verringerung der Steifigkeit der wenigstens einen Endplatte (5) zusätzlich zu der wenigstens einen Bohrung (17) und/oder der wenigstens einen Einlassöffnung (8, 10) und/oder der wenigstens einen Auslassöffnung (9, 11) in der wenigstens einen Endplatte (5) ausgebildet ist.Heat exchanger according to one or more of the preceding claims,
characterized in that
the at least one recess (23) for reducing the rigidity of the at least one end plate (5) in addition to the at least one bore (17) and / or the at least one inlet opening (8, 10) and / or the at least one outlet opening (9, 11 ) is formed in the at least one end plate (5). Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
die Dicke der wenigstens einen Endplatte (5) größer ist als die Dicke der Scheiben (2).Heat exchanger according to one or more of the preceding claims,
characterized in that
the thickness of the at least one end plate (5) is greater than the thickness of the discs (2). Wärmeübertrager nach Anspruch 8,
dadurch gekennzeichnet, dass
die Dicke der wenigstens einen Endplatte (5) um das wenigstens 1,5-oder 2-, vorzugsweise wenigstens 3- oder 4-, fache größer ist als die Dicke wenigstens einer Scheibe (2).Heat exchanger according to claim 8,
characterized in that
the thickness of the at least one end plate (5) is at least 1.5 or 2, preferably at least 3 or 4, times greater than the thickness of at least one disk (2). Wärmeübertrager nach einem oder mehreren der vorhergehenden Anusprüche,
dadurch gekennzeichnet, dass
die Materialdicken der Scheiben (2) im Wesentlichen gleich groß sind.Heat exchanger according to one or more of the preceding claims,
characterized in that
the material thicknesses of the discs (2) are substantially equal. Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
die Endplatten (5) und/oder die Scheiben (2) wenigstens teilweise aus Metall, z. B. Stahl oder Aluminium, bestehen.Heat exchanger according to one or more of the preceding claims,
characterized in that
the end plates (5) and / or the discs (2) at least partially made of metal, for. As steel or aluminum exist. Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
die wenigstens eine Ausnehmung (23) die wenigstens eine Endplatte (5) vollständig durchstößt.Heat exchanger according to one or more of the preceding claims,
characterized in that
the at least one recess (23) completely penetrates the at least one end plate (5). Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprliche,
dadurch gekennzeichnet, dass
die wenigstens eine Ausnehmung (23) die wenigstens eine Endplatte (5) nur teilweise durchstößt.Heat exchanger according to one or more of the preceding claims,
characterized in that
the at least one recess (23) penetrates the at least one end plate (5) only partially. Wärmeübertrager nach einem oder mehreren der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
die Scheiben (2) stoffschlüssig miteinander verbunden, insbesondere verlötet, sind und/oder die wenigstens eine Endplatte (5) mit der Scheibe (2) stoffschlüssig verbunden, insbesondere angelötet, ist.Heat exchanger according to one or more of the preceding claims,
characterized in that
the discs (2) are materially connected to each other, in particular soldered, and / or the at least one end plate (5) with the disc (2) integrally connected, in particular soldered, is. Wärmeübertrager nach einem oder mehreren der vorhergehenden Anspruche,
dadurch gekennzeichnet, dass
in dem wenigstens einen ersten Fluidkanal (3) und/oder dem wenigstens einen zweiten Fluidkanal (4) eine Turbulenzeinlage (18) angeordnet ist und insbesondere die Turbulenzeinlage (18) an zwei Scheiben (2), vorzugsweise mittels Löten, befestigt ist.Heat exchanger according to one or more of the preceding claims,
characterized in that
in which at least one first fluid channel (3) and / or the at least one second fluid channel (4) a turbulence insert (18) is arranged and in particular the turbulence insert (18) on two discs (2), preferably by means of soldering, is attached. Verbrennungsmotor mit einem Verdichter, z. B. einem Turbolader oder Kompressor, zum Verdichten der dem Verbrennungsmotor zuzuführenden Ladeluft und einem Wärmeübertrager (1) zur Kühlung der von dem Verdichter verdichteten Ladeluft, wobei durch den Wärmeübertrager (1) die verdichtete Ladeluft und ein Kühlfluid durchleitbar ist zur Übertragung von Warme von der verdichteten Ladeluft zu dem Kühlfluid,
dadurch gekennzeichnet, dass
der Wärmeübertrager (1) gemäß einem oder mehreren der vorhergehenden Ansprüche ausgebildet ist.Internal combustion engine with a compressor, z. As a turbocharger or compressor, for compressing the internal combustion engine to be supplied charge air and a heat exchanger (1) for cooling the compressed air from the compressor charge air, through the heat exchanger (1) the compressed charge air and a cooling fluid is durchleitbar for transmitting heat from the compressed charge air to the cooling fluid,
characterized in that
the heat exchanger (1) is designed according to one or more of the preceding claims.
EP10155227.1A 2009-03-13 2010-03-02 Plate Heat exchanger for high exposure from thermal cycling Active EP2236969B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009012784A DE102009012784A1 (en) 2009-03-13 2009-03-13 Heat exchanger

Publications (3)

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EP2236969A3 EP2236969A3 (en) 2014-04-02
EP2236969B1 EP2236969B1 (en) 2017-05-10

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ID=42263320

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EP (1) EP2236969B1 (en)
DE (1) DE102009012784A1 (en)

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Also Published As

Publication number Publication date
EP2236969A3 (en) 2014-04-02
EP2236969B1 (en) 2017-05-10
US9243849B2 (en) 2016-01-26
US20100258095A1 (en) 2010-10-14
DE102009012784A1 (en) 2010-09-16

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