EP2622299B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP2622299B1
EP2622299B1 EP11757177.8A EP11757177A EP2622299B1 EP 2622299 B1 EP2622299 B1 EP 2622299B1 EP 11757177 A EP11757177 A EP 11757177A EP 2622299 B1 EP2622299 B1 EP 2622299B1
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EP
European Patent Office
Prior art keywords
planar wall
wall parts
heat exchanger
recess
plates
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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.)
Not-in-force
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EP11757177.8A
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German (de)
French (fr)
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EP2622299A2 (en
Inventor
Heinrich J Kuehne
Thomas Cott
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Hydac Cooling GmbH
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Hydac Cooling GmbH
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Publication of EP2622299A2 publication Critical patent/EP2622299A2/en
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Publication of EP2622299B1 publication Critical patent/EP2622299B1/en
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    • 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
    • F28D9/0062—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 spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

Definitions

  • the invention relates to a heat exchanger having the features in the preamble of claim 1.
  • Heat exchangers of this type are state of the art, cf. DE 20 208 748 U1 , With air as the cooling medium, such heat exchangers are often used for cooling hydraulic fluids for the working hydraulics of mechanical systems, such as construction machinery. Like., For hydrostatic travel drives or as oil cooler for high-loaded transmission, especially in wind turbines. In the operation of such systems, the heat exchangers are exposed not only to mechanical stresses, but because of the high operating temperature of the fluids to be cooled, in particular thermal loads. This is particularly the case when intermittent operations result in temperature jumps, resulting in excessive stresses in the package of components due to material strains, which are connected to a rigid block by soldering. The result is stress cracks, especially in the area of the solder joints, with the risk of failure of the heat exchanger and thus the threat to the associated system.
  • the invention has for its object to provide a heat exchanger available, which is characterized by a improved resistance to operating loads, so that a safe long-term operation is possible.
  • the DE3521914 discloses a heat exchanger, in particular for fluid cooling devices, with a package of plane-parallel plates, wherein between pairs of superimposed plates in alternation fürström Kunststoffe for a hot medium and for a cooling medium are formed, which are bounded laterally by the respective plates at a distance holding profile strips on the Form plates adjacent solder surfaces, wherein the profile strips at the flow areas of a medium and the other medium along an angle abutting edges of the plates, wherein at least the moldings of the flow areas of the cooling medium comprises a base body, two of this along the solder surfaces extending leg and between these have an open to the adjacent flow area recess, and wherein the recess is limited at least in the adjoining at its inner end portion region of planar wall parts. According to the invention this object is achieved by a heat exchanger having the features of claim 1 in its entirety.
  • a significant feature of the invention is that the recess, starting from its inner end portion, divergent first planar wall portions extending to narrow points of the cross section of the legs, adjoining the bottlenecks, converging second planar wall parts and adjoining third planar wall parts which, parallel to the soldering surfaces, extend in the vicinity of the opening of the recess.
  • zones of lower flexural strength are formed on the profile legs, to which leg sections on both sides connect in which the bending resistance increases substantially linearly.
  • the bottlenecks not only define a bending line of a kind of bending joint, but also represent the location of the steepest temperature gradient. Since this is effective at the location of the smallest material cross-section, resulting correspondingly low material expansions and stresses.
  • the shape of the cross-section adjoining the soldering surfaces of the legs is optimized with regard to the avoidance of excessive stresses by special shaping of the recess, at least in the case of the profile strips adjoining the cooling medium.
  • the recess starting from the inner end portion having planar wall parts, an at least approximately linear change in the bending strength over the length of the profile legs can be achieved, so that by selecting the length and / or inclination of these planar wall parts relative to the Lötzine an optimal Bending behavior of the legs is achievable.
  • the recess is shaped in such a way that adjoin the third planar wall parts fourth planar wall parts which extend slightly divergent to the opening of the recess to each other.
  • the first planar wall portions may form mutually perpendicular planes, and the second planar wall portions may include an obtuse angle with the first planar wall portions, which is preferably only slightly greater than a right angle.
  • the cross-sectional shape of the recess in the region adjacent to the inner end corresponds approximately to a square open towards the opening.
  • the arrangement can be made such that the first planar wall parts are connected to each other and these with the second planar wall parts each over curved wall locations with the same radius of curvature.
  • the second planar wall parts are connected to the third planar wall parts and these with the fourth planar wall parts preferably also each curved over wall locations with the same, second radius of curvature, which is twice the first radius of curvature.
  • the arrangement is preferably made so that the thickness of the cross section of the legs in the region of the third planar wall parts is approximately twice the thickness of the cross section at the bottlenecks.
  • the Fig.1 illustrates an embodiment in the form of a conventional plate-type heat exchanger with a stack of flat plates 1, preferably made of an aluminum alloy, which run in parallel planes and separating plates for flow areas located between them form, between each successive plate pairs in alternation in each case a flow area 3 for the medium to be cooled, for example, hydraulic oil, and a flow area 5 for a cooling medium, such as cooling air, are formed.
  • a flow area 3 for the medium to be cooled for example, hydraulic oil
  • a flow area 5 for a cooling medium such as cooling air
  • the für Hopkins Society 5 of the cooling medium is laterally also each bounded by end strips, which form the spacers between the respective plate pair and which are formed as profiled strips 11 with special, inventive design.
  • This embodiment of the invention is based on the Fig.2 explained in more detail.
  • the profile strips 11, which are also preferably extruded from an aluminum alloy, have a cuboid or block-shaped basic body 13 which faces the edge region of the plates 1, a recess 15 in the form of a continuous longitudinal groove and the recess 15 limbs 17 bordering on both sides.
  • the recess 15 is open to the flow area 5, in which there are cooling fins 19, which, as well as the turbulators 9 in the flow area 3, increase the effective heat transfer area.
  • the inner end portion 23 ( Fig.2 ) of the recess 15 is located from the closed end 21 of the profile strip 11 at a distance which is slightly greater than the distance between the end portion 23 and opening of the recess 15.
  • the recess 15 is, starting from its inner end portion 23, bounded by planar wall portions 29 which, diverging to each other and enclosing a right angle, extend into the vicinity of the relevant soldering surface 25 and form there a Profilengstelle 31 of the profile cross section of the legs 17.
  • the constriction 31 is adjoined by second planar wall parts 33, which converge toward one another and enclose an obtuse angle with the first planar wall parts 29, which angle is slightly larger than a right angle.
  • the length of these second planar wall portions 33 is slightly smaller than the length of the first planar wall portions 29, and these third planar wall portions 33 are followed by third planar wall portions 35 defining planes parallel to the soldering surfaces 25 and extending into the vicinity of the opening the recess 15 extend. At this third planar wall portions 35 in turn close fourth planar wall portions 37 which extend slightly divergent to the opening of the recess 15 to each other.
  • the connection of the first planar wall portions 29 with each other and with the second planar wall portions 33 takes place in each case via curved wall portions 39 with the same radius of curvature.
  • the connection of the second planar wall portions 33 with the third planar wall portions 35 and this with the fourth planar wall portions 37 also takes place over curved wall portions 41, in which the radius of curvature is twice the radius of curvature at the wall portions 39.
  • the inventively provided cross-sectional shape of the recess 15 results in an effective reduction of the operational stress peaks and the risk of cracking at the solder joints.
  • the bottlenecks 31 on the leg profile form the location of the steepest temperature gradient.
  • this is also the location of the smallest material cross-section, so that thermal deformations are limited to correspondingly limited material parts. Since the profile thickness of the legs 17, starting from the constrictions 31, increases towards the opening to a profile thickness which corresponds approximately to twice the constrictions 31, an optimum stress distribution over the area of the soldering surfaces 25 results.
  • the heat exchanger device according to the invention need not be limited to the field of fluid cooling, but can also be used generally for the cooling of gaseous media and here in particular intercooler (diesel engines), as well as secondary and intercooler (compressors) to include.
  • intercooler diesel engines
  • secondary and intercooler compressors
  • the temperature differences (cooling air to medium) in the pertinent applications are comparatively much higher than described above.

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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)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Description

Die Erfindung betrifft einen Wärmetauscher mit den Merkmalen im Oberbegriff von Anspruch 1.The invention relates to a heat exchanger having the features in the preamble of claim 1.

Wärmetauscher dieser Art, auch Lamellenkühler genannt, sind Stand der Technik, vgl. DE 20 208 748 U1 . Mit Luft als Kühlmedium werden solche Wärmetauscher vielfach zur Kühlung von Hydraulikflüssigkeiten für die Arbeitshydraulik maschineller Anlagen, wie Baumaschinen od. dgl., für hydrostatische Fahrantriebe oder als Ölkühler für hoch belastete Getriebe, namentlich bei Windkraftanlagen, eingesetzt. Beim Betrieb derartiger Anlagen sind die Wärmetauscher nicht nur mechanischen Belastungen, sondern wegen der hohen Betriebstemperatur abzukühlender Fluide in besonderem Maße auch thermischen Belastungen ausgesetzt. Dies ist insbesondere der Fall, wenn sich durch intermittierende Betriebsweisen Temperatursprünge ergeben, was aufgrund von Werkstoffdehnungen zu starken Spannungen in dem Paket der Komponenten führt, die durch Löten zu einem starren Block verbunden sind. Die Folge sind Spannungsrisse, insbesondere im Bereich der Lötnähte, mit der Gefahr des Versagens des Wärmetauschers und damit der Gefährdung des zugehörigen Systems.Heat exchangers of this type, also called lamella coolers, are state of the art, cf. DE 20 208 748 U1 , With air as the cooling medium, such heat exchangers are often used for cooling hydraulic fluids for the working hydraulics of mechanical systems, such as construction machinery. Like., For hydrostatic travel drives or as oil cooler for high-loaded transmission, especially in wind turbines. In the operation of such systems, the heat exchangers are exposed not only to mechanical stresses, but because of the high operating temperature of the fluids to be cooled, in particular thermal loads. This is particularly the case when intermittent operations result in temperature jumps, resulting in excessive stresses in the package of components due to material strains, which are connected to a rigid block by soldering. The result is stress cracks, especially in the area of the solder joints, with the risk of failure of the heat exchanger and thus the threat to the associated system.

Im Hinblick auf diese Problematik liegt der Erfindung die Aufgabe zugrunde, einen Wärmetauscher zur Verfügung zu stellen, der sich durch eine verbesserte Widerstandsfähigkeit gegen Betriebsbelastungen auszeichnet, so dass ein sicherer Langzeitbetrieb ermöglicht ist.In view of this problem, the invention has for its object to provide a heat exchanger available, which is characterized by a improved resistance to operating loads, so that a safe long-term operation is possible.

Die DE3521914 offenbart einen Wärmetauscher, insbesondere für Fluidkühlvorrichtungen, mit einem Paket aus planparallelen Platten, wobei zwischen Paaren übereinanderliegender Platten im Wechsel Durchströmbereiche für ein heißes Medium und für ein Kühlmedium gebildet sind, die jeweils durch die Platten auf Abstand haltende Profilleisten seitlich begrenzt sind, die an den Platten anliegende Lötflächen bilden, wobei sich die Profilleisten an den Durchströmbereichen des einen Mediums und des anderen Mediums entlang von im Winkel aneinanderstoßender Ränder der Platten erstrecken, wobei zumindest die Profilleisten der Durchströmbereiche des Kühlmediums einen Grundkörper, zwei sich von diesem entlang der Lötflächen erstreckende Schenkel sowie zwischen diesen eine zum angrenzenden Durchströmbereich offene Ausnehmung aufweisen, und wobei die Ausnehmung zumindest in dem an ihren inneren Endabschnitt angrenzenden Bereich von ebenflächigen Wandteilen begrenzt ist. Erfindungsgemäß ist diese Aufgabe durch einen Wärmetauscher gelöst, der die Merkmale des Patentanspruches 1 in seiner Gesamtheit aufweist.The DE3521914 discloses a heat exchanger, in particular for fluid cooling devices, with a package of plane-parallel plates, wherein between pairs of superimposed plates in alternation Durchströmbereiche for a hot medium and for a cooling medium are formed, which are bounded laterally by the respective plates at a distance holding profile strips on the Form plates adjacent solder surfaces, wherein the profile strips at the flow areas of a medium and the other medium along an angle abutting edges of the plates, wherein at least the moldings of the flow areas of the cooling medium comprises a base body, two of this along the solder surfaces extending leg and between these have an open to the adjacent flow area recess, and wherein the recess is limited at least in the adjoining at its inner end portion region of planar wall parts. According to the invention this object is achieved by a heat exchanger having the features of claim 1 in its entirety.

Nach dem kennzeichnenden Teil des Anspruches 1 besteht eine wesentliche Besonderheit der Erfindung darin, dass die Ausnehmung, ausgehend von ihrem inneren Endabschnitt, divergierende erste ebenflächige Wandteile, die sich zu Engstellen des Querschnittes der Schenkel erstrecken, sich an die Engstellen anschließende, konvergierende zweite ebenflächige Wandteile sowie sich daran anschließende dritte ebenflächige Wandteile aufweist, die sich, zu den Lötflächen parallel, in die Nähe der Öffnung der Ausnehmung erstrecken. Dadurch sind an den Profilschenkeln Zonen geringerer Biegefestigkeit gebildet, an die sich zu beiden Seiten Schenkelabschnitte anschließen, in denen der Biegewiderstand im Wesentlichen linear zunimmt. Die Engstellen definieren nicht nur eine Biegelinie einer Art Biegegelenk, sondern stellen auch den Ort des steilsten Temperaturgradienten dar. Da dieser am Ort des geringsten Materialquerschnitts wirksam ist, ergeben sich entsprechend geringe Materialdehnungen und -spannungen.According to the characterizing part of claim 1, a significant feature of the invention is that the recess, starting from its inner end portion, divergent first planar wall portions extending to narrow points of the cross section of the legs, adjoining the bottlenecks, converging second planar wall parts and adjoining third planar wall parts which, parallel to the soldering surfaces, extend in the vicinity of the opening of the recess. As a result, zones of lower flexural strength are formed on the profile legs, to which leg sections on both sides connect in which the bending resistance increases substantially linearly. The bottlenecks not only define a bending line of a kind of bending joint, but also represent the location of the steepest temperature gradient. Since this is effective at the location of the smallest material cross-section, resulting correspondingly low material expansions and stresses.

Weiterhin ist vorgesehen, dass durch spezielle Formgebung der Ausnehmung zumindest bei den an das Kühlmedium angrenzenden Profilleisten die Form des an die Lötflächen der Schenkel angrenzenden Querschnittes im Hinblick auf die Vermeidung übermäßiger Spannungen optimiert ist. Dadurch, dass die Ausnehmung, ausgehend vom inneren Endabschnitt, ebenflächige Wandteile aufweist, läßt sich eine zumindest näherungsweis lineare Änderung der Biegefestigkeit über die Länge der Profilschenkel erreichen, so dass durch Wahl der Länge und/oder der Neigung dieser ebenflächigen Wandteile relativ zur Lötflächenebene ein optimales Biegeverhalten der Schenkel erreichbar ist.Furthermore, it is provided that the shape of the cross-section adjoining the soldering surfaces of the legs is optimized with regard to the avoidance of excessive stresses by special shaping of the recess, at least in the case of the profile strips adjoining the cooling medium. Characterized in that the recess, starting from the inner end portion having planar wall parts, an at least approximately linear change in the bending strength over the length of the profile legs can be achieved, so that by selecting the length and / or inclination of these planar wall parts relative to the Lötflächenebene an optimal Bending behavior of the legs is achievable.

Bei besonders vorteilhaften Ausführungsbeispielen ist die Ausnehmung in der Weise geformt, dass sich an die dritten ebenflächigen Wandteile vierte ebenflächige Wandteile anschließen, die zueinander leicht divergierend bis zur Öffnung der Ausnehmung verlaufen.In particularly advantageous embodiments, the recess is shaped in such a way that adjoin the third planar wall parts fourth planar wall parts which extend slightly divergent to the opening of the recess to each other.

Vorzugsweise können die ersten ebenflächigen Wandteile zueinander senkrechte Ebenen bilden, und die zweiten ebenflächigen Wandteile können mit den ersten ebenflächigen Wandteilen einen stumpfen Winkel einschließen, der vorzugsweise lediglich geringfügig größer als ein rechter Winkel ist. Damit entspricht die Querschnittsform der Ausnehmung in dem an das innere Ende angrenzenden Bereich in etwa einem zur Öffnung hin offenen Quadrat.Preferably, the first planar wall portions may form mutually perpendicular planes, and the second planar wall portions may include an obtuse angle with the first planar wall portions, which is preferably only slightly greater than a right angle. Thus, the cross-sectional shape of the recess in the region adjacent to the inner end corresponds approximately to a square open towards the opening.

Mit Vorteil kann die Anordnung so getroffen sein, dass die ersten ebenflächigen Wandteile miteinander und diese mit den zweiten ebenflächigen Wandteilen jeweils über gewölbte Wandstellen mit gleichem Krümmungsradius verbunden sind. Die zweiten ebenflächigen Wandteile sind mit den dritten ebenflächigen Wandteilen und diese mit den vierten ebenflächigen Wandteilen vorzugsweise auch jeweils über gewölbte Wandstellen mit gleichem, zweitem Krümmungsradius verbunden, der das Doppelte des ersten Krümmungsradius beträgt.Advantageously, the arrangement can be made such that the first planar wall parts are connected to each other and these with the second planar wall parts each over curved wall locations with the same radius of curvature. The second planar wall parts are connected to the third planar wall parts and these with the fourth planar wall parts preferably also each curved over wall locations with the same, second radius of curvature, which is twice the first radius of curvature.

Hinsichtlich der Dimensionierung der Engstellen relativ zur Querschnittsdicke der sich in Richtung auf die Öffnung anschließenden Schenkel ist die Anordnung vorzugsweise so getroffen, dass die Dicke des Querschnitts der Schenkel im Bereich der dritten ebenflächigen Wandteile in etwa das Doppelte der Dicke des Querschnittes an den Engstellen beträgt.With regard to the dimensioning of the bottlenecks relative to the cross-sectional thickness of the adjacent leg in the direction of the opening, the arrangement is preferably made so that the thickness of the cross section of the legs in the region of the third planar wall parts is approximately twice the thickness of the cross section at the bottlenecks.

Nachstehend ist die Erfindung anhand der Zeichnung im Einzelnen erläutert. Es zeigen:

Fig.1
in der Art einer explosionsartig auseinander gezogenen perspektivischen Schrägansicht lediglich einen Eckbereich eines Teils des Plattenpakets eines Ausführungsbeispiels des erfindungsgemäßen Wärmetauschers; und
Fig.2
eine vergrößert gezeichnete Seitenansicht lediglich einer Profilleiste zur Bildung eines Abstandhalters zwischen Platten des Pakets.
The invention is explained in detail below with reference to the drawing. Show it:
Fig.1
in the manner of an explosively exploded perspective oblique view only a corner region of a portion of the plate pack of an embodiment of the heat exchanger according to the invention; and
Fig.2
an enlarged drawn side view only a profile strip to form a spacer between plates of the package.

Die Fig.1 verdeutlicht ein Ausführungsbeispiel in Form eines in üblicher Plattenbauweise gefertigten Wärmetauschers mit einem Stapel ebener Platten 1, vorzugsweise aus einer Aluminiumlegierung, die in parallelen Ebenen verlaufen und Trennplatten für zwischen ihnen befindliche Durchströmbereiche bilden, wobei zwischen aufeinanderfolgenden Plattenpaaren im Wechsel jeweils ein Durchströmbereich 3 für das zu kühlende Medium, beispielsweise Hydrauliköl, und ein Durchströmbereich 5 für ein Kühlmedium, etwa Kühlluft, gebildet sind. Wie aus Fig.1 ersichtlich ist, erstrecken sich die Durchströmbereiche 3 und 5 im rechten Winkel zueinander. Der in der Zeichnung oben liegende Durchströmbereich 3 für das heiße Medium ist an zwei einander gegenüberliegenden Seiten durch in üblicher Weise gestaltete Abschlußleisten 7 geschlossen, zwischen denen sich der jeweilige Zuström- und Abströmbereich befindet, wobei zwischen den Abschlußleisten 7 in üblicher Weise Turbulatoren 9 in der Art von Lamellen vorgesehen sind.The Fig.1 illustrates an embodiment in the form of a conventional plate-type heat exchanger with a stack of flat plates 1, preferably made of an aluminum alloy, which run in parallel planes and separating plates for flow areas located between them form, between each successive plate pairs in alternation in each case a flow area 3 for the medium to be cooled, for example, hydraulic oil, and a flow area 5 for a cooling medium, such as cooling air, are formed. How out Fig.1 it can be seen, the flow-through areas 3 and 5 extend at right angles to each other. The lying in the drawing above Durchströmbereich 3 for the hot medium is closed on two opposite sides by conventionally designed end strips 7, between which the respective inflow and outflow is, between the end strips 7 in the usual way turbulators 9 in the Type of slats are provided.

Der Durchströmbereich 5 des Kühlmediums ist seitlich jeweils ebenfalls durch Abschlußleisten begrenzt, die die Abstandhalter zwischen dem jeweiligen Plattenpaar bilden und die als Profilleisten 11 mit besonderer, erfindungsgemäßer Gestaltung gebildet sind. Diese erfindungsgemäße Ausbildung ist anhand der Fig.2 näher erläutert.The Durchströmbereich 5 of the cooling medium is laterally also each bounded by end strips, which form the spacers between the respective plate pair and which are formed as profiled strips 11 with special, inventive design. This embodiment of the invention is based on the Fig.2 explained in more detail.

Wie ersichtlich, weisen die ebenfalls aus einer Aluminiumlegierung vorzugsweise stranggepressten Profilleisten 11 einen quader- oder blockförmigen Grundkörper 13, der dem Randbereich der Platten 1 zugewandt ist, eine Ausnehmung 15 in Form einer durchgehenden Längsnut sowie die Ausnehmung 15 beidseits begrenzende Schenkel 17 auf. Wie Fig.1 zeigt, ist die Ausnehmung 15 zum Durchströmbereich 5 hin offen, in dem sich Kühllamellen 19 befinden, die, ebenso wie die Turbulatoren 9 im Durchströmbereich 3, die effektive Wärmeübertragungsfläche vergrößern. Der innere Endabschnitt 23 (Fig.2) der Ausnehmung 15 befindet sich vom geschlossenen Ende 21 der Profilleiste 11 in einem Abstand, der etwas größer ist als der Abstand zwischen Endabschnitt 23 und Öffnung der Ausnehmung 15. Die ebenen oberen und unteren Endflächen der Profilleiste 11, also vom Grundkörper 13 bis zum Endbereich der Schenkel 17, bilden die Lötflächen 25 für die Verbindung des Plattenpakets. Am offenen Ende der Ausnehmung 15 befinden sich lippenartige Vorsprünge 27. Wie Fig.1 zeigt, stützen die Lippen 27 die Lamellen 5 vor dem Ende der Lötflächen 25 ab, so dass bei der Stapelbildung die Gefahr vermieden ist, dass Lamellenenden in den Spalt zwischen Platte 1 und Lötfläche 25 eindringen.As can be seen, the profile strips 11, which are also preferably extruded from an aluminum alloy, have a cuboid or block-shaped basic body 13 which faces the edge region of the plates 1, a recess 15 in the form of a continuous longitudinal groove and the recess 15 limbs 17 bordering on both sides. As Fig.1 shows, the recess 15 is open to the flow area 5, in which there are cooling fins 19, which, as well as the turbulators 9 in the flow area 3, increase the effective heat transfer area. The inner end portion 23 ( Fig.2 ) of the recess 15 is located from the closed end 21 of the profile strip 11 at a distance which is slightly greater than the distance between the end portion 23 and opening of the recess 15. The flat upper and lower end surfaces of the profile strip 11, ie from the base body 13 to the end the leg 17, form the solder surfaces 25 for the connection of the disk pack. At the open end of the recess 15 are lip-like projections 27. Like Fig.1 shows, support the lips 27, the fins 5 from the end of the solder pads 25, so that in the stacking the risk is avoided that lamella ends penetrate into the gap between the plate 1 and solder 25.

Die Ausnehmung 15 ist, von ihrem inneren Endabschnitt 23 ausgehend, durch ebenflächige Wandteile 29 begrenzt, die sich, zueinander divergierend und einen rechten Winkel einschließend, bis in die Nähe der betreffenden Lötfläche 25 erstrecken und dort eine Profilengstelle 31 des Profilquerschnitts der Schenkel 17 bilden. An die Engstelle 31 schließen sich zweite ebenflächige Wandteile 33 an, die zueinander konvergierend verlaufen und mit den ersten ebenflächigen Wandteilen 29 einen stumpfen Winkel einschließen, der wenig größer als ein rechter Winkel ist. Die Länge dieser zweiten ebenflächigen Wandteile 33 ist etwas geringer als die Länge der ersten ebenflächigen Wandteile 29, und an diese zweiten ebenflächigen Wandteile 33 schließen sich dritte ebenflächige Wandteile 35 an, die zu den Lötflächen 25 parallele Ebenen definieren und sich bis in die Nähe der Öffnung der Ausnehmung 15 erstrecken. An diese dritten ebenflächigen Wandteile 35 schließen sich wiederum vierte ebenflächige Wandteile 37 an, die sich zueinander leicht divergierend bis zur Öffnung der Ausnehmung 15 erstrecken. Die Verbindung der ersten ebenflächigen Wandteile 29 miteinander und mit den zweiten ebenflächigen Wandteilen 33 erfolgt jeweils über gewölbte Wandstellen 39 mit gleichem Krümmungsradius. Die Verbindung der zweiten ebenflächigen Wandteile 33 mit den dritten ebenflächigen Wandteilen 35 und dieser mit den vierten ebenflächigen Wandteilen 37 erfolgt ebenfalls über gewölbte Wandstellen 41, bei denen der Krümmungsradius jeweils das Doppelte des Krümmungsradius an den Wandstellen 39 beträgt.The recess 15 is, starting from its inner end portion 23, bounded by planar wall portions 29 which, diverging to each other and enclosing a right angle, extend into the vicinity of the relevant soldering surface 25 and form there a Profilengstelle 31 of the profile cross section of the legs 17. The constriction 31 is adjoined by second planar wall parts 33, which converge toward one another and enclose an obtuse angle with the first planar wall parts 29, which angle is slightly larger than a right angle. The length of these second planar wall portions 33 is slightly smaller than the length of the first planar wall portions 29, and these third planar wall portions 33 are followed by third planar wall portions 35 defining planes parallel to the soldering surfaces 25 and extending into the vicinity of the opening the recess 15 extend. At this third planar wall portions 35 in turn close fourth planar wall portions 37 which extend slightly divergent to the opening of the recess 15 to each other. The connection of the first planar wall portions 29 with each other and with the second planar wall portions 33 takes place in each case via curved wall portions 39 with the same radius of curvature. The connection of the second planar wall portions 33 with the third planar wall portions 35 and this with the fourth planar wall portions 37 also takes place over curved wall portions 41, in which the radius of curvature is twice the radius of curvature at the wall portions 39.

Die erfindungsgemäß vorgesehene Querschnittsform der Ausnehmung 15 resultiert in einer wirksamen Verringerung der betrieblichen Spannungsspitzen und der Gefahr einer Rissbildung an den Lötstellen. Bei dem Durchstrom des Kühlmittels durch die Ausnehmung 15 bilden die Engstellen 31 am Schenkelprofil den Ort des steilsten Temperaturgradienten. Gleichzeitig ist dies auch der Ort des geringsten Materialquerschnitts, so dass thermische Verformungen auf entsprechend begrenzte Materialpartien beschränkt sind. Da von den Engstellen 31 ausgehend sich die Profildicke der Schenkel 17 zur Öffnung hin auf eine Profildicke vergrößert, die etwa dem Doppelten an den Engstellen 31 entspricht, ergibt sich eine optimale Spannungsverteilung über den Bereich der Lötflächen 25.The inventively provided cross-sectional shape of the recess 15 results in an effective reduction of the operational stress peaks and the risk of cracking at the solder joints. In the passage of the coolant through the recess 15, the bottlenecks 31 on the leg profile form the location of the steepest temperature gradient. At the same time, this is also the location of the smallest material cross-section, so that thermal deformations are limited to correspondingly limited material parts. Since the profile thickness of the legs 17, starting from the constrictions 31, increases towards the opening to a profile thickness which corresponds approximately to twice the constrictions 31, an optimum stress distribution over the area of the soldering surfaces 25 results.

Die erfindungsgemäße Wärmetauschereinrichtung braucht auf das Gebiet der Fluidkühlung nicht eingeschränkt zu sein, sondern kann auch allgemein für die Kühlung gasförmiger Medien eingesetzt werden und hier insbesondere auch Ladeluftkühler (Dieselmotoren), sowie Nach- und Zwischenkühler (Kompressoren) mit einbeziehen. Die Temperaturdifferenzen (Kühlluft zu Medium) bei den dahingehenden Anwendungen liegen vergleichsweise noch wesentlich höher als vorstehend beschrieben.The heat exchanger device according to the invention need not be limited to the field of fluid cooling, but can also be used generally for the cooling of gaseous media and here in particular intercooler (diesel engines), as well as secondary and intercooler (compressors) to include. The temperature differences (cooling air to medium) in the pertinent applications are comparatively much higher than described above.

Claims (7)

  1. A heat exchanger, in particular for fluid cooling devices, that has a package of plane-parallel plates (1), flow regions (3, 5) for a hot medium and for a cooling medium being formed alternately between pairs of plates (1) lying one on top of the other, which regions are each bordered laterally by profile strips (7, 11) that keep the plates (1) spaced apart from one another and which form solder surfaces (25) which adjoin the plates (1), the profile strips (7, 11) at the flow regions (3, 5) of one medium and the other medium extending along edges of the plates (1) abutting one another at an angle, at least the profile strips (11) of the flow regions (5) of the cooling medium having a base body (13), two legs (17) extending from said base body along the solder surfaces (25), and between said legs a recess (15) which is open toward the adjacent flow region (5), and the recess (15) being bordered at least in the region adjacent to its inner end section (23) by planar wall parts (29), characterised in that the recess (15), starting from its inner end section (23), has diverging first planar wall parts (29) which extend to constrictions (31) of the cross section of the legs (17), converging second planar wall parts (33) which adjoin the constrictions (31), and third planar wall parts (35) which adjoin said second planar wall parts and which extend parallel to the solder surfaces (25) into the vicinity of the opening of the recess (15).
  2. The heat exchanger according to Claim 1, characterised in that fourth planar wall parts (37) which run slightly divergently to one another as far as the opening of the recess (15) adjoin the third planar wall parts (35).
  3. The heat exchanger according to any of the preceding claims, characterised in that the first planar wall parts (29) form planes which are perpendicular to one another.
  4. The heat exchanger according to any of the preceding claims, characterised in that the second planar wall parts (33) enclose an obtuse angle with the first planar wall parts (29).
  5. The heat exchanger according to any of the preceding claims, characterised in that the first planar wall parts (29) are connected to one another and to the second planar wall parts (33), in each case by means of arched wall sections (39) with the same first radius of curvature.
  6. The heat exchanger according to any of the preceding Claims 2-5, characterised in that the second planar wall parts (33) are connected to the third planar wall parts (35), and the latter are connected to the fourth planar wall parts (37), in each case by means of arched wall sections (41) with the same second radius of curvature which is twice the first radius of curvature.
  7. The heat exchanger according to any of the preceding claims, characterised in that the thickness of the cross section of the legs (17) in the region of the third planar wall parts (35) is approximately twice the thickness at the constrictions (31).
EP11757177.8A 2010-09-29 2011-09-09 Heat exchanger Not-in-force EP2622299B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010046913A DE102010046913A1 (en) 2010-09-29 2010-09-29 heat exchangers
US12/923,905 US8579021B2 (en) 2010-09-29 2010-10-13 Heat exchanger
PCT/EP2011/004545 WO2012052093A2 (en) 2010-09-29 2011-09-09 Heat exchanger

Publications (2)

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EP2622299A2 EP2622299A2 (en) 2013-08-07
EP2622299B1 true EP2622299B1 (en) 2017-04-12

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EP11757177.8A Not-in-force EP2622299B1 (en) 2010-09-29 2011-09-09 Heat exchanger

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US (1) US8579021B2 (en)
EP (1) EP2622299B1 (en)
CN (1) CN103097848B (en)
DE (1) DE102010046913A1 (en)
WO (1) WO2012052093A2 (en)

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EP3473961B1 (en) * 2017-10-20 2020-12-02 Api Heat Transfer, Inc. Heat exchanger
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US11168943B2 (en) 2018-10-12 2021-11-09 Api Heat Transfer Thermasys Corporation Channel fin heat exchangers and methods of manufacturing the same
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US11221186B2 (en) * 2019-07-18 2022-01-11 Hamilton Sundstrand Corporation Heat exchanger closure bar with shield
DE102020001455A1 (en) 2020-03-06 2021-09-09 Hydac Ag Heat exchanger

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Publication number Publication date
WO2012052093A3 (en) 2012-08-23
US8579021B2 (en) 2013-11-12
WO2012052093A2 (en) 2012-04-26
DE102010046913A1 (en) 2012-03-29
US20120073793A1 (en) 2012-03-29
EP2622299A2 (en) 2013-08-07
CN103097848A (en) 2013-05-08
CN103097848B (en) 2015-07-29

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