EP1571407B1 - Plate heat exchanger - Google Patents

Plate heat exchanger Download PDF

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Publication number
EP1571407B1
EP1571407B1 EP05003752.2A EP05003752A EP1571407B1 EP 1571407 B1 EP1571407 B1 EP 1571407B1 EP 05003752 A EP05003752 A EP 05003752A EP 1571407 B1 EP1571407 B1 EP 1571407B1
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EP
European Patent Office
Prior art keywords
heat exchanger
plate
furrows
plates
surface side
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.)
Expired - Fee Related
Application number
EP05003752.2A
Other languages
German (de)
French (fr)
Other versions
EP1571407A2 (en
EP1571407A3 (en
Inventor
Roland Dipl.-Ing. Strähle (FH)
Daniel Dipl.-Ing. Borst (FH)
Frank Dr. Rer.Nat. Vetter
Herbert Marschner
Daniela Welchner
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Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
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Publication date
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Publication of EP1571407A2 publication Critical patent/EP1571407A2/en
Publication of EP1571407A3 publication Critical patent/EP1571407A3/en
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Publication of EP1571407B1 publication Critical patent/EP1571407B1/en
Expired - Fee Related legal-status Critical Current
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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
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/10—Particular layout, e.g. for uniform temperature distribution

Definitions

  • the invention relates to a plate heat exchanger, consisting of first and second heat exchanger plates with at least four openings for two media, the heat exchanger plates being alternately stacked between a base plate and a cover plate in such a way that the openings form collecting or distribution channels which pass through the stack of heat exchanger plates. wherein there are inlets or outlets from the collecting or distribution channels to flow channels between the heat exchanger plates in which the heat transfer takes place, and wherein the flow channels for the one medium from one surface side of the first heat exchanger plate and from the spaced one surface side of the second heat exchanger plate are limited.
  • Such a plate heat exchanger is based on the unpublished European application with the publication number EP 14 00 772 A2 which belongs to the same applicant.
  • This plate-type heat exchanger is suitable for heat transfer between media under relatively high pressure, as is the case, for example, in an air conditioning circuit on the refrigerant side.
  • a suitable, in particular pressure-stable, design of the collecting and distribution channels for the refrigerant, for example for CO 2 was described in the document specified. However, the formation of the flow channels for the CO 2 gas was neither shown nor described there.
  • the preamble of claim 1 also goes from WO 01 / 88454A1 forth.
  • the heat exchanger plates of one type are provided with deep-drawn knobs in order to generate turbulence.
  • the knobs are formed on the entire bottom of the plates, also around the four openings.
  • the one from the WO 03/054468 A1 Known heat transfer device is also part of an air conditioning circuit. All heat exchanger plates of this device are provided with a structure, which could be assessed as too complex from a manufacturing point of view. In addition, this known device could be regarded as spatially too large (large building).
  • the object of the invention is to propose a plate heat exchanger which can be used and is inexpensive to produce for media under high pressure, for example for heat exchange between the refrigerant in air conditioning systems and a liquid.
  • the flow channels for the one medium are formed by the connection of the first heat exchanger plate embossed on one surface side and a surface side of an unembossed or likewise embossed second heat exchanger plate, and the flow channels for the other medium are through the other unembossed surface side of the embossed first heat exchanger plate and through that spaced other surface side of the unembossed or also embossed second heat exchanger plate.
  • the plate heat exchanger preferably consists of one-sided embossed and non-embossed heat exchanger plates.
  • This particularly preferred embodiment also ensures that the plate thicknesses of the two types of heat exchanger plates can be significantly different from one another, ie the non-embossed heat exchanger plates are preferably designed to be considerably thinner than the embossed heat exchanger plates, which leads to material and weight savings.
  • This advantage was not necessarily to be expected for plate heat exchangers for media under high pressure.
  • the stamping of the flow channels permits their arbitrarily shaped design to achieve the desired heat exchange effects, which cannot be achieved with extrusion processes known in the prior art.
  • the impressions are preferably made using a Stamping tool made on a press. They are preferably created by cold forming, which is quite possible, especially if the plates are made from a suitable aluminum sheet. Production using embossing rollers is fundamentally not excluded.
  • the two heat exchanger plates to one another and between them to form the flow channels for one medium, preferably for the high-pressure medium, in the form of impressions and on the other hand to arrange the two heat exchanger plates at a distance from one another, the flow channels for the other medium are formed.
  • the impressions represent structures made of groove-like furrows, which are provided in a surface side of one type of heat exchanger plate and which are formed by flat contact with a heat exchanger plate of the other type to form flow channels for the one medium.
  • the groove-like furrows provide a hydraulic connection from one opening of the one medium to the other opening of the same medium.
  • the openings, or the collection and distribution channels thus formed in the stack of heat exchanger plates are arranged within an essential section of the heat exchanger plate provided with the groove-like furrows (structures).
  • the plate heat exchanger according to the invention is advantageously also suitable for use as a water / oil heat exchanger.
  • the cross-sectional size or the hydraulic diameter of the flow channels can be changed for the respective application.
  • Preferred hydraulic diameters of the flow channels for the refrigerant are approximately between 0.5 and 1.0 mm.
  • the hydraulic diameter of the flow channels is above these values when used as a water / oil heat exchanger.
  • the plate heat exchanger shown is used for heat exchange between the refrigerant CO 2 (or another refrigerant) and the coolant of a motor vehicle engine and is integrated in the refrigerant circuit of the air conditioning system and in the coolant circuit in a known and therefore not shown manner.
  • Trough-shaped heat exchanger plates 4a and 4b were produced from the aluminum sheets, which have a simply beveled edge 24 and which are each provided with four openings 5 .
  • the same shape was also provided for the cover plate 3 and for the base plate 2 .
  • the base plate 2 is designed without openings 5 , since the CO 2 gas and the cooling liquid are provided on and off the cover plate 3 .
  • the heat exchanger plates 4a, 4b are assembled into a stack.
  • fins 13 through which the coolant can flow were inserted in the flow channels 11 in a known manner, which ensure efficient heat exchange.
  • the lamellae 13 also contribute to greater compressive strength, since they are soldered to the surface sides mentioned.
  • the slats 13 were only hinted at.
  • the edge 24 of the plates 4a, 4b points upwards.
  • the four openings 5 of the heat exchanger plates 4a, 4b stacked one on top of the other form four collecting or distribution channels 6 , 7 , 8 , 9 which pass vertically through the stack.
  • connection stub 6.1 show that the cooling liquid in the distribution channel 6 of the plate heat exchanger via the Connection stub 6.1 flows in and leaves the same via the collecting duct 7 and the connection stub 7.1 after flowing through the flow ducts 11 .
  • the connecting pieces 8.1 and 9.1 for the refrigerant are special high-pressure fittings.
  • every second flow channel 10 is hydraulically connected to the distributor - and to the collecting channel 8 , 9 . Since the flow channels 10 and 11 formed by the heat exchanger plates 4a , 4b alternate, the first flow channels 11 are hydraulically connected to the distributor and to the collecting channel 6 , 7 . It is from the Fig. 3 It can be seen that the heat exchanger plates 4a are formed around the openings 5 with passages 15 which are produced by shaping and block the hydraulic connection from the distribution channel 8 and the collecting channel 9 into the flow channel 11 . Instead of the passages 15 , rings could also be inserted.
  • the connecting flanges have been formed from the cover plate 3 by forming.
  • the flange plate on the base plate 2 likewise, the flange plate also having a reducer 31 , in which the lower end 32 of a body 12 is soldered, which provides the required pressure stability.
  • a body 12 which in this case relates only to a preferred exemplary embodiment , is located both in the distribution channel 8 and in the collecting channel 9 , wherein in the Fig.
  • the body 12 can be dispensed with because the substantially lower pressures there allow this.
  • Fig. 1 and 3rd show that the flow channels 10 for the CO 2 through the connection of the one surface side of an embossed heat exchanger plate 4a with the one surface side of an unembossed heat exchanger plate 4b are formed, and that the flow channels 11 for the cooling liquid are delimited by the other surface side of the embossed heat exchanger plate 4a and by the other spaced surface side of the unembossed heat exchanger plate 4b .
  • the Fig. 2 shows a view of an embossed heat exchanger plate 4a , which (in this exemplary embodiment) is the thicker of the two heat exchanger plates 4a , 4b .
  • Structures 20 can be seen in the surface side of the embossed heat exchanger plates 4a that are formed as groove-like furrows 20 .
  • This surface side lies in the Fig. 1 Embodiment shown flat on the surface side of an embossed and essentially also flat heat exchanger plate 4b , whereby the groove-like furrows 20 form the flow channels 10 for the CO 2 .
  • the embossed surface side of the plates 4a points upwards and the second heat exchanger plate 4b lies flat against it with its one surface side. In the Fig. 4 the foothills of the flow channels 10 are clearly visible.
  • Fig. 2 ostensibly gives the impression of an ornamental design. However, this is aimed at achieving intended technical effects.
  • the section 21 of the heat exchanger plates 4a covered with the structures 20 should be as large as possible, and on the other hand, this entire section 21 should be used as much as possible for heat exchange.
  • the best possible heat exchange is achieved in that the same pressure loss should always be present in all flow channels 10 through a clever choice of the design and the length of each flow channel. It is also a uniform distribution of the flow channels 10 intended over the entire section 21, which is why one has been provided both to a vertical symmetrical VA as well as to a horizontal axis HA of the design portion 21st As a result, the length of all flow channels 10 is approximately the same.
  • the flow channels 10 are of a discrete type.
  • the parallel flow channels 10 should preferably not be in a short-circuit-like hydraulic connection with one another.
  • the additional metallic connections described above are provided on regions 22 and regions 25 .
  • a hexagonal shape of the heat exchanger plates 4a , 4b was selected. From the Fig. 2 it can be seen that this special shape is related to the required size of the regions 25 and the larger openings 5 for the cooling liquid, or has its causes therein.
  • the openings 5 for the cooling liquid lie outside the essential section 21 , whereas the openings 5 for the CO 2 are arranged inside the latter.
  • edges 24 on the thicker heat exchanger plates 4a are significantly shorter than the edges 24 on the thinner heat exchanger plates 4b . This could be done because, on the one hand, there are pressures on the coolant side that allow this construction and, on the other hand, the high-pressure CO 2 gas flows on the side on which there is a durable flat metallic connection between the thin heat exchanger plate 4b and the thicker one Heat exchanger plate 4a is present. This leads to an extremely compact design of the Plate heat exchanger and for further material and weight savings, which should not go unmentioned with a large number of such plates 4a , 4b .
  • the 7 and 8 show a view of the two surface sides of the heat transfer plates 104a and 104b , which are metallically connected to form the flow channels 110 in a second exemplary embodiment.
  • one of the plates 104a or 104b is rotated through 180 ° about the axis HA , so that the surface sides shown come to lie against one another.
  • FIG. 2 shows an example of two connected heat exchanger plates 104a , 104b , which illustrates the above.
  • the structures 120 lying on the left or right of the vertical axis of symmetry VA were divided between the two heat exchanger plates 104a and 104b .
  • both plates 104a , 104b can have the same sheet thickness.
  • the symmetry only relates to the arrangement of the structures 120 and the two openings 105 .
  • the outer shape of the plates shown is not symmetrical in the two representations, but should preferably be symmetrical.
  • the walls 230 between the furrows of one plate 204a are metallically connected to the walls 230 of the other plate 204b . Further modifications, not shown, of such exemplary embodiments can be made.
  • Fig. 9 it is shown how the shape of the groove-like furrows 20 , which form the flow channels 10 , has changed after the soldering process has been completed.
  • the illustration shows the preferred embodiment with the different thickness heat exchanger plates 4a and 4b .
  • the embossing produces groove-like furrows 20 with a width of approximately 0.8 mm and a depth of approximately 1.0 mm.
  • the solder flows into the grooves 50 , so that an approximately elliptical or circular cross section is formed in each groove-like groove 20 .
  • This ideal cross-sectional shape ensures the lowest possible pressure loss along each flow channel 10 .
  • the depth and the width of the groove-like furrows 20 can be adapted to the required conditions.

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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)

Description

Die Erfindung betrifft einen Plattenwärmeübertrager, bestehend aus ersten und zweiten Wärmeübertragerplatten mit mindestens vier Durchbrüchen für zwei Medien, wobei zwischen einer Grundplatte und einer Deckplatte die Wärmeübertragerplatten im Wechsel so gestapelt sind, dass die Durchbrüche durch den Stapel von Wärmeübertragerplatten hindurchgehende Sammel - oder Verteilerkanäle bilden, wobei von den Sammel - oder Verteilerkanälen Zu - bzw. Ausgänge zu Strömungskanälen zwischen den Wärmeübertragerplatten vorhanden sind, in denen die Wärmeübertragung stattfindet, und wobei die Strömungskanäle für das eine Medium von der einen Oberflächenseite der ersten Wärmeübertragerplatte sowie von der beabstandeten einen Oberflächenseite der zweiten Wärmeübertragerplatte begrenzt sind.The invention relates to a plate heat exchanger, consisting of first and second heat exchanger plates with at least four openings for two media, the heat exchanger plates being alternately stacked between a base plate and a cover plate in such a way that the openings form collecting or distribution channels which pass through the stack of heat exchanger plates. wherein there are inlets or outlets from the collecting or distribution channels to flow channels between the heat exchanger plates in which the heat transfer takes place, and wherein the flow channels for the one medium from one surface side of the first heat exchanger plate and from the spaced one surface side of the second heat exchanger plate are limited.

Ein solcher Plattenwärmeübertrager geht aus der nicht vorveröffentlichten europäischen Anmeldung mit der Veröffentlichungsnummer EP 14 00 772 A2 hervor, die derselben Anmelderin gehört. Dieser Plattenwärmeübertrager ist zur Wärmeübertragung zwischen unter relativ hohem Druck stehende Medien geeignet, wie er beispielsweise in einem Klimatisierungskreislauf auf der Kältemittelseite vorherrscht. In dem angegebenen Dokument wurde eine geeignete, insbesondere druckstabile, Ausbildung der Sammel - und Verteilerkanäle für das Kältemittel, beispielsweise für CO2, beschrieben. Die Ausbildung der Strömungskanäle für das CO2 - Gas wurde dort jedoch weder gezeigt noch beschrieben.Such a plate heat exchanger is based on the unpublished European application with the publication number EP 14 00 772 A2 which belongs to the same applicant. This plate-type heat exchanger is suitable for heat transfer between media under relatively high pressure, as is the case, for example, in an air conditioning circuit on the refrigerant side. A suitable, in particular pressure-stable, design of the collecting and distribution channels for the refrigerant, for example for CO 2 , was described in the document specified. However, the formation of the flow channels for the CO 2 gas was neither shown nor described there.

Der Oberbegriff des Anspruchs 1 geht auch aus der WO 01/88454A1 hervor. In dieser Referenz werden die Wärmeübertragerplatten der einen Art mit tiefgezogenen Noppen versehen, um Turbulenzen zu erzeugen. Die Noppen sind auf dem gesamten Boden der Platten ausgebildet, auch um die vier Durchbrüche herum.The preamble of claim 1 also goes from WO 01 / 88454A1 forth. In this reference, the heat exchanger plates of one type are provided with deep-drawn knobs in order to generate turbulence. The knobs are formed on the entire bottom of the plates, also around the four openings.

Die aus der WO 03/054468 A1 bekannte Vorrichtung zur Wärmeübertragung ist ebenfalls ein Bestandteil eines Klimatisierungskreislaufes. Sämtliche Wärmeübertragerplatten dieser Vorrichtung sind mit einer Struktur versehen, was aus fertigungstechnischer Sicht als zu aufwendig beurteilt werden könnte. Außerdem könnte diese bekannte Vorrichtung als räumlich noch zu ausladend (großbauend) angesehen werden.The one from the WO 03/054468 A1 Known heat transfer device is also part of an air conditioning circuit. All heat exchanger plates of this device are provided with a structure, which could be assessed as too complex from a manufacturing point of view. In addition, this known device could be regarded as spatially too large (large building).

Diesbezüglich vorteilhafter scheint der aus WO 01 / 69157 A2 bekannte Wärmeübertrager für eine Fahrzeugklimaanlage zu sein. Dort ist jedoch ansonsten ein sogenannter Zwischenwärmeübertrager beschrieben, in dem Kältemittel höherer Temperatur mit demselben Kältemittel niedrigerer Temperatur im Wärmeaustausch steht. Deshalb sind dort in sämtlichen Strömungskanälen des Wärmeübertragers feine Kanäle vorgesehen, die , wie es dort heißt, mittels auftragender oder abtragender Fertigungsverfahren auf bzw. in den Wärmeübertagerplatten hergestellt werden sollen.In this regard it seems more advantageous WO 01/69157 A2 to be known heat exchangers for a vehicle air conditioning system. However, there is otherwise a so-called intermediate heat exchanger described, in which higher temperature refrigerant with the same lower temperature refrigerant exchanges heat stands. For this reason, fine channels are provided in all flow channels of the heat exchanger, which, as is stated there, are to be produced on or in the heat exchanger plates by means of application or removal manufacturing processes.

Weiterer Stand der Technik geht aus der GB 1 468 514 sowie aus der WO 91/ 13308A1 hervor.Another state of the art is based on the GB 1 468 514 as well as from the WO 91/13308A1 forth.

Die Aufgabe der Erfindung besteht darin, einen Plattenwärmeübertrager vorzuschlagen, der für unter hohem Druck stehende Medien, beispielsweise zum Wärmeaustausch zwischen dem Kältemittel in Klimaanlagen und einer Flüssigkeit, einsetzbar und kostengünstig herstellbar ist.The object of the invention is to propose a plate heat exchanger which can be used and is inexpensive to produce for media under high pressure, for example for heat exchange between the refrigerant in air conditioning systems and a liquid.

Diese Aufgabe wird bei dem im Oberbegriff des Anspruchs 1 beschriebenen Plattenwärmeübertrager durch die im Kennzeichen aufgeführten Merkmale erfindungsgemäß gelöst.This object is achieved according to the invention in the plate heat exchanger described in the preamble of claim 1 by the features listed in the characterizing part.

Die Strömungskanäle für das eine Medium sind durch die Verbindung der einen auf einer Oberflächenseite geprägten ersten Wärmeübertragerplatte und einer Oberflächenseite einer ungeprägten oder ebenfalls geprägten zweiten Wärmeübertragerplatte gebildet, und die Strömungskanäle für das andere Medium sind durch die andere ungeprägte Oberflächenseite der geprägten ersten Wärmeübertragerplatte und durch die beabstandete andere Oberflächenseite der ungeprägten oder ebenfalls geprägten zweiten Wärmeübertragerplatte gebildet worden. Bei der umformtechnischen Herstellung der metallischen Wärmeübertragerplatten können die Einprägungen in einem Zug ausgebildet werden, wodurch die kostengünstige Herstellung erreicht wird. Vorzugsweise besteht der Plattenwärmeübertrager aus einseitig geprägten und aus ungeprägten Wärmeübertragerplatten. Durch diese besonders bevorzugte Ausbildung wird ferner erreicht, dass die Plattendicken der beiden Arten von Wärmeübertragerplatten deutlich verschieden voneinander sein können, d. h., vorzugsweise sind die ungeprägten Wärmeübertragerplatten wesentlich dünner ausgebildet, als die geprägten Wärmeübertragerplatten, was zu einer Material - und Gewichtsersparnis führt. Dieser Vorteil ist bei Plattenwärmeübertragern für unter Hochdruck stehende Medien nicht unbedingt zu erwarten gewesen. Ferner gestattet das Einprägen der Strömungskanäle deren beliebig geformte Ausbildung, zur Erzielung gewünschter Wärmetauscheffekte, was mit im Stand der Technik bekannten Extrusionsverfahren nicht erreicht werden kann. Die Einprägungen werden vorzugsweise mittels eines Prägewerkzeuges auf einer Presse hergestellt. Sie werden vorzugsweise mittels Kaltumformung geschaffen, was gut möglich ist, insbesondere dann, wenn die Platten aus einem entsprechenden Aluminiumblech hergestellt werden. Die Herstellung mittels Prägewalzen ist grundsätzlich nicht ausgeschlossen.The flow channels for the one medium are formed by the connection of the first heat exchanger plate embossed on one surface side and a surface side of an unembossed or likewise embossed second heat exchanger plate, and the flow channels for the other medium are through the other unembossed surface side of the embossed first heat exchanger plate and through that spaced other surface side of the unembossed or also embossed second heat exchanger plate. When the metal heat exchanger plates are manufactured using metal forming technology, the impressions can be formed in one go, as a result of which cost-effective production is achieved. The plate heat exchanger preferably consists of one-sided embossed and non-embossed heat exchanger plates. This particularly preferred embodiment also ensures that the plate thicknesses of the two types of heat exchanger plates can be significantly different from one another, ie the non-embossed heat exchanger plates are preferably designed to be considerably thinner than the embossed heat exchanger plates, which leads to material and weight savings. This advantage was not necessarily to be expected for plate heat exchangers for media under high pressure. Furthermore, the stamping of the flow channels permits their arbitrarily shaped design to achieve the desired heat exchange effects, which cannot be achieved with extrusion processes known in the prior art. The impressions are preferably made using a Stamping tool made on a press. They are preferably created by cold forming, which is quite possible, especially if the plates are made from a suitable aluminum sheet. Production using embossing rollers is fundamentally not excluded.

Erfindungsgemäß ist also vorgesehen, die zwei Wärmeübertragerplatten einerseits flächig miteinander zu verbinden und dazwischen die Strömungskanäle für das eine Medium, vorzugsweise für das Hochdruckmedium, in Form von Einprägungen auszubilden und andererseits die zwei Wärmeübertagerplatten mit einem Abstand zueinander anzuordnen, wobei in dem Abstand die Strömungskanäle für das andere Medium ausgebildet sind.According to the invention, it is therefore provided on the one hand to connect the two heat exchanger plates to one another and between them to form the flow channels for one medium, preferably for the high-pressure medium, in the form of impressions and on the other hand to arrange the two heat exchanger plates at a distance from one another, the flow channels for the other medium are formed.

Die Einprägungen stellen Strukturen aus rillenartigen Furchen dar, die in einer Oberflächenseite einer Art Wärmeübertragerplatten vorgesehen sind und die durch flächige Anlage mit einer Wärmeübertragerplatte der anderen Art zu Strömungskanälen für das eine Medium ausgebildet sind. Die rillenartigen Furchen stellen eine hydraulische Verbindung von dem einen Durchbruch des einen Mediums zum anderen Durchbruch desselben Mediums zur Verfügung. Dazu sind die Durchbrüche, bzw. die damit im Stapel der Wärmeübertragerplatten gebildeten Sammel - und Verteilerkanäle, innerhalb eines mit den rillenartigen Furchen (Strukturen) versehenen wesentlichen Abschnitts der Wärmeübertragerplatte angeordnet. Durch diese Maßnahme wird erreicht, dass die an den Verteiler - bzw. Sammelkanälen vorgesehenen Vorkehrungen zur hydraulischen Trennung der unterschiedlichen Medien vergleichsweise einfach sein können, denn diese sind nur auf einer Medienseite notwendig, in diesem Fall an den Durchbrüchen, die sich innerhalb des erwähnten Abschnitts befinden. Die erwähnten Vorkehrungen können darin bestehen, dass diese Durchbrüche mit Durchzügen ausgebildet sein können, die jeweils die Strömungskanäle für das andere Medium absperren.The impressions represent structures made of groove-like furrows, which are provided in a surface side of one type of heat exchanger plate and which are formed by flat contact with a heat exchanger plate of the other type to form flow channels for the one medium. The groove-like furrows provide a hydraulic connection from one opening of the one medium to the other opening of the same medium. For this purpose, the openings, or the collection and distribution channels thus formed in the stack of heat exchanger plates, are arranged within an essential section of the heat exchanger plate provided with the groove-like furrows (structures). This measure ensures that the provisions for the hydraulic separation of the different media provided on the distributor or collecting channels can be comparatively simple, since these are only necessary on one media side, in this case the openings which are within the mentioned section are located. The precautions mentioned can consist in the fact that these openings can be formed with passages that block off the flow channels for the other medium.

Es wurde festgestellt, dass sich der erfindungsgemäße Plattenwärmeübertrager in vorteilhafter Weise auch für den Einsatz als Wasser / Öl - Wärmeübertrager eignet. Die Querschnittsgröße bzw. der hydraulische Durchmesser der Strömungskanäle kann für den jeweiligen Einsatzfall verändert werden. Bevorzugte hydraulische Durchmesser der Strömungskanäle für das Kältemittel liegen etwa zwischen 0,5 und 1,0 mm. Der hydraulische Durchmesser der Strömungskanäle liegt bei Verwendung als Wasser / Öl - Wärmeübertrager oberhalb dieser Werte.It was found that the plate heat exchanger according to the invention is advantageously also suitable for use as a water / oil heat exchanger. The cross-sectional size or the hydraulic diameter of the flow channels can be changed for the respective application. Preferred hydraulic diameters of the flow channels for the refrigerant are approximately between 0.5 and 1.0 mm. The hydraulic diameter of the flow channels is above these values when used as a water / oil heat exchanger.

Wegen weiterer Merkmale und Vorteile der Erfindung wird auf die abhängigen Ansprüche und auf die folgende Beschreibung von Ausführungsbeispielen anhand der Zeichnungen verwiesen.For further features and advantages of the invention, reference is made to the dependent claims and to the following description of exemplary embodiments with reference to the drawings.

Die beiliegenden Figuren zeigen Folgendes:

  • Fig. 1 Vertikalschnitt durch einen Plattenwärmeübertrager eines ersten Ausführungsbeispiels; der teilweise durch die Kühlmittelseite gelegt wurde;
  • Fig. 2 Blick auf eine geprägte Wärmeübertragerplatte;
  • Fig. 3 Vertikalschnitt durch den Plattenwärmetauscher auf der Seite des Kältemittels;
  • Fig. 4 Vergrößerter Ausschnitt aus der Fig. 3;
  • Fig. 5 Prinzip eines zweiten Ausführungsbeispiels;
  • Fig. 6 - 8 Wärmeübertragerplatten eines dritten Ausführungsbeispiels;
  • Fig. 9 Strömungskanäle nach der Lötverbindung zweier Wärmeübertragerplatten;
The attached figures show the following:
  • Fig. 1 Vertical section through a plate heat exchanger of a first embodiment; that was partially laid through the coolant side;
  • Fig. 2 View of an embossed heat exchanger plate;
  • Fig. 3 Vertical section through the plate heat exchanger on the side of the refrigerant;
  • Fig. 4 Enlarged section from the Fig. 3 ;
  • Fig. 5 Principle of a second embodiment;
  • 6 - 8 Heat exchanger plates of a third embodiment;
  • Fig. 9 Flow channels after the solder connection of two heat exchanger plates;

Der gezeigte Plattenwärmeübertrager dient dem Wärmeaustausch zwischen dem Kältemittel CO2 (oder ein anderes Kältemittel) und der Kühlflüssigkeit eines Kraftfahrzeugmotors und wird in bekannter und deshalb nicht gezeigter Weise sowohl in den Kältemittelkreislauf der Klimaanlage als auch in den Kühlflüssigkeitskreislauf integriert.The plate heat exchanger shown is used for heat exchange between the refrigerant CO 2 (or another refrigerant) and the coolant of a motor vehicle engine and is integrated in the refrigerant circuit of the air conditioning system and in the coolant circuit in a known and therefore not shown manner.

Er besteht im gezeigten Ausführungsbeispiel komplett aus mit Lot beschichteten Aluminiumblechen von sechseckiger Gestalt, wobei die Gestalt zweckentsprechend ausgewählt werden kann. Aus den Aluminiumblechen wurden wannenförmige Wärmeübertragerplatten 4a und 4b hergestellt, die einen einfach abgekanteten Rand 24 aufweisen und die mit jeweils vier Durchbrüchen 5 versehen sind. Die gleiche Gestalt wurde auch für die Deckplatte 3 und für die Grundplatte 2 vorgesehen. Die Grundplatte 2 ist in diesem Ausführungsbeispiel ohne Durchbrüche 5 ausgebildet, da die Zu - und Abführung des CO2 - Gases und der Kühlflüssigkeit an der Deckplatte 3 vorgesehen ist. Die Wärmeübertragerplatten 4a, 4b werden zu einem Stapel zusammengefügt. Zwischen den Wärmeübertragerplatten 4a, 4b bzw. zwischen deren beabstandeten Oberflächenseiten wurden in den Strömungskanälen 11 in bekannter Art und Weise von der Kühlflüssigkeit durchströmbare Lamellen 13 eingefügt, die für einen effizienten Wärmeaustausch sorgen. Die Lamellen 13 tragen außerdem zu einer größeren Druckfestigkeit bei, denn sie sind mit den erwähnten Oberflächenseiten verlötet. In den Figuren wurden die Lamellen 13 lediglich angedeutet. In den Ausführungsbeispielen zeigt der Rand 24 der Platten 4a, 4b nach oben. Die vier Durchbrüche 5 der aufeinander gestapelten Wärmeübertragerplatten 4a, 4b bilden vier vertikal durch den Stapel hindurchgehende Sammel - bzw. Verteilerkanäle 6, 7, 8, 9. Die Strömungspfeile in der Fig. 1 zeigen, dass die Kühlflüssigkeit in den Verteilerkanal 6 des Plattenwärmetauschers über den Anschlussstutzen 6.1 einströmt und über den Sammelkanal 7 und den Anschlussstutzen 7.1, nach Durchströmung der Strömungskanäle 11, denselben wieder verlässt. Analog strömt gemäß der Fig. 3 bei 8 das Kältemittel über einen Anschlusstutzen 8.1 in den Plattenwärmeübertrager ein, welches nach Durchströmung der Strömungskanäle 10 den Plattenwärmeübertrager bei 9 bzw. 9.1 wieder verlässt. Die Anschlussstutzen 8.1 und 9.1 für das Kältemittel sind spezielle Hochdruckfittinge.In the exemplary embodiment shown, it consists completely of aluminum sheets of hexagonal shape coated with solder, wherein the shape can be selected appropriately. Trough-shaped heat exchanger plates 4a and 4b were produced from the aluminum sheets, which have a simply beveled edge 24 and which are each provided with four openings 5 . The same shape was also provided for the cover plate 3 and for the base plate 2 . In this exemplary embodiment, the base plate 2 is designed without openings 5 , since the CO 2 gas and the cooling liquid are provided on and off the cover plate 3 . The heat exchanger plates 4a, 4b are assembled into a stack. Between the heat exchanger plates 4a, 4b or between their spaced surface sides, fins 13 through which the coolant can flow were inserted in the flow channels 11 in a known manner, which ensure efficient heat exchange. The lamellae 13 also contribute to greater compressive strength, since they are soldered to the surface sides mentioned. In the figures, the slats 13 were only hinted at. In the exemplary embodiments, the edge 24 of the plates 4a, 4b points upwards. The four openings 5 of the heat exchanger plates 4a, 4b stacked one on top of the other form four collecting or distribution channels 6 , 7 , 8 , 9 which pass vertically through the stack. The flow arrows in the Fig. 1 show that the cooling liquid in the distribution channel 6 of the plate heat exchanger via the Connection stub 6.1 flows in and leaves the same via the collecting duct 7 and the connection stub 7.1 after flowing through the flow ducts 11 . Analog flows according to the Fig. 3 at 8 the refrigerant via a connection piece 8.1 into the plate heat exchanger, which leaves the plate heat exchanger at 9 or 9.1 after flowing through the flow channels 10 . The connecting pieces 8.1 and 9.1 for the refrigerant are special high-pressure fittings.

Im Ausführungsbeispiel ist jeder zweite Strömungskanal 10 hydraulisch mit dem Verteiler - und mit dem Sammelkanal 8, 9 verbunden. Da sich die durch die Wärmeübertragerplatten 4a, 4b gebildeten Strömungskanäle 10 und 11 abwechseln, sind die ersten Strömungskanäle 11 hydraulisch mit dem Verteiler - und mit dem Sammelkanal 6, 7 verbunden. Es ist aus der Fig. 3 erkennbar, dass die Wärmeübertragerplatten 4a um die Durchbrüche 5 herum mit durch Umformung hergestellten Durchzügen 15 ausgebildet sind, die die hydraulische Verbindung vom Verteilerkanal 8 und dem Sammelkanal 9 in den Strömungskanal 11 hinein blockieren. Anstelle der Durchzüge 15 könnten auch Ringe eingelegt werden.In the exemplary embodiment, every second flow channel 10 is hydraulically connected to the distributor - and to the collecting channel 8 , 9 . Since the flow channels 10 and 11 formed by the heat exchanger plates 4a , 4b alternate, the first flow channels 11 are hydraulically connected to the distributor and to the collecting channel 6 , 7 . It is from the Fig. 3 It can be seen that the heat exchanger plates 4a are formed around the openings 5 with passages 15 which are produced by shaping and block the hydraulic connection from the distribution channel 8 and the collecting channel 9 into the flow channel 11 . Instead of the passages 15 , rings could also be inserted.

Die Anschlussflansche sind aus der Deckplatte 3 durch Umformung gebildet worden. Die Flanschplatte an der Grundplatte 2 ebenfalls, wobei auch die Flanschplatte ein Reduzierstück 31 aufweist, in dem das untere Ende 32 eines Körpers 12 eingelötet ist, der die benötigte Druckstabiltität zur Verfügung stellt. Im Einzelnen wurde das in der nicht vorveröffentlichten europäischen Anmeldung EP 14 00 772 A2 beschrieben, die zum diesbezüglichen Verständnis herangezogen werden kann. Ein solcher, hier lediglich ein bevorzugtes Ausführungsbeispiel betreffender Körper 12, befindet sich sowohl im Verteilerkanal 8 als auch im Sammelkanal 9, wobei in der Fig. 3 lediglich der stabartige Körper 12 im Sammelkanal 9 eingezeichnet wurde, um die Einzelheiten der Strömungskanäle 10 deutlich zu machen, die in den Verteiler - bzw. Sammelkanal 8, 9 münden und auf die weiter unten genauer eingegangen wird. Zwischen dem Körper 12 und dem Rand des Verteiler - bzw. Sammelkanals 8, 9 befindet sich ein Ringspalt 40, durch den das CO2 strömen kann.The connecting flanges have been formed from the cover plate 3 by forming. The flange plate on the base plate 2 likewise, the flange plate also having a reducer 31 , in which the lower end 32 of a body 12 is soldered, which provides the required pressure stability. Specifically, this was in the unpublished European application EP 14 00 772 A2 described, which can be used to understand this. Such a body 12, which in this case relates only to a preferred exemplary embodiment , is located both in the distribution channel 8 and in the collecting channel 9 , wherein in the Fig. 3 only the rod-like body 12 was drawn in the collecting duct 9 in order to make clear the details of the flow ducts 10 which open into the distributor or collecting duct 8 , 9 and which will be discussed in more detail below. Between the body 12 and the edge of the distributor or collecting channel 8 , 9 there is an annular gap 40 through which the CO 2 can flow.

Insbesondere bei einem Ölkühler kann auf den Körper 12 verzichtet werden, weil die dort herrschenden wesentlich niedrigeren Drücke das gestatten.In the case of an oil cooler in particular, the body 12 can be dispensed with because the substantially lower pressures there allow this.

Die Fig. 1 und 3 zeigen, dass die Strömungskanäle 10 für das CO2 durch die Verbindung der einen Oberflächenseite einer geprägten Wärmeübertragerplatte 4a mit der einen Oberflächenseite einer ungeprägten Wärmeübertragerplatte 4b gebildet sind, und dass die Strömungskanäle 11 für die Kühlflüssigkeit von der anderen Oberflächenseite der geprägten Wärmeübertragerplatte 4a sowie von der anderen beabstandeten Oberflächenseite der ungeprägten Wärmeübertragerplatte 4b begrenzt sind.The Fig. 1 and 3rd show that the flow channels 10 for the CO 2 through the connection of the one surface side of an embossed heat exchanger plate 4a with the one surface side of an unembossed heat exchanger plate 4b are formed, and that the flow channels 11 for the cooling liquid are delimited by the other surface side of the embossed heat exchanger plate 4a and by the other spaced surface side of the unembossed heat exchanger plate 4b .

Die Fig. 2 zeigt eine Ansicht auf eine geprägte Wärmeübertragerplatte 4a, die (in diesem Ausführungsbeispiel) die dickere der beiden Wärmeübertragerplatten 4a, 4b ist. Es sind Strukturen 20 in der gezeigten Oberflächenseite der geprägten Wärmeübertragerplatten 4a erkennbar, die als rillenartige Furchen 20 ausgebildet sind. Diese Oberflächenseite liegt im in der Fig. 1 gezeigten Ausführungsbeispiel flächig an der Oberflächenseite einer ungeprägten und im wesentlichen ebenfalls ebenen Wärmeübertragerplatte 4b an, wodurch die rillenartigen Furchen 20 die Strömungskanäle 10 für das CO2 ausbilden. Wie die Fig. 1 und 4 deutlich machen, zeigt die geprägte Oberflächenseite der Platten 4a jeweils nach oben und die zweite Wärmeübertragerplatte 4b liegt mit ihrer einen Oberflächenseite flächig daran an. In der Fig. 4 sind die Ausläufer der Strömungskanäle 10 gut zu erkennen.The Fig. 2 shows a view of an embossed heat exchanger plate 4a , which (in this exemplary embodiment) is the thicker of the two heat exchanger plates 4a , 4b . Structures 20 can be seen in the surface side of the embossed heat exchanger plates 4a that are formed as groove-like furrows 20 . This surface side lies in the Fig. 1 Embodiment shown flat on the surface side of an embossed and essentially also flat heat exchanger plate 4b , whereby the groove-like furrows 20 form the flow channels 10 for the CO 2 . As the Fig. 1 and 4th make clear, the embossed surface side of the plates 4a points upwards and the second heat exchanger plate 4b lies flat against it with its one surface side. In the Fig. 4 the foothills of the flow channels 10 are clearly visible.

Ein Blick auf die Fig. 2 erweckt vordergründig den Eindruck einer ornamentalen Gestaltung. Diese ist jedoch auf die Erzielung beabsichtigter technischer Wirkungen gerichtet. So soll zum einen der mit den Strukturen 20 bedeckte Abschnitt 21 der Wärmeübertragerplatten 4a so groß wie möglich sein und zum anderen soll dieser gesamte Abschnitt 21 so gut wie möglich zum Wärmeaustausch ausgenutzt werden. Der bestmögliche Wärmeaustausch wird dadurch erreicht, dass in allen Strömungskanälen 10, durch geschickte Wahl der Gestaltung und der Länge eines jeden Strömungskanals, möglichst immer der gleiche Druckverlust vorhanden sein soll. Es ist auch eine möglichst gleichmäßige Verteilung der Strömungskanäle 10 über den gesamten Abschnitt 21 beabsichtigt, weshalb eine sowohl zu einer vertikalen VA als auch zu einer horizontalen Achse HA symmetrische Gestaltung des Abschnitts 21 vorgesehen wurde. Das führt dazu, dass die Länge aller Strömungskanäle 10 in etwa gleich ist. Den extrem hohen Drücken von bis zu 300 bar wurde dadurch Rechnung getragen, dass innerhalb des wesentlichen Abschnitts 21 zahlreiche inselartige Regionen 22 ohne Einprägungen belassen wurden, in denen eine metallische Verbindung mit der anderen Wärmeübertragerplatte 4b vorgenommen werden kann, die im Übrigen wesentlich dünner ist als die Wärmeübertragerplatte 4a. Eine metallische Verbindung mit der anderen Wärmeübertragerplatte 4b ist natürlich auch an den Wänden 30 zwischen den rillenartigen Furchen 20 vorhanden, die jedoch alleine, wie die Erfinder erkannt haben, wegen der relativ kleinen Flächenanteile, keine ausreichende Festigkeit zur Verfügung stellen kann. Darüber hinaus gibt es außerhalb des wesentlichen Abschnitts 21 liegende Gebiete 25, die ebenfalls flächig mit der anderen Wärmeübertragerplatte 4b verbunden werden. Die Erfinder betonen aber, dass eine exzellente metallische Verbindung zwischen den Wänden 30 (Fig. 4) oder Stegen und der angrenzenden Wärmeübertragerplatte 4b sehr von Vorteil ist, so dass die Strömungskanäle 10 diskreter Art sind. Das heißt, die parallelen Strömungskanäle 10 sollen untereinander vorzugsweise nicht in kurzschlussartiger hydraulischer Verbindung stehen. Um die Haltbarkeit zu unterstützen, sind die vorstehend beschriebenen zusätzlichen metallischen Verbindungen an den Regionen 22 und den Gebieten 25 vorgesehen. In diesem Ausführungsbeispiel wurde, wie eingangs bereits erwähnt, eine sechseckige Form der Wärmeübertragerplatten 4a, 4b ausgewählt. Aus der Fig. 2 ist erkennbar, dass diese spezielle Formgebung mit der erforderlichen Größe der Gebiete 25 und mit den größeren Durchbrüchen 5 für die Kühlflüssigkeit zusammenhängt, bzw. darin ihre Ursachen hat. Die Durchbrüche 5 für die Kühlflüssigkeit liegen außerhalb des wesentlichen Abschnitts 21, wohingegen die Durchbrüche 5 für das CO2 innerhalb desselben angeordnet sind.A look at that Fig. 2 ostensibly gives the impression of an ornamental design. However, this is aimed at achieving intended technical effects. On the one hand, the section 21 of the heat exchanger plates 4a covered with the structures 20 should be as large as possible, and on the other hand, this entire section 21 should be used as much as possible for heat exchange. The best possible heat exchange is achieved in that the same pressure loss should always be present in all flow channels 10 through a clever choice of the design and the length of each flow channel. It is also a uniform distribution of the flow channels 10 intended over the entire section 21, which is why one has been provided both to a vertical symmetrical VA as well as to a horizontal axis HA of the design portion 21st As a result, the length of all flow channels 10 is approximately the same. The extremely high pressures of up to 300 bar were taken into account by leaving numerous island-like regions 22 without impressions within the essential section 21 , in which a metallic connection can be made to the other heat exchanger plate 4b , which is otherwise much thinner than the heat exchanger plate 4a . A metallic connection to the other heat exchanger plate 4b is of course also on the walls 30 between the groove-like furrows 20 are present which, however, alone, as the inventors have recognized, cannot provide sufficient strength because of the relatively small area proportions. In addition, there are areas 25 lying outside of the essential section 21 , which are also connected flat to the other heat exchanger plate 4b . However, the inventors emphasize that an excellent metallic connection between the walls 30 ( Fig. 4 ) or webs and the adjacent heat exchanger plate 4b is very advantageous, so that the flow channels 10 are of a discrete type. This means that the parallel flow channels 10 should preferably not be in a short-circuit-like hydraulic connection with one another. To support durability, the additional metallic connections described above are provided on regions 22 and regions 25 . In this exemplary embodiment, as already mentioned at the outset, a hexagonal shape of the heat exchanger plates 4a , 4b was selected. From the Fig. 2 it can be seen that this special shape is related to the required size of the regions 25 and the larger openings 5 for the cooling liquid, or has its causes therein. The openings 5 for the cooling liquid lie outside the essential section 21 , whereas the openings 5 for the CO 2 are arranged inside the latter.

Zurückkommend auf die bereits erwähnten Regionen 22 soll noch hinzugefügt werden, dass dieselben auch einen fertigungstechnischen Aspekt besitzen, der darin besteht, dass wenigstens in einigen dieser Regionen 22 sogenannte Abstreifer im Prägewerkzeug (nicht gezeigt) ausgebildet sind, die dafür sorgen, dass die Wärmeübertragerplatte 4a nach dem Prägevorgang aus dem Werkzeug entnehmbar ist.Returning to the regions 22 already mentioned, it should also be added that they also have a manufacturing aspect, which consists in the fact that at least in some of these regions 22, so-called wipers are formed in the embossing tool (not shown), which ensure that the heat exchanger plate 4a can be removed from the tool after the embossing process.

In den Fig. 1 und 3 ist weiterhin bemerkenswert, dass die Ränder 24 an den dickeren Wärmeübertragerplatten 4a deutlich kürzer sind als die Ränder 24 an den dünneren Wärmeübertragerplatten 4b. Das konnte deshalb so ausgeführt werden, weil einerseits auf der Kühlflüssigkeitsseite Drücke herrschen, die diese Bauweise zulassen und weil andererseits das unter Hochdruck stehende CO2 - Gas auf der Seite strömt, auf der eine haltbare flächige metallische Verbindung zwischen der dünnen Wärmeübertragerplatte 4b und der dickeren Wärmeübertragerplatte 4a vorhanden ist. Das führt zu einer äußerst kompakten Gestaltung des Plattenwärmeübertragers und zur weiteren Material - und Gewichtseinsparung, die bei einer Vielzahl solcher Platten 4a, 4b nicht unerwähnt bleiben soll.In the Fig. 1 and 3rd it is also noteworthy that the edges 24 on the thicker heat exchanger plates 4a are significantly shorter than the edges 24 on the thinner heat exchanger plates 4b . This could be done because, on the one hand, there are pressures on the coolant side that allow this construction and, on the other hand, the high-pressure CO 2 gas flows on the side on which there is a durable flat metallic connection between the thin heat exchanger plate 4b and the thicker one Heat exchanger plate 4a is present. This leads to an extremely compact design of the Plate heat exchanger and for further material and weight savings, which should not go unmentioned with a large number of such plates 4a , 4b .

Die Fig. 7 und 8 zeigen einen Blick auf die beiden Oberflächenseiten der Wärmeübertagerplatten 104a und 104b, die zur Bildung der Strömungskanäle 110 metallisch verbunden werden in einem zweiten Ausführungsbeispiel. Eine der Platten 104a oder 104b wird dazu um 180 ° um die Achse HA gedreht, so dass die gezeigten Oberflächenseiten aneinander zu liegen kommen. Die Fig. 6 zeigt in einem Ausschnitt exemplarisch zwei verbundene Wärmeübertragerplatten 104a, 104b, die Vorstehendes verdeutlicht. In diesem Ausführungsbeispiel wurden die links bzw. rechts der vertikalen Symmetrieachse VA liegenden Strukturen 120 auf beide Wärmeübertragerplatten 104a und 104b aufgeteilt. Hierbei können beide Platten 104a, 104b die gleiche Blechdicke aufweisen. Die Symmetrie bezieht sich lediglich auf die Anordnung der Strukturen 120 und der beiden Durchbrüche 105. Die gezeigte äußere Form der Platten ist in den beiden Darstellungen nicht symmetrisch, sollte aber vorzugsweise symmetrisch sein.The 7 and 8 show a view of the two surface sides of the heat transfer plates 104a and 104b , which are metallically connected to form the flow channels 110 in a second exemplary embodiment. For this purpose, one of the plates 104a or 104b is rotated through 180 ° about the axis HA , so that the surface sides shown come to lie against one another. The Fig. 6 FIG. 2 shows an example of two connected heat exchanger plates 104a , 104b , which illustrates the above. In this exemplary embodiment, the structures 120 lying on the left or right of the vertical axis of symmetry VA were divided between the two heat exchanger plates 104a and 104b . Here, both plates 104a , 104b can have the same sheet thickness. The symmetry only relates to the arrangement of the structures 120 and the two openings 105 . The outer shape of the plates shown is not symmetrical in the two representations, but should preferably be symmetrical.

In anderen Ausführungsbeispielen wurde vorgesehen, beide Wärmeübertragerplatten 204a und 204b in einem wesentlichen Abschnitt 221 mit einer Struktur zu versehen und miteinander zur Bildung der Strömungskanäle 210 zu verbinden, wie es in der Fig. 5 angedeutet wurde. Dabei sind die Wände 230 zwischen den Furchen der einen Platte 204a an den Wänden 230 der anderen Platte 204b metallisch verbunden. Weitere nicht gezeigte Abwandlungen solcher Ausführungsbeispiele können vorgenommen werden.In other exemplary embodiments, provision was made to provide both heat exchanger plates 204a and 204b with a structure in an essential section 221 and to connect them to one another to form the flow channels 210 , as shown in FIG Fig. 5 was hinted at. The walls 230 between the furrows of one plate 204a are metallically connected to the walls 230 of the other plate 204b . Further modifications, not shown, of such exemplary embodiments can be made.

In der Fig. 9 ist gezeigt, wie sich die Form der rillenartigen Furchen 20, die die Strömungskanäle 10 bilden, nach dem Abschluss des Lötprozesses verändert hat. Die Darstellung zeigt das bevorzugte Ausführungsbeispiel mit den verschieden dicken Wärmetauscherplatten 4a und 4b. Durch das Prägen werden rillenartige Furchen 20 mit etwa 0,8 mm Breite und etwa 1,0 mm Tiefe erzeugt. Während des Lötvorgangs fließt das Lot in die Kehlen 50, so dass sich ein etwa ellipsen - oder kreisförmiger Querschnitt in jeder rillenartigen Furche 20 bildet. Diese ideale Querschnittsform sorgt für einen möglichst geringen Druckverlust entlang eines jeden Strömungskanals 10. Für Ölkühler können die Tiefe und die Breite der rillenartigen Furchen 20 an die benötigten Bedingungen angepasst werden.In the Fig. 9 it is shown how the shape of the groove-like furrows 20 , which form the flow channels 10 , has changed after the soldering process has been completed. The illustration shows the preferred embodiment with the different thickness heat exchanger plates 4a and 4b . The embossing produces groove-like furrows 20 with a width of approximately 0.8 mm and a depth of approximately 1.0 mm. During the soldering process, the solder flows into the grooves 50 , so that an approximately elliptical or circular cross section is formed in each groove-like groove 20 . This ideal cross-sectional shape ensures the lowest possible pressure loss along each flow channel 10 . For oil coolers, the depth and the width of the groove-like furrows 20 can be adapted to the required conditions.

Claims (15)

  1. Plate heat exchanger, consisting of first and second heat exchanger plates (4a, 4b) with at least four apertures (5) for two media, the heat exchanger plates (4a, 4b) being stacked in an alternating manner between a bottom plate (3) and a top plate (2) in such a way that the apertures (5) form collector or distribution ducts (6, 7, 8, 9) which pass through the stack of heat exchanger plates (4), there being inlets and outlets from the collector or distribution ducts (6, 7, 8, 9) to flow ducts (10, 11) between the heat exchanger plates (4), in which the transfer of heat takes place, and the flow ducts (11) for the one medium being delimited by the one surface side of the first heat exchanger plate (4a) and by the spaced-apart one surface side of the second heat exchanger plate (4b), characterized in that the flow ducts (10, 110) for the other medium are of a discrete type, with the result that the said flow ducts are not in a hydraulic connection among one another in the manner of a short circuit, and are formed by way of flat bearing and metallic connection of the other surface side of the first heat exchanger plate (4a, 104a) to the other surface side of the second heat exchanger plate (4b, 104b), the other surface side of the first heat exchanger plate (4a, 104a) having structures (20, 120) in the form of groove-like furrows, and the other surface side of the second heat exchanger plate (4b, 104b) being configured either with or without structures (20, 120) of this type, fins (13) being inserted between the heat exchanger plates (4a, 4b) in the flow ducts (11) for the one medium, and the structures (20) being produced by way of stamping of the heat exchanger plates (4a or 4a and 4b).
  2. Plate heat exchanger according to Claim 1, characterized in that the structures or the groove-like furrows (20) provide a hydraulic connection from the one aperture (5) of the other medium to the other aperture (5), to which end the apertures (5) or the collector and distribution ducts (8, 9) which are formed by way of them are arranged within a substantial section (21) of the heat exchanger plate (4a), which section is provided with the groove-like furrows (20).
  3. Plate heat exchanger according to Claim 3, characterized in that the groove-like furrows (20) or the structures (20) which are arranged in the substantial section (21) of the heat exchanger plate (4a) have a symmetrically identical pattern, with the result that there are flow ducts (10) of approximately identical length on the two pattern sides.
  4. Plate heat exchanger according to Claim 1, characterized in that the first heat exchanger plates (4a) have a considerably greater plate thickness than the second heat exchanger plates (4b).
  5. Plate heat exchanger according to Claim 1, characterized in that the first and second heat exchanger plates (4a, 4b) have the same plate thickness.
  6. Plate heat exchanger according to one of the preceding claims, characterized in that the other apertures (5) for the one medium and the collector and distribution ducts (6, 7) which are formed by way of them are arranged outside a section (21) of the heat exchanger plates (4a, 4b) which is provided with the stamped structures (20).
  7. Plate heat exchanger according to one of the preceding claims, characterized in that the first and second heat exchanger plates (4a, 4b) have a circumferential bent-over edge (24), at which adjoining heat exchanger plates (4a, 4b) are connected to one another metallically.
  8. Plate heat exchanger according to Claim 8, characterized in that the edge (13) of the one heat exchanger plates (4b) is longer than the edge of the other heat exchanger plates (4a).
  9. Plate heat exchanger according to Claim 1, 3 or 4, characterized in that the substantial section (21) of the heat exchanger plate (4a), which section (21) is provided with structures (20) or with the groove-like furrows (20) is flanked by a multiplicity of substantially parallel furrows, and in that a further multiplicity of groove-like furrows (20) are configured within the flanked section (23), in which there are non-stamped regions (22) .
  10. Plate heat exchanger according to Claim 9, characterized in that in each case one first heat exchanger plate (4a) is connected over the full area metallically to a second heat exchanger plate (4b) outside the substantial section (21) and at the regions (22) within the section (21), and in that there is also a metallic connection at the groove-like furrows (20), with the result that the flow ducts (10) are of pressure-resistant configuration and are of a discrete type.
  11. Plate heat exchanger according to Claim 11, characterized in that the groove-like furrows (20) have a serpentine course within the flanked section (23), which serpentine course has in part a plurality of parallel furrows and individual furrows (20) which are arranged around the regions (22).
  12. Plate heat exchanger according to Claim 4, characterized in that there are preferably planar areas (25) outside the substantial section (21), in which planar areas (25) the heat exchanger plate (4a) is connected over the full area metallically to the heat exchanger plate (4b).
  13. Plate heat exchanger according to one of the preceding claims, characterized in that the flow ducts (10) which are formed by way of a stamped surface side of the first heat exchanger plate (4a) and by way of a non-stamped surface side of the second heat exchanger plate (4b), are provided for CO2 as refrigerant of air conditioning systems in motor vehicles, whereas the other flow ducts (11) are configured in such a way that cooling liquid of an engine can flow through the other flow ducts (11).
  14. Plate heat exchanger according to Claim 15, characterized in that a rod-shaped body (12) which increases the pressure stability of the plate heat exchanger is arranged in the collector and distribution ducts (8, 9) for the refrigerant.
  15. Use of a plate heat exchanger according to one of the preceding claims, as a water/oil heat exchanger.
EP05003752.2A 2004-03-05 2005-02-22 Plate heat exchanger Expired - Fee Related EP1571407B1 (en)

Applications Claiming Priority (2)

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DE102004010640 2004-03-05
DE102004010640A DE102004010640A1 (en) 2004-03-05 2004-03-05 Plate heat exchangers

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EP1571407A2 EP1571407A2 (en) 2005-09-07
EP1571407A3 EP1571407A3 (en) 2010-09-29
EP1571407B1 true EP1571407B1 (en) 2020-04-08

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US (1) US7600559B2 (en)
EP (1) EP1571407B1 (en)
DE (1) DE102004010640A1 (en)

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Also Published As

Publication number Publication date
DE102004010640A1 (en) 2005-09-22
EP1571407A2 (en) 2005-09-07
US7600559B2 (en) 2009-10-13
EP1571407A3 (en) 2010-09-29
US20050194123A1 (en) 2005-09-08

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