EP0867679A2 - Plate-like heat exchanger, more particularly oil cooler - Google Patents

Plate-like heat exchanger, more particularly oil cooler Download PDF

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Publication number
EP0867679A2
EP0867679A2 EP98890077A EP98890077A EP0867679A2 EP 0867679 A2 EP0867679 A2 EP 0867679A2 EP 98890077 A EP98890077 A EP 98890077A EP 98890077 A EP98890077 A EP 98890077A EP 0867679 A2 EP0867679 A2 EP 0867679A2
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EP
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Prior art keywords
flow
heat exchanger
troughs
parallel ribs
ribs
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Granted
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EP98890077A
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German (de)
French (fr)
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EP0867679A3 (en
EP0867679B1 (en
Inventor
Harald Ing. Bachinger
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KTM Kuehler GmbH
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KTM Kuehler GmbH
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    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • 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

Definitions

  • the invention is of course not based on the illustrated embodiment limited. So could the cooling oil through the flow troughs 1 with that formed from the crossing ribs Guide device to be directed.
  • the design of the Flow troughs 1 largely free, because the only thing that matters is that Trough bottoms 2 to be provided with parallel ribs, which alternate protrude on opposite sides of the tub bottoms 2 to within each second flow trough 1 a corresponding guide for this To receive flow trough 1 flowing medium.

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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

Deep-drawn guide devices comprising two crossing shares form parallel ribs (15), the height of which corresponds to half the counter-sided spacing of the bases of the troughs. The bases of the troughs have parallel ribs (15). The parallel ribs of directly adjacent heat exchanger plates are provided either on the facing sides of the heat exchanger plates or on the sides turned away from each other and extend exclusively into the flow paths for one of the two media.

Description

Die Erfindung bezieht sich auf einen Plattenwärmetauscher, insbesondere Ölkühler, mit mehreren ineinandergesteckten Strömungswannen, deren Böden je eine Wärmetauscherplatte zwischen zwei wärmeaustauschenden Medien sowie tiefgezogene Leiteinrichtungen aus zwei einander kreuzenden Scharen paralleler Rippen bilden, deren Höhe dem halben gegenseitigen Abstand der Böden entspricht.The invention relates to a plate heat exchanger, in particular Oil cooler, with several nested flow troughs, their bottoms one heat exchanger plate between two heat exchanging media as well as deep-drawn guidance systems made up of two intersecting shares form parallel ribs, the height of which is half the mutual distance Soils.

Bei üblichen Plattenwärmetauschern aus mehreren ineinandergesteckten Strömungswannen bilden die Strömungswannen jeweils einen durch den Boden der anschließenden Strömungswanne begrenzten Strömungsweg, so daß bei einer abwechselnden Beschickung der aufeinanderfolgenden Strömungswannen mit den beiden wärmeaustauschenden Medien die Wannenböden Wärmetauscherplatten bilden. Die Zu- und Ableitung der Medien erfolgt dabei durch die Wannenböden, die tiefgezogene Ansätze mit entsprechenden Durchtrittsöffnungen aufweisen. Die Anordnung ist dabei so getroffen, daß diese Ansätze die zwischen den Wannenböden gebildeten Strömungswege abwechselnd flüssigkeitsdicht durchsetzen, um die abwechselnde Beschickung dieser Strömungswege mit den beiden wärmeaustauschenden Medien sicherstellen zu können. Damit innerhalb der einzelnen Strömungswannen eine vorteilhafte Strömungsaufteilung zwischen den Medienzu- und -abflüssen durch die tiefgezogenen Ansätze sichergestellt wird, werden in die einzelnen Strömungswannen Turbulenzbleche eingelegt. Diese Turbulenzbleche bilden aus der Blechebene wellenartig ausgebogene, durch parallele Schlitze begrenzte Laschen, die entsprechende Strömungsdurchtritte quer zu den einzelnen Laschenreihen ergeben, so daß ein in Richtung der Laschenreihen angeströmtes Turbulenzblech eine entsprechende Querverteilung des Strömungsmediums mit sich bringt, allerdings mit einer erheblichen Vergrößerung des Strömungswiderstandes in Richtung der Laschenreihen. Um den mit dem Einsatz gesonderter Turbulenzbleche vermehrten Aufwand herabzusetzten, ist es bekannt (DE 195 19 312 A1), die Böden der Strömungswannen mit tiefgezogenen Noppen zu versehen, die über die Grundfläche der Strömungswannen verteilt eine Leiteinrichtung für das die jeweilige Strömungswanne durchströmende Medium bilden, das zufolge dieser ein Turbulenzblech ersetzenden Leitnoppen ebenfalls verwirbelt wird, allerdings nur unzureichend. Wegen der begrenzten Tiefzieheigenschaften von höherfestem Aluminium, das insbesondere für Ölkühler im Fahrzeugbau eingesetzt wird, werden die für die Wasserführung vorgesehenen Strömungswannen mit einer entsprechend geringeren Tiefe als die das Öl aufnehmenden Strömungswannen ausgeführt, die mit herkömmlichen Turbulenzblechen versehen werden. Der gegenüber den Strömungswannen für die Ölführung verminderte Strömungsquerschnitt der Strömungswannen für das Kühlwasser muß jedoch als nachteilig angesehen werden.With conventional plate heat exchangers made of several nested Flow troughs each form a flow trough through the floor the subsequent flow trough limited flow path, so that at an alternating loading of the successive flow troughs with the two heat-exchanging media, the tub bottoms of the heat exchanger plates form. The media are fed in and out by Tub floors, the deep-drawn approaches with appropriate through openings exhibit. The arrangement is such that these approaches flow paths alternately liquid-tight formed between the trough bottoms enforce the alternate loading of these flow paths to be able to ensure with the two heat exchanging media. An advantageous flow distribution within the individual flow troughs between the media inflows and outflows through the deep-drawn Approaches are ensured, turbulence plates in the individual flow troughs inserted. These turbulence sheets form waves from the sheet level bent tabs delimited by parallel slots, the corresponding Flow passages result across the individual rows of tabs, so that a flow in the direction of the rows of tabs has a corresponding turbulence plate Cross-distribution of the flow medium entails, however with a significant increase in flow resistance in the direction of Rows of tabs. To the increased with the use of separate turbulence plates To reduce effort, it is known (DE 195 19 312 A1), the floors of the Flow troughs with deep-drawn knobs to be provided over the base area the flow troughs distribute a guide device for each Form flow medium flowing through this, according to this one Turbulence plate replacing guide knobs is also swirled, but only insufficient. Because of the limited deep-drawing properties of higher strength Aluminum, which is used in particular for oil coolers in vehicle construction, the flow troughs provided for the water supply with a correspondingly less deep than the flow troughs that hold the oil executed, which are provided with conventional turbulence plates. Of the compared to the flow troughs for the oil flow reduced flow cross-section the flow troughs for the cooling water must, however, be disadvantageous be considered.

Schließlich ist es bekannt (WO 93/00563 A1), die Böden der Strömungswannen mit tiefgezogene Leiteinrichtungen aus zwei einander kreuzenden Scharen paralleler Rippen zu versehen, um einerseits zu steigern und anderseits den Strömungswiderstand für die beiden durch den Wannenboden voneinander getrennten, wärmeaustauschenden Medien zu erhöhen. Zu diesem Zweck weisen die Böden der Strömungswannen jeweils zwei einander kreuzende Scharen von parallelen Rippen auf, die scharenweise nach entgegengesetzten Seiten über den Wannenboden vorragen, und zwar um den halben gegenseitigen Abstand der Wannenböden. Die Anordnung ist dabei so getroffen, daß die zwischen zwei benachbarten Wannenböden gegeneinander paarweise vorragenden, parallelen Rippen einander entlang ihres Rückens berühren, so daß diese paarweise gegeneinander vorragenden Rippen zwischen den benachbarten Wannenböden Trennwände bilden, die für den Mediendurchtritt lediglich im Kreuzungsbereich mit den dazu querverlaufenden, auf die andere Bodenseite vorstehenden Rippen unterbrochen sind. Aus diesem Grunde ergeben sich vor allem parallele Strömungskanäle zwischen den die Trennwände bildenden Rippen, was im Zusammenwirken mit den begrenzten Strömungsdurchtritten durch diese Trennwände ungünstige Strömungsverhältnisse schafft, und zwar im Strömungsbereich beider Medien. Außerdem ergibt sich eine aufwendige Bodenform, weil die Bodenbereiche zwischen den einander kreuzenden Rippenscharen zusätzlich unterschiedlich weit aus der Bodenebene ausgeformt und mit Sicken versehen sind, was hohe Anforderungen an das Tiefziehverhalten des Werkstoffes der Strömungswannen stellt.Finally, it is known (WO 93/00563 A1), the bottoms of the flow troughs with deep-drawn guide devices made of two intersecting shares parallel ribs to increase on the one hand and on the other hand the Flow resistance for the two of them through the bottom of the tub separate, heat-exchanging media. To this end the bottoms of the flow troughs each intersect two Flocks of parallel ribs, which flock to opposite Project sides over the bottom of the tub, by half each other Distance of the tub floors. The arrangement is such that that between two neighboring bathtub floors in pairs protruding, parallel ribs touch each other along their backs, so that these ribs protruding in pairs against each other between the neighboring ones Tub floors form partitions that are only for the media passage in the intersection area with the transverse to the other bottom side protruding ribs are interrupted. For this reason arise from all parallel flow channels between those forming the partitions Ribs, which interact with the limited flow passages creates unfavorable flow conditions through these partitions, namely in Flow area of both media. In addition, there is an elaborate shape of the bottom, because the bottom areas between the crossing ribs additionally shaped differently from the floor level and with Beads are provided, which places high demands on the deep-drawing behavior of the Material of the flow troughs.

Der Erfindung liegt somit die Aufgabe zugrunde, einen Plattenwärmetauscher, insbesondere einen Ölkühler, der eingangs geschilderten Art so auszugestalten, daß für eines der beiden wärmeaustauschenden Medien die Strömungsverteilung in den Strömungswannen durch Turbulenzbleche erzwungen, für das andere Medium aber in vorteilhafter Weise durch die tiefgezogenen Leiteinrichtungen der Wannenböden sichergestellt wird.The invention is therefore based on the object of a plate heat exchanger, in particular to design an oil cooler of the type described at the beginning, that the flow distribution for one of the two heat-exchanging media forced in the flow troughs by turbulence plates for that other medium but advantageously by the deep-drawn guide devices the tub floors are ensured.

Die Erfindung löst die gestellte Aufgabe dadurch, daß die Böden der Stömungswannen jeweils lediglich eine Schar paralleler Rippen aufweisen und daß die einander kreuzenden Scharen paralleler Rippen unmittelbar benachbarter Wärmetauscherplatten entweder auf der einander zugekehrten Seite oder auf der voneinander abgekehrten Seite der Wärmetauscherplatten vorgesehen sind und ausschließlich in die Strömungswege für eines der beiden Medien ragen.The invention solves this problem in that the bottoms of the flow troughs each have only a set of parallel ribs and that the crosses of parallel ribs immediately adjacent Heat exchanger plates either on the side facing each other or on the opposite side of the heat exchanger plates are provided and only protrude into the flow paths for one of the two media.

Da zufolge dieser Maßnahmen die einen Strömungswannen eine Schar paralleler Rippen aufweisen, die in den Strömungsweg dieser Strömungswannen vorragen, während die anderen Strömungswannen Rippen bilden, die auf der der Wanne abgekehrten Seite des Wannenbodens verlaufen, erhält man durch ein abwechselndes Ineinanderstecken dieser unterschiedlichen Strömungswannen im Bereich des Strömungsweges jeder zweiten Strömungswanne eine wirksame Leiteinrichtung für das durch diese Wannen strömende Medium aus einander kreuzenden Scharen von parallelen Rippen, die lediglich im Bereich der Kreuzungsstellen aneinander anliegen und aufgrund der sich dadurch ergebenden Gitterstruktur für eine vorteilhafte Turbulenz des zwischen ihnen strömenden Mediums sorgen, ohne den Strömungswiderstand übermäßig zu erhöhen, weil ja die Rippen mit Ausnahme der Kreuzungsbereiche lediglich die halbe Höhe der Strömungswannen sperren. Da die Rippenhöhe nur dem halben gegenseitigen Abstand der Böden unmittelbar ineinandergesteckter Strömungswannen entspricht und die Rippen ausschließlich auf einer Seite des sonst ebenen Bodens vorragen, können erheblich geringere Anforderungen an die Tiefzieheigenschaften des Wannenwerkstoffes gestellt werden, was den Einsatz auch höherfester Aluminiumlegierungen zur Herstellung solcher Wärmetauscher erlaubt, insbesondere wenn auch die tiefgezogenen Ansätze zur Führung der Medien zwischen den einzelnen Strömungswannen im Bereich der unmittelbar ineinandergesteckten Strömungswannen gegeneinander paarweise vorragen und eine den Rippen entsprechende Höhe aufweisen.As a result of these measures the one flow troughs a flock parallel Have ribs in the flow path of these flow troughs protrude, while the other flow troughs form ribs on the the side of the tub floor facing away from the tub can be obtained by an alternating insertion of these different flow troughs in the area of the flow path of every second flow trough effective guide device for the medium flowing through these troughs intersecting bands of parallel ribs that are only in the area of the crossing points lie against each other and because of this resulting lattice structure for advantageous turbulence between them flowing medium without causing excessive flow resistance increase, because the ribs with the exception of the crossing areas only the Block half the height of the flow troughs. Because the rib height is only half mutual spacing of the bottoms of directly merged flow troughs corresponds and the ribs only on one side of the otherwise projecting flat floor can make considerably less demands on the Thermoforming properties of the tub material are made, what use also higher strength aluminum alloys for the manufacture of such heat exchangers allowed, especially if the deep-drawn approaches to the management of Media between the individual flow troughs in the immediate area protrude into each other in pairs and have a height corresponding to the ribs.

Um eine besonders gleichmäßige Verteilung und Durchwirbelung des einen Mediums mit Hilfe der Leiteinrichtung zu erhalten, können die beiden Scharen paralleler Rippen einander unter einem Winkel von 90° kreuzen, wie dies an sich bekannt ist.A particularly even distribution and swirling of one To obtain medium with the help of the guide device, the two groups parallel ribs cross each other at an angle of 90 ° like this is known.

In der Zeichnung ist der Erfindungsgegenstand beispielsweise dargestellt. Es zeigen

Fig. 1
einen erfindungsgemäßen Plattenwärmetauscher in einer Draufsicht auf eine Strömungswanne,
Fig. 2
diesen Plattenwärmetauscher in einem Schnitt nach der Linie II-II der Fig. 1 in einem größeren Maßstab, und
Fig. 3
einen Schnitt nach der Linie III-III der Fig. 1 durch zwei ineinandergesteckte Strömungswannen ebenfalls in einem größeren Maßstab.
The subject matter of the invention is shown in the drawing, for example. Show it
Fig. 1
a plate heat exchanger according to the invention in a plan view of a flow pan,
Fig. 2
this plate heat exchanger in a section along the line II-II of Fig. 1 on a larger scale, and
Fig. 3
a section along the line III-III of Fig. 1 by two nested flow troughs also on a larger scale.

Wie das dargestellte Ausführungsbeispiel zeigt, ist der Plattenwärmetauscher aus einzelnen, ineinandergesteckten Strömungswannen 1 aufgebaut, die jeweils aus einem Boden 2 mit einem hochgezogenen, umlaufenden Rand 3 gebildet werden, der mit einer Erweiterung 4 den Rand 3 des Bodens 2 der jeweils benachbarten Strömungswanne 1 übergreift. Diese Wannenböden 2 weisen einander paarweise zugeordnete Durchtrittsöffnungen 5 und 6 für die wärmetauschenden Medien, beispielsweise Öl und Wasser, auf. Die Anordnung ist dabei so getroffen, daß die Durchtrittsöffnungen 5 und 6 im Bereich von tiefgezogenen Ansätzen 7 liegen, deren Höhe dem halben Abstand a zwischen den benachbarten Wannenböden 2 entspricht. Da die Durchtrittsöffnungen 5 und 6 kleiner als der Boden dieser Ansätze 7 sind, ergibt sich zwischen den Böden der gegeneinander vorragenden Ansätze 7 benachbarter Wärmetauscherplatten 2 eine die dichte Verbindung der Ansätze 7 unterstützende flächige Anlage um den jeweiligen Öffnungsrand. Wie der Fig. 2 entnommen werden kann, sind die Ansätze 7 im Bereich fluchtender Durchtrittsöffnungen 5 und 6 abwechselnd auf entgegengesetzten Plattenseiten vorgesehen, so daß sich über die Ansätze 7 jeweils ein flüssigkeitsdichter Durchtritt durch jede zweite Strömungswanne 1 ergibt. Zusätzlich müssen die Ansätze 7 für den Durchtritt des einen Mediums gegenüber den Ansätzen 7 für den Durchtritt des anderen Mediums auf gegenüberliegenden Plattenseiten liegen.As the illustrated embodiment shows, the plate heat exchanger made up of individual, nested flow troughs 1, each formed from a bottom 2 with a raised peripheral edge 3 be with an extension 4 the edge 3 of the bottom 2 of each overlaps adjacent flow trough 1. These trough floors 2 face each other Passages 5 and 6 assigned in pairs for the heat exchangers Media, such as oil and water. The arrangement is there made so that the passage openings 5 and 6 in the area of deep-drawn Approaches 7 are located, the height of which is half the distance a between the adjacent ones Tub floors 2 corresponds. Because the openings 5 and 6 are smaller than the bottom of these approaches 7, there is between the bottoms of mutually projecting approaches 7 of adjacent heat exchanger plates 2 a flat system supporting the tight connection of the approaches 7 the respective opening edge. As can be seen from FIG. 2, the Approaches 7 in the area of aligned openings 5 and 6 alternately opposite plate sides are provided so that the approaches 7th one liquid-tight passage through each second flow trough 1 results. In addition, the approaches 7 for the passage of one medium compared to approaches 7 for the passage of the other medium on opposite Sides of the plate.

Wird beispielsweise das zu kühlende Öl durch die Durchtrittsöffnungen 5 und das die Ölwärme aufnehmende Wasser durch die Durchtrittsöffnungen 6 geleitet, wobei das Öl jeweils vom Zulauf 8 zum Ablauf 9 und das Wasser im Gegenstrom vom Zulauf 10 zum Ablauf 11 die Strömungswannen 1 durchströmen, so ergibt sich für das Öl eine durch die Pfeile 12 und für das Wasser eine durch die Pfeile 13 in der Fig. 2 angedeutete Strömung, die hinsichtlich ihrer Verteilung über die Wärmetauscherplatten von der Anordnung entsprechender Leiteinrichtungen in den einzelnen Strömungswannen 1 abhängt. Während für die Ölströmung übliche Turbulenzbleche 14 eingesetzt werden, wird die Leiteinrichtung in den dazwischenliegenden Strömungswannen 1 durch tiefgezogene Rippen 15 in den Wannenböden 2 gebildet. Die Anordnung ist dabei so getroffen, daß die parallelen Rippen 15 der einen Strömungswanne 1 die Schar der ebenfalls parallelen Rippen 15 der unmittelbar anschließenden Strömungswanne vorzugsweise unter einem Winkel von 90° kreuzen, wie dies der Fig. 1 entnommen werden kann. Da die Rippen 15 jeweils in den Strömungsweg für das Kühlwasser vorragen und eine Höhe h aufweisen, die dem halben Abstand a der Wannenböden 2 entspricht, liegen die gegeneinander vorragenden Rippen 15 im Bereich der Kreuzungsstellen aneinander an. Dies bringt im Zusammenhang mit dem durchgehenden Rippenverlauf zwischen den Kreuzungsstellen eine vorteilhafte Durchwirbelung des Kühlwassers mit sich, was wohl keiner näheren Erklärung bedarf. Durch die Rippen 15 wird außerdem die Oberfläche der Wärmetauscherplatte vergrößert, so daß insgesamt vorteilhafte Wärmeaustauschbedingungen sichergestellt werden können.For example, the oil to be cooled through the openings 5 and the water absorbing the oil heat is passed through the passage openings 6, the oil from the inlet 8 to the outlet 9 and the water in countercurrent flow through the flow troughs 1 from the inlet 10 to the outlet 11, so results for the oil by the arrows 12 and one for the water by the Arrows 13 in Fig. 2 indicated flow, with regard to their distribution on the heat exchanger plates from the arrangement of appropriate control devices depends in the individual flow troughs 1. While for the oil flow usual turbulence plates 14 are used, the guide device in the flow troughs 1 in between by deep-drawn ribs 15 formed in the tub bottoms 2. The arrangement is such that the parallel ribs 15 of a flow trough 1 also the coulter parallel ribs 15 of the immediately adjacent flow trough preferably Cross at an angle of 90 °, as shown in FIG. 1 can be. Since the ribs 15 each in the flow path for the cooling water protrude and have a height h, which is half the distance a Trough bottoms 2, the mutually projecting ribs 15 in the area of the crossing points. This is related with the continuous course of the ribs between the crossing points advantageous swirling of the cooling water with it, which probably no closer Explanation needed. Through the ribs 15, the surface of the Heat exchanger plate enlarged, so that overall advantageous heat exchange conditions can be ensured.

Die Erfindung ist selbstverständlich nicht auf das dargestellte Ausführungsbeispiel beschränkt. So könnte auch das zukühlende Öl durch die Strömungswannen 1 mit der aus den einander kreuzenden Rippenscharen gebildeten Leiteinrichtung geleitet werden. Außerdem ist die konstruktive Ausgestaltung der Strömungswannen 1 weitgehend frei, weil es ja lediglich darauf ankommt, die Wannenböden 2 mit parallelen Rippenscharen zu versehen, die abwechselnd auf entgegengesetzten Seiten der Wannenböden 2 vorragen, um innerhalb jeder zweiten Strömungswanne 1 eine entsprechende Leiteinrichtung für das diese Strömungswanne 1 durchströmende Medium zu erhalten.The invention is of course not based on the illustrated embodiment limited. So could the cooling oil through the flow troughs 1 with that formed from the crossing ribs Guide device to be directed. In addition, the design of the Flow troughs 1 largely free, because the only thing that matters is that Trough bottoms 2 to be provided with parallel ribs, which alternate protrude on opposite sides of the tub bottoms 2 to within each second flow trough 1 a corresponding guide for this To receive flow trough 1 flowing medium.

Claims (2)

Plattenwärmetauscher, insbesondere Ölkühler, mit mehreren ineinandergesteckten Strömungswannen (1), deren Böden (2) je eine Wärmetauscherplatte zwischen zwei wärmeaustauschenden Medien sowie tiefgezogene Leiteinrichtungen aus zwei einander kreuzenden Scharen paralleler Rippen (15) bilden, deren Höhe (h) dem halben gegenseitigen Abstand (a) der Böden (2) entspricht, dadurch gekennzeichnet, daß die Böden (2) der Stömungswannen (1) jeweils lediglich eine Schar paralleler Rippen (15) aufweisen und daß die einander kreuzenden Scharen paralleler Rippen (15) unmittelbar benachbarter Wärmetauscherplatten entweder auf der einander zugekehrten Seite oder auf der voneinander abgekehrten Seite der Wärmetauscherplatten vorgesehen sind und ausschließlich in die Strömungswege für eines der beiden Medien ragen.Plate heat exchanger, especially oil cooler, with several nested Flow troughs (1), the bottoms (2) of which each have a heat exchanger plate between two heat-exchanging media and deep-drawn control devices form from two intersecting sets of parallel ribs (15), the Height (h) corresponds to half the mutual distance (a) of the floors (2), thereby characterized in that the bottoms (2) of the flow troughs (1) each have only a set of parallel ribs (15) and that the each other crossing sets of parallel ribs (15) of immediately adjacent heat exchanger plates either on the side facing each other or on the side facing each other opposite side of the heat exchanger plates are provided and only project into the flow paths for one of the two media. Plattenwärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die beiden Scharen paralleler Rippen (15) einander unter einem Winkel von 90° kreuzen.Plate heat exchanger according to claim 1, characterized in that the two groups of parallel ribs (15) at an angle of 90 ° to each other cross.
EP19980890077 1997-03-25 1998-03-23 Plate-like heat exchanger, more particularly oil cooler Expired - Lifetime EP0867679B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT51597 1997-03-25
AT51597A AT407920B (en) 1997-03-25 1997-03-25 PLATE HEAT EXCHANGERS, ESPECIALLY OIL COOLERS
AT515/97 1997-03-25

Publications (3)

Publication Number Publication Date
EP0867679A2 true EP0867679A2 (en) 1998-09-30
EP0867679A3 EP0867679A3 (en) 1999-12-01
EP0867679B1 EP0867679B1 (en) 2003-09-24

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ID=3492648

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980890077 Expired - Lifetime EP0867679B1 (en) 1997-03-25 1998-03-23 Plate-like heat exchanger, more particularly oil cooler

Country Status (4)

Country Link
EP (1) EP0867679B1 (en)
AT (1) AT407920B (en)
DE (1) DE59809679D1 (en)
ES (1) ES2209101T3 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2795165A1 (en) * 1999-06-21 2000-12-22 Valeo Thermique Moteur Sa PLATE HEAT EXCHANGER, IN PARTICULAR OIL COOLER FOR MOTOR VEHICLES
FR2795167A1 (en) * 1999-06-21 2000-12-22 Valeo Thermique Moteur Sa PLATE HEAT EXCHANGER, ESPECIALLY FOR COOLING A MOTOR VEHICLE OIL
DE19930805A1 (en) * 1999-07-03 2001-01-11 Zahnradfabrik Friedrichshafen Heat exchanger has coolant feed/return connection on connector plate on side of heat exchanger remote from housing, distance pieces bridging distance between plate and housing
DE19917761C1 (en) * 1999-12-07 2001-01-18 Peter Rehberg Plate heat exchanger has stacked rectangular heat exchanger plates provided with flow openings at corners for each transfer medium enclosed by flat ring on one side and raised teeth on opposite side of plate
DE19959780B4 (en) * 1999-04-12 2004-11-25 Rehberg, Peter, Dipl.-Ing. Plate heat exchangers
EP1526350A2 (en) 2003-10-21 2005-04-27 Modine Manufacturing Company Plate heat exchanger
DE102005034305A1 (en) * 2005-07-22 2007-01-25 Behr Gmbh & Co. Kg Plate element for a plate cooler
WO2007073304A1 (en) * 2005-12-22 2007-06-28 Alfa Laval Corporate Ab Heat transfer plate for plate heat exchanger with even load distribution in port regions
FR2910119A1 (en) * 2006-12-18 2008-06-20 Renault Sas Heat exchanger for internal combustion engine, has stack of plates defining openings, where openings present different geometries such that circulation paths induce identical friction losses on coolant and oil

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010063141A1 (en) 2010-12-15 2012-06-21 Mahle International Gmbh heat exchangers
DE102011112512B4 (en) 2011-09-07 2013-06-06 Umicore Ag & Co. Kg Process for the production of plate heat exchangers

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WO1993000563A1 (en) 1991-06-24 1993-01-07 Alfa-Laval Thermal Ab Plate heat exchanger
DE19519312A1 (en) 1995-05-26 1996-11-28 Laengerer & Reich Gmbh & Co Plate-type heat-exchanger

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FR998449A (en) * 1945-10-03 1952-01-18 Construction method for heat exchanger
GB867869A (en) * 1957-06-14 1961-05-10 Rolls Royce Improvements in or relating to heat exchangers
SE7508256L (en) * 1975-07-18 1977-01-19 Munters Ab Carl WAY TO PRODUCE A HEAT EXCHANGER BODY FOR RECOVERY EXCHANGERS
US4932469A (en) * 1989-10-04 1990-06-12 Blackstone Corporation Automotive condenser
IT1263611B (en) * 1993-02-19 1996-08-27 Giannoni Srl PLATE HEAT EXCHANGER

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
WO1993000563A1 (en) 1991-06-24 1993-01-07 Alfa-Laval Thermal Ab Plate heat exchanger
DE19519312A1 (en) 1995-05-26 1996-11-28 Laengerer & Reich Gmbh & Co Plate-type heat-exchanger

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19959780B4 (en) * 1999-04-12 2004-11-25 Rehberg, Peter, Dipl.-Ing. Plate heat exchangers
FR2795165A1 (en) * 1999-06-21 2000-12-22 Valeo Thermique Moteur Sa PLATE HEAT EXCHANGER, IN PARTICULAR OIL COOLER FOR MOTOR VEHICLES
FR2795167A1 (en) * 1999-06-21 2000-12-22 Valeo Thermique Moteur Sa PLATE HEAT EXCHANGER, ESPECIALLY FOR COOLING A MOTOR VEHICLE OIL
EP1063488A1 (en) * 1999-06-21 2000-12-27 Valeo Thermique Moteur Plate heat exchanger, especially for cooling oil of motor vehicles
EP1063486A1 (en) * 1999-06-21 2000-12-27 Valeo Thermique Moteur Plate heat exchanger, especially oil cooler for motor vehicles
DE19930805A1 (en) * 1999-07-03 2001-01-11 Zahnradfabrik Friedrichshafen Heat exchanger has coolant feed/return connection on connector plate on side of heat exchanger remote from housing, distance pieces bridging distance between plate and housing
DE19930805C2 (en) * 1999-07-03 2002-11-14 Zahnradfabrik Friedrichshafen heat exchangers
DE19917761C1 (en) * 1999-12-07 2001-01-18 Peter Rehberg Plate heat exchanger has stacked rectangular heat exchanger plates provided with flow openings at corners for each transfer medium enclosed by flat ring on one side and raised teeth on opposite side of plate
EP1526350A2 (en) 2003-10-21 2005-04-27 Modine Manufacturing Company Plate heat exchanger
DE10348803B4 (en) 2003-10-21 2024-03-14 Modine Manufacturing Co. Housing-less plate heat exchanger
DE102005034305A1 (en) * 2005-07-22 2007-01-25 Behr Gmbh & Co. Kg Plate element for a plate cooler
WO2007073304A1 (en) * 2005-12-22 2007-06-28 Alfa Laval Corporate Ab Heat transfer plate for plate heat exchanger with even load distribution in port regions
WO2007073305A1 (en) * 2005-12-22 2007-06-28 Alfa Laval Corporate Ab Means for plate heat exchanger
EP1963770A1 (en) * 2005-12-22 2008-09-03 Alfa Laval Corporate AB Means for plate heat exchanger
CN101346597B (en) * 2005-12-22 2010-10-06 阿尔法拉瓦尔股份有限公司 Heat transfer plate for plate heat exchanger with even load distribution in port regions
US8109326B2 (en) 2005-12-22 2012-02-07 Alfa Laval Corporate Ab Heat transfer plate for plate heat exchanger with even load distribution in port regions
CN101346598B (en) * 2005-12-22 2012-07-11 阿尔法拉瓦尔股份有限公司 Means for plate heat exchanger
EP1963770A4 (en) * 2005-12-22 2013-05-22 Alfa Laval Corp Ab Means for plate heat exchanger
FR2910119A1 (en) * 2006-12-18 2008-06-20 Renault Sas Heat exchanger for internal combustion engine, has stack of plates defining openings, where openings present different geometries such that circulation paths induce identical friction losses on coolant and oil

Also Published As

Publication number Publication date
EP0867679A3 (en) 1999-12-01
ATA51597A (en) 2000-11-15
DE59809679D1 (en) 2003-10-30
AT407920B (en) 2001-07-25
EP0867679B1 (en) 2003-09-24
ES2209101T3 (en) 2004-06-16

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