[go: up one dir, main page]

EP0992756A2 - Heat exchanger, more particularly for gases and liquids - Google Patents

Heat exchanger, more particularly for gases and liquids Download PDF

Info

Publication number
EP0992756A2
EP0992756A2 EP99119392A EP99119392A EP0992756A2 EP 0992756 A2 EP0992756 A2 EP 0992756A2 EP 99119392 A EP99119392 A EP 99119392A EP 99119392 A EP99119392 A EP 99119392A EP 0992756 A2 EP0992756 A2 EP 0992756A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
flow channels
plates
exchanger plates
collection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99119392A
Other languages
German (de)
French (fr)
Other versions
EP0992756A3 (en
EP0992756B1 (en
Inventor
Roland Dipl.-Ing. Strähle
Viktor Dipl.-Ing. Brost
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP0992756A2 publication Critical patent/EP0992756A2/en
Publication of EP0992756A3 publication Critical patent/EP0992756A3/en
Application granted granted Critical
Publication of EP0992756B1 publication Critical patent/EP0992756B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/104—Particular pattern of flow of the heat exchange media with parallel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements

Definitions

  • the invention relates to a heat exchanger, in particular for the heat exchange between a gas and a liquid, for example charge air or exhaust gas heat exchangers cooled with water, comprising a stack of shell-shaped heat exchanger plates which are joined in mirror image and are connected to one another at the edge flange and around their openings lying on a line that they include collection and distribution spaces for one of the agents and its flow channels, and with collection rooms in which the flow channels for the other agent open.
  • This heat exchanger provided as an exhaust gas heat exchanger, is known from EP 677 715 A1.
  • Bowl-shaped heat exchanger plates are provided in this document when the exhaust gas is cooled with cooling air.
  • the flow channels for the exhaust gas formed by the shell-shaped heat exchanger plates are arranged at a distance, and at these distances there are fins through which the cooling air flows freely.
  • the cooling is provided with a liquid, for example with cooling water
  • the flow channels for both media are formed by means of plates which have rods or spacers between them to form the flow channels and which are also enclosed by a housing which covers the outer wall of the Forms cooling water channels.
  • This design can be considered complex because the number of individual parts is very high.
  • the object of the invention is to build up the heat exchanger described in the preamble of claim 1 for cooling the gas with a liquid in a simple manner with shell-shaped heat exchanger plates and to dispense with the outer housing.
  • the stack of bowl-shaped heat exchanger plates includes separate flow channels for both means in itself, that the heat exchanger plates have a circumferential shape, which comprise the inlet and the outlet opening for the one means that the circumferential shape of the one heat exchanger plate with the Expression of the next heat exchanger plate is connected and separates both parallel flow channels arranged within the area enclosed by the circumferential expression from one another and towards the outside, and that the flow channels for the other agent lead into at least one collecting space outside of the peripheral expression. Because the circumferential configuration also seals off both types of flow channels from the outside, the heat exchanger according to the invention can be designed without an outer housing and is therefore easier to manufacture and use less material.
  • the circumferential shape is incorporated into the embossing or deep-drawing tool and does not require any additional work in the plate production.
  • the circumferential shape has a suitable cross-sectional shape. It is preferably approximately U-shaped and has sections which run near the edge of the heat exchanger plates and further sections which cross the heat exchanger plates. Because the base section of the U-shaped configuration comes into contact with the same base section of the next heat exchanger plate when the heat exchanger plates are stacked, horizontal connecting surfaces, that is to say parallel to the plane of the heat exchanger plates, are formed between the individual plates, which enable an excellent soldered connection. The crossing point ends one of the flow channels.
  • the other flow channels go beyond this crossing point and preferably open at both opposite ends in the collecting spaces assigned to them.
  • a collection box arranged at one end, with a partition, inlet and outlet and a deflection box arranged at the other end.
  • the collecting spaces can have a tube sheet which has openings adapted to the cross section of the flow channels, or the flow channels can be widened at the ends and connected to the longitudinal walls, as a result of which the known design can be implemented without the use of tube sheets.
  • the collecting and the distribution space are preferably formed by pot-like depressions around the openings in the stacked heat exchanger plates, as is known per se.
  • sleeves that can be used instead of the pot-like depressions are also within the scope of the present invention.
  • the flow channels for the liquid coolant preferably have support knobs which are connected to the same knobs of the adjacent plate. However, these knobs can also be replaced by inner inserts. Internal inserts are preferably arranged in the flow channels for the gas. The shape of the inserts depends on the respective application.
  • exhaust gas is to be cooled, the decision will be made to use it indoors, where as little deposits as possible can form, i.e. which have smooth surfaces.
  • internal inserts can be provided, which ensure more turbulence and even better heat exchange.
  • the inner inserts have been completely omitted in another inventive embodiment.
  • the heat exchanger plates were equipped with alternately arranged first and second beads.
  • the second beads can have interruptions, so that only in one row support knobs remain.
  • An inventive embodiment also has cover plates, which ensure very flexible connection positions of the connecting pieces, because the connecting pieces can be located at any point on the connecting plates.
  • the exhaust gas heat exchanger consists of a suitable stainless steel. All connections between the individual parts of the exhaust gas heat exchanger are preferably made by soldering.
  • FIG. 1 which shows a top view without a cover plate 22, the collecting space 4 and the distribution space 4 are arranged on opposite sides 12 of the exhaust gas heat exchanger in projecting areas 13. For this reason, two types of heat exchanger plates 1 are required to form the flow channels 5 and 7.
  • the flow channels 5 are provided for water W and the flow channels 7 for exhaust gas G.
  • the heat exchanger plates 1 are connected in pairs at their peripheral edges 2.
  • peripheral features 8 which has been shown as a thick line in the plan view and which comprises an area of the exhaust gas heat exchanger which is smaller than the total area of the heat exchanger plates 1 or smaller than the area enclosed by the edge 10 .
  • the area enclosed by the peripheral configuration 8 includes the inlet openings 3 and the outlet openings 3 for the cooling water and consists of sections 9 running in the vicinity of the edge 10 and sections 11 which cross the heat exchanger plates 1. This crossing can run at any angle to the longitudinal axis of the heat exchanger plates 1 and is arranged perpendicular to the longitudinal axis in FIG. 1.
  • the circumferential shape 8 is embossed in a U-shape in the heat exchanger plates 1, as the sketchy FIGS. 1a and 1b show.
  • 1b also shows that the flow channels 5 for the cooling water W end at the circumferential configuration 8, but they continue to flow channels 7 for the exhaust gas G into the collecting space 6 or into the tube sheet 15.
  • the sketch 1c shows the cross section of the flow channels 7 in this area. Inside the flow channels 7 there are inner inserts 17 which extend over the entire length of the flow channels 7, even if they have not been shown in FIG. 1a. Where the circumferential features 8 of two heat exchanger plates 1 are connected to one another, both the flow channel 5 is sealed off from the flow channel 7, and both channels 5 and 7 to the outside, so that no outer housing has to enclose the stack of heat exchanger plates 1. 1c shows that the flow channels 7 each have two longitudinal walls 16.
  • the tube sheet 15 has individual openings which correspond to the cross section of the flow channels 7 in order to be able to accommodate them.
  • the ends of the flow channels 7 are widened, so that the longitudinal walls 16 of the adjacent channels 7 can be connected to one another, as a result of which the tube sheet 15 can be omitted because an opening is present directly in the collecting space 6 which can accommodate all of the flow channels 7 .
  • Studs 20 have been drawn in on the uppermost heat exchanger plate of FIG. 1. These knobs 20 can also be found in FIG. 3, which shows the section C - C from FIG. 1, with the difference that the cover plate 22, which delimits a space 24 to the first heat exchanger plate 1, has been drawn in the section C - C .
  • the knobs 20 extend into the flow channel 5, in which water W flows.
  • the knobs 16 of the one heat exchanger plate 1 are connected to the knobs 16 of the next heat exchanger plate 1.
  • 3 also shows the design of the collecting or distribution rooms 4. Pot-like depressions 14 are formed around the openings 3 in the heat exchanger plates 1 and, lying on a vertical line, form the collecting and distribution space 4, which is in connection with the flow channels 5, so that the water W can flow in accordance with the flow arrows shown .
  • the formation of the edges 2 with the circumferential shape 8 in the area of the collecting and distribution spaces 4 can also be seen in FIG. 3.
  • the cover plate 22 makes it possible to freely select the position of the connecting pieces 19 for the water W, and that at any point on the entire plate 22.
  • FIG. 4 shows a view from the direction of a collecting space 6 for the exhaust gas G.
  • a part of the tube sheet 15 can be seen, in which the flow channels 7 with inner inserts 17 open.
  • the connection to the exhaust pipe, not shown, can be made here by means of a clamping ring 21.
  • the exhaust gas heat exchanger is fastened, for example in a vehicle, by suitable brackets 23
  • the side view of the exhaust gas heat exchanger shown in FIG. 2 shows another embodiment in which the inlet and outlet connections 19 for the water W have been arranged on a common side 12 of the exhaust gas heat exchanger, in the drawing on the rear side, not shown. This has the advantage that all heat exchanger plates 1 can be designed the same. From this side view, the area B emerges, which is determined by the peripheral shape 8.
  • FIGS. 5 and 7 show two other embodiments in which inner inserts 17 have been completely dispensed with. As a result, the number of individual parts is lower, with the result that the manufacturing process can be made simpler.
  • the top views in FIGS. 5 and 7 were each drawn without a cover plate 22.
  • the heat exchanger plates 1 are provided with an undulating wall, which have been realized by alternating longitudinal beads 25 and 26.
  • the embodiment shown in FIGS. 5 and 6 differs from the embodiment of FIGS. 7 to 9 in that the first-mentioned embodiment has no continuous first beads 25.
  • FIGS. 5 and 6 show no projecting areas 13 of the heat exchanger plates 1.
  • the collecting and distribution spaces 4 are arranged within the rectangular basic shape of the heat exchanger plates 1. 7 to 9 projecting areas 13 are provided, in which the collection and distribution spaces 4 are located.
  • the last two embodiments described allow an even more compact design of the exhaust gas heat exchanger.

Landscapes

  • 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)
  • Physical Or Chemical Processes And Apparatus (AREA)

Abstract

The heat exchanger plate (1) are so connected that they enclose collection and distribution spaces (4) for one of the media and its horizontal flow channels (5). In the collection space (6) issue flow channels for the second medium. The shell-shaped plates are stacked and identically brought together and enclose the flow channels for the second medium. The plates have an all-round molding (8) which has at least one inlet and one outlet aperture (3) for the one medium. The one molding of one plate is connected with that of the next plate. It is possible for two types of heat exchanger plates to be used and for the collection space (4) on one side (12) and the distributor space to be arranged on the opposite side of the heat exchanger.

Description

Die Erfindung betrifft einen Wärmetauscher, insbesondere für den Wärmeaustausch zwischen einem Gas und einer Flüssigkeit, beispielsweise mit Wasser gekühlte Ladeluft - oder Abgaswärmetauscher, umfassend einen Stapel aus schalenförmigen Wärmetauscherplatten, die spiegelbildlich zusammengefügt und am Randflansch und um ihren auf einer Linie liegenden Öffnungen so verbunden sind, daß sie Sammel-und Verteilerräume für eines der Mittel und dessen Strömungskanäle in sich einschließen sowie mit Sammelräumen, in denen die Strömungskanäle für das andere Mittel münden.
Dieser Wärmetauscher, vorgesehen als Abgaswärmetauscher, ist aus EP 677 715 A1 bekannt. Schalenförmige Wärmetauscherplatten werden in diesem Dokument dann vorgesehen, wenn das Abgas mit Kühlluft gekühlt wird. In diesem Fall sind die durch die schalenförmigen Wärmetauscherplatten gebildeten Strömungskanäle für das Abgas auf Abstand angeordnet und in diesen Abständen befinden sich Lamellen die von der Kühlluft frei durchströmt werden.
Ist hingegen die Kühlung mit einer Flüssigkeit, beispielsweise mit Kühlwasser, vorgesehen, dann werden die Strömungskanäle für beide Medien mittels Platten gebildet, die zwischen sich Stäbe oder Distanzstücke zur Bildung der Strömungskanäle aufweisen und die ferner von einem Gehäuse eingeschlossen sind, das die äußere Wandung der Kühlwasserkanäle bildet. Diese Bauweise kann als aufwendig angesehen werden, weil die Zahl der Einzelteile sehr hoch ist.
Die Aufgabe der Erfindung besteht darin, den im Oberbegriff des Anspruchs 1 beschriebenen Wärmetauscher zur Kühlung des Gases mit einer Flüssigkeit auf einfache Art und Weise mit schalenförmigen Wärmetauscherplatten aufzubauen und dabei auf das äußere Gehäuse zu verzichten.
Diese Aufgabe wurde erfindungsgemäß durch die Merkmale in den Patentansprüchen gelöst.
Nach Anspruch 1 ist vorgesehen, daß der Stapel schalenförmiger Wärmetauscherplatten getrennte Strömungskanäle für beide Mittel in sich einschließt, daß die Wärmetauscherplatten eine umlaufende Ausprägung aufweisen, die die Einlaß-und die Auslaßöffnung für das eine Mittel umfassen, daß die umlaufende Ausprägung der einen Wärmetauscherplatte mit der Ausprägung der nächsten Wärmetauscherplatte verbunden ist und beide innerhalb des von der umlaufenden Ausprägung eingeschlossenen Bereiches angeordneten parallelen Strömungskanäle voneinander und nach außen hin trennt und daß die Strömungskanäle für das andere Mittel außerhalb der umlaufenden Ausprägung in wenigstens einen Sammelraum münden.
Weil die umlaufende Ausprägung beide Arten Strömungskanäle auch nach außen hin abschottet, kann der erfindungsgemäße Wärmetauscher ohne äußeres Gehäuse ausgeführt werden und ist deshalb mit weniger Materialeinsatz bzw. leichter herstellbar. Im Vergleich mit Wärmetauschern, die in Stab-Platten-Bauweise aufgebaut sind, sind wesentlich weniger Einzelteile vorhanden, wodurch der Fertigungsprozeß vereinfacht wird. Die umlaufende Ausprägung wird in das Präge- oder Tiefziehwerkzeug eingearbeitet und erfordert keinen zusätzlichen Arbeitsgang bei der Plattenherstellung.
Die umlaufende Ausprägung weist eine geeignete Querschnittsform auf. Vorzugsweise ist sie etwa u-förmig ausgebildet und besitzt Abschnitte, die in der Nähe des Randes der Wärmetauscherplatten verlaufen und weitere Abschnitte, die die Wärmetauscherplatten kreuzen. Weil der Basisabschnitt der u-förmigen Ausprägung beim Stapeln der Wärmetauscherplatten mit demselben Basisabschnitt der nächsten Wärmetauscherplatte zur Anlage kommt, werden jeweils horizontale, d. h. parallel zu der Ebene der Wärmetauscherplatten verlaufende Verbindungsflächen zwischen den einzelnen Platten gebildet, die eine exzellente Lötverbindung ermöglichen.
Die Kreuzungsstelle beendet die einen Strömungskanäle. Die anderen Strömungs kanäle gehen jedoch über diese Kreuzungsstelle hinaus und münden vorzugsweise an beiden gegenüberliegenden Enden in den ihnen zugeordneten Sammelräumen. Selbstverständlich gibt es Ausführungsformen mit nur an einem Ende angeordneten Sammelkasten, mit Trennwand, Einlaß und Auslaß und am anderen Ende angeordneten Umlenkkasten.
Die Sammelräume können einen Rohrboden aufweisen, der dem Querschnitt der Strömungskanäle angepaßte Öffnungen aufweist, oder die Strömungskanäle können an den Enden aufgeweitet und an den Längswänden verbunden sein, wodurch die an sich bekannte Ausführung ohne Verwendung von Rohrböden realisiert werden kann. The invention relates to a heat exchanger, in particular for the heat exchange between a gas and a liquid, for example charge air or exhaust gas heat exchangers cooled with water, comprising a stack of shell-shaped heat exchanger plates which are joined in mirror image and are connected to one another at the edge flange and around their openings lying on a line that they include collection and distribution spaces for one of the agents and its flow channels, and with collection rooms in which the flow channels for the other agent open.
This heat exchanger, provided as an exhaust gas heat exchanger, is known from EP 677 715 A1. Bowl-shaped heat exchanger plates are provided in this document when the exhaust gas is cooled with cooling air. In this case, the flow channels for the exhaust gas formed by the shell-shaped heat exchanger plates are arranged at a distance, and at these distances there are fins through which the cooling air flows freely.
If, on the other hand, the cooling is provided with a liquid, for example with cooling water, then the flow channels for both media are formed by means of plates which have rods or spacers between them to form the flow channels and which are also enclosed by a housing which covers the outer wall of the Forms cooling water channels. This design can be considered complex because the number of individual parts is very high.
The object of the invention is to build up the heat exchanger described in the preamble of claim 1 for cooling the gas with a liquid in a simple manner with shell-shaped heat exchanger plates and to dispense with the outer housing.
This object was achieved according to the invention by the features in the claims.
According to claim 1 it is provided that the stack of bowl-shaped heat exchanger plates includes separate flow channels for both means in itself, that the heat exchanger plates have a circumferential shape, which comprise the inlet and the outlet opening for the one means that the circumferential shape of the one heat exchanger plate with the Expression of the next heat exchanger plate is connected and separates both parallel flow channels arranged within the area enclosed by the circumferential expression from one another and towards the outside, and that the flow channels for the other agent lead into at least one collecting space outside of the peripheral expression.
Because the circumferential configuration also seals off both types of flow channels from the outside, the heat exchanger according to the invention can be designed without an outer housing and is therefore easier to manufacture and use less material. Compared to heat exchangers, which are constructed in rod-plate construction, there are significantly fewer individual parts, which simplifies the manufacturing process. The circumferential shape is incorporated into the embossing or deep-drawing tool and does not require any additional work in the plate production.
The circumferential shape has a suitable cross-sectional shape. It is preferably approximately U-shaped and has sections which run near the edge of the heat exchanger plates and further sections which cross the heat exchanger plates. Because the base section of the U-shaped configuration comes into contact with the same base section of the next heat exchanger plate when the heat exchanger plates are stacked, horizontal connecting surfaces, that is to say parallel to the plane of the heat exchanger plates, are formed between the individual plates, which enable an excellent soldered connection.
The crossing point ends one of the flow channels. However, the other flow channels go beyond this crossing point and preferably open at both opposite ends in the collecting spaces assigned to them. Of course, there are embodiments with a collection box arranged at one end, with a partition, inlet and outlet and a deflection box arranged at the other end.
The collecting spaces can have a tube sheet which has openings adapted to the cross section of the flow channels, or the flow channels can be widened at the ends and connected to the longitudinal walls, as a result of which the known design can be implemented without the use of tube sheets.

In Abhängigkeit von der Lage der Anschlüsse können sowohl baugleiche Wärmetauscherplatten Anwendung finden, was sehr vorteilhaft ist, es kann aber auch erforderlich sein, den Stapel mit zwei verschiedenen Sätzen von Wärmetauscherplatten zu bilden.
Der Sammel-und der Verteilerraum werden vorzugsweise durch topfartige Vertiefungen um die Öffnungen herum in den aufeinandergestapelten Wärmetauscherplatten ausgebildet, wie das an und für sich bekannt ist. Im Rahmen der vorliegenden Erfindung liegen jedoch auch Hülsen, die anstelle der topfartigen Vertiefungen eingesetzt werden können.
Vorzugsweise besitzen die Strömungskanäle für das flüssige Kühlmittel Abstütznoppen, die mit ebensolchen Noppen der benachbarten Platte verbunden sind.
Diese Noppen kann man jedoch ebenfalls durch Inneneinsätze ersetzen. Inneneinsätze sind vorzugsweise in den Strömungskanälen für das Gas angeordnet.
Die Form der Inneneinsätze ist abhängig von dem jeweiligen Einsatzfall. Soll Abgas gekühlt werden, wird man sich für Inneneinsätze entscheiden, an denen sich möglichst wenig Ablagerungen bilden können, die also glatte Oberflächen haben.
Bei Ladeluft können Inneneinsätze vorgesehen werden, die für mehr Turbulenz und noch besseren Wärmesustausch sorgen.
Die Inneneinsätze sind bei einer anderen erfinderischen Ausführungsform vollständig weggelassen worden. Dafür wurden die Wärmetauscherplatten mit alternierend angeordneten ersten und zweiten Sicken ausgestattet. Die zweiten Sicken können Unterbrechungen aufweisen, so daß lediglich in einer Reihe liegende Abstütznoppen übrigbleiben.
Eine erfinderische Ausführungsform besitzt ferner Abdeckplatten, die für sehr flexible Anschlußlagen der Stutzen sorgen, weil sich die Stutzen an beliebigen Stellen der Anschlußplatten befinden können.Depending on the position of the connections, identical heat exchanger plates can be used, which is very advantageous, but it may also be necessary to form the stack with two different sets of heat exchanger plates.
The collecting and the distribution space are preferably formed by pot-like depressions around the openings in the stacked heat exchanger plates, as is known per se. However, sleeves that can be used instead of the pot-like depressions are also within the scope of the present invention.
The flow channels for the liquid coolant preferably have support knobs which are connected to the same knobs of the adjacent plate.
However, these knobs can also be replaced by inner inserts. Internal inserts are preferably arranged in the flow channels for the gas.
The shape of the inserts depends on the respective application. If exhaust gas is to be cooled, the decision will be made to use it indoors, where as little deposits as possible can form, i.e. which have smooth surfaces.
With charge air, internal inserts can be provided, which ensure more turbulence and even better heat exchange.
The inner inserts have been completely omitted in another inventive embodiment. For this purpose, the heat exchanger plates were equipped with alternately arranged first and second beads. The second beads can have interruptions, so that only in one row support knobs remain.
An inventive embodiment also has cover plates, which ensure very flexible connection positions of the connecting pieces, because the connecting pieces can be located at any point on the connecting plates.

Nachfolgend wird die Erfindung anhand mehrerer Ausführungsbeispiele erläutert, wozu auf die beiliegenden Zeichnungen Bezug genommen wird.

Fig. 1
Draufsicht auf einen Abgaswärmetauscher
Fig. 1a
Schnitt am Längsrand in Fig. 1
Fig. 1b
Schnitt im Kreuzungsbereich in Fig. 1
Fig. 1c
Schnitt durch die Abgaskanäle in Fig. 1
Fig. 2
Seitenansicht eines Abgaswärmetauschers
Fig. 3
Schnitt C-C in Fig. 1
Fig. 4
Vorderansicht von Fig. 1
Fig. 5
Draufsicht einer anderen Ausführungsform
Fig. 6
Schnitt A - A in Fig. 5
Fig. 7
Draufsicht einer dritten Ausführungsform
Fig. 8
Schnitt A-A in Fig. 7
Fig. 9
Schnitt B-B in Fig. 7
The invention is explained below using several exemplary embodiments, for which reference is made to the accompanying drawings.
Fig. 1
Top view of an exhaust gas heat exchanger
Fig. 1a
Section along the longitudinal edge in Fig. 1st
Fig. 1b
Section in the intersection area in Fig. 1st
Fig. 1c
Section through the exhaust gas channels in Fig. 1st
Fig. 2
Side view of an exhaust gas heat exchanger
Fig. 3
Section CC in Fig. 1st
Fig. 4
1
Fig. 5
Top view of another embodiment
Fig. 6
Section A - A in Fig. 5
Fig. 7
Top view of a third embodiment
Fig. 8
Section AA in FIG. 7
Fig. 9
Section BB in FIG. 7

Der Abgaswärmetauscher besteht aus einem geeigneten Edelstahl. Sämtliche Verbindungen zwischen den Einzelteilen des Abgaswärmetauschers werden vorzugsweise durch Löten hergestellt.
Im Ausführungsbeispiel nach Fig. 1, die eine Draufsicht ohne Abdeckplatte 22 zeigt, sind der Sammelraum 4 und der Verteilerraum 4 an gegenüberliegenden Seiten 12 des Abgaswärmetauschers in überkragenden Bereichen 13 angeordnet.
Aus diesem Grund sind hier zwei Arten Wärmetauscherplatten 1 erforderlich, um die Strömungskanäle 5 und 7 zu bilden. Die Strömungskanäle 5 sind für Wasser W vorgesehen und die Strömungskanäle 7 für Abgas G. Die Wärmetauscherplatten 1 sind paarweise an ihren umlaufenden Rändern 2 verbunden. Außerdem sind sie an ihren umlaufenden Ausprägungen 8 verbunden, die in der Draufsicht als eine dicke Linie dargestellt worden ist und die einen Bereich des Abgaswärmetauschers umfaßt, der kleiner ist, als die Gesamtfläche der Wärmetauscherplatten 1 bzw. kleiner als der von dem Rand 10 eingeschlossene Bereich. Der von der umlaufenden Ausprägung 8 umschlossene Bereich schließt die Einlaßöffnungen 3 und die Auslaßöffnungen 3 für das Kühlwasser ein und besteht aus in der Nähe des Randes 10 verlaufenden Abschnitten 9 und aus Abschnitten 11, die die Wärmetauscherplatten 1 kreuzen. Diese Kreuzung kann in einem beliebigen Winkel zur Längsachse der Wärmetauscherplatten 1 verlaufen und ist in Fig. 1 senkrecht zur Längsachse angeordnet. Die umlaufende Ausprägung 8 ist hier u-förmig in die Wärmetauscherplatten 1 eingeprägt, wie die skizzenhaften Fig. 1a und 1b zeigen. Die Fig. 1b zeigt ferner, daß die Strömungskanäle 5 für das Kühlwasser W an der umlaufenden Ausprägung 8 enden, jedoch sie Strömungskanäle 7 für das Abgas G bis in den Sammelraum 6 bzw. in den Rohrboden 15 weitergeführt sind. Die Skizze 1c zeigt den Querschnitt der Strömungskanäle 7 in diesem Bereich. In den Strömungskanälen 7 befinden sich Inneneinsätze 17, die sich über die Gesamtlänge der Strömungskanäle 7 erstrecken, auch wenn sie in Fig. 1a nicht eingezeichnet worden sind. Dort wo die umlaufenden Ausprägungen 8 zweier Wärmetauscherplatten 1 miteinander verbunden sind, ist sowohl der Strömungskanal 5 vom Strömungskanal 7 abgeschottet, als auch beide Kanäle 5 und 7 nach außen hin, so daß kein äußeres Gehäuse den Stapel der Wärmetauscherplatten 1 umschließen muß. Die Fig. 1c zeigt, daß die Strömungskanäle 7 je zwei Längswände 16 aufweisen. In dem gezeigten Ausführungsbeispiel hat der Rohrboden 15 einzelne Öffnungen, die dem Querschnitt der Strömungskanäle 7 entsprechen, um dieselben aufnehmen zu können. In einem nicht gezeigten Ausführungsbeispiel sind die Enden der Strömungskanäle 7 aufgeweitet, so daß die Längswände 16 der benachbarten Kanäle 7 miteinander verbunden werden können, wodurch der Rohrboden 15 entfallen kann, weil direkt im Sammelraum 6 eine Öffnung vorhanden ist, die sämtliche Strömungskanäle 7 aufnehmen kann.
Auf der obersten Wärmetauscherplatte der Fig. 1 sind Noppen 20 eingezeichnet worden. Diese Noppen 20 sind auch in Fig. 3 zu finden, die den Schnitt C - C aus Fig. 1 zeigt, mit dem Unterschied, daß im Schnitt C - C die Abdeckplatte 22 eingezeichnet wurde, die einen Raum 24 zur ersten Wärmetauscherplatte 1 hin eingrenzt. Die Noppen 20 erstrecken sich in den Strömungskanal 5, in dem Wasser W strömt. Die Noppen 16 der einen Wärmetauscherplatte 1 sind mit den Noppen 16 der nächsten Wärmetauscherplatte 1 verbunden. Aus der Fig. 3 geht außerdem die Ausbildung der Sammel-oder Verteilerräume 4 hervor. Um die Öffnungen 3 herum sind in den Wärmetauscherplatten 1 topfartige Vertiefungen 14 angeformt, die auf einer vertikalen Linie liegend den Sammel-und den Verteilerraum 4 ausbilden, der in Verbindung mit den Strömungskanälen 5 ist, so daß das Wasser W gemäß den eingezeichneten Strömungspfeilen fließen kann. Die Ausbildung der Ränder 2 mit der umlaufenden Ausprägung 8 im Bereich der Sammel-und Verteilerräume 4 kann ebenfalls aus Fig. 3 entnommen werden. Die Abdeckplatte 22 ermöglicht es, die Lage der Anschlußstutzen 19 für das Wasser W frei wählen zu können und zwar an einer beliebigen Stelle an der gesamten Platte 22.
Die Fig. 4 zeigt eine Ansicht aus Richtung des einen Sammelraumes 6 für das Abgas G. Zu erkennen ist ein Teil des Rohrbodens 15, in dem die Strömungskanäle 7 mit Inneneinsätzen 17 münden. Der Anschluß an die nicht gezeigte Abgasleitung kann hier mittels eines Spannringes 21 vorgenommen werden. Die Befestigung des Abgaswärmetauschers, beispielsweise in einem Fahrzeug, erfolgt durch geeignete Halterungen 23
Die in der Fig. 2 dargestellte Seitenansicht des Abgaswärmetauschers zeigt ein anderes Ausführungsbeispiel, bei dem die Ein-und Auslaßstutzen 19 für das Wasser W an einer gemeinsamen Seite 12 des Abgaswärmetauschers angeordnet worden sind, in der Zeichnung an der nicht gezeigten Rückseite. Dadurch ergibt sich der Vorteil, daß alle Wärmetauscherplatten 1 gleich gestaltet sein können. Aus dieser Seitenansicht geht der Bereich B hervor, der von der umlaufenden Ausprägung 8 bestimmt wird. Innerhalb dieses Bereiches B laufen die Strömungskanäle 5 und 7 parallel. Außerhalb dieses Bereiches münden die Strömungskanäle 7 in den Sammelräumen 6. Die Strömungskanäle 5 enden dort, wo die umlaufende Ausprägung 8 die Wärmetauscherplatten 1 kreuzt.
Die Fig. 5 bis 9 zeigen zwei andere Ausführungsformen bei denen auf Inneneinsätze 17 vollständig verzichtet worden ist. Dadurch ist die Zahl der Einzelteile geringer, mit der Folge, daß der Herstellungsprozeß einfacher gestaltet werden kann. Die Draufsichten in den Fig. 5 und 7 wurden jeweils ohne Abdeckplatte 22 gezeichnet. Die Wärmetauscherplatten 1 sind mit einer wellenförmigen Wandung versehen, die durch alternierende Längssicken 25 und 26 realisiert worden sind.
Die in den Fig. 5 und 6 gezeigte Ausführungsform unterscheidet sich von der Ausführungsform der Fig. 7 bis 9 dadurch, daß die erstgenannte Ausführungsform keine durchgehenden ersten Sicken 25 aufweist. Diese Sicken 25 sind durch in einer Reihe angeordnete Abstütznoppen 20 ersetzt worden. Dadurch ist der Strömungswiderstand für das Kühlwasser W in den Kanälen 5 reduziert worden.
In Fig. 5 ist durch Strömungspfeile deutlich gemacht worden, daß das Wasser leichter ein-und ausströmen kann, wie ein Vergleich mit der Fig. 7 zeigt. Ein weiterer Unterschied zwischen diesen beiden Ausführungsformen besteht in der Anordnung der Sammel-und Verteilerräume 4. Die Fig. 5 und 6 zeigen keine auskragenden Bereiche 13 der Wärmetauscherplatten 1. Die Sammel-und Verteilerräume 4 sind innerhalb der rechteckigen Grundform der Wärmetauscherplatten 1 angeordnet. In den Fig. 7 bis 9 sind auskragende Bereiche 13 vorgesehen, in denen sich die Sammel-und Verteilerräume 4 befinden. Die zuletzt beschriebenen beiden Ausführungsformen erlauben eine noch kompaktere Bauweise des Abgaswärmetauschers. The exhaust gas heat exchanger consists of a suitable stainless steel. All connections between the individual parts of the exhaust gas heat exchanger are preferably made by soldering.
In the exemplary embodiment according to FIG. 1, which shows a top view without a cover plate 22, the collecting space 4 and the distribution space 4 are arranged on opposite sides 12 of the exhaust gas heat exchanger in projecting areas 13.
For this reason, two types of heat exchanger plates 1 are required to form the flow channels 5 and 7. The flow channels 5 are provided for water W and the flow channels 7 for exhaust gas G. The heat exchanger plates 1 are connected in pairs at their peripheral edges 2. They are also connected at their peripheral features 8, which has been shown as a thick line in the plan view and which comprises an area of the exhaust gas heat exchanger which is smaller than the total area of the heat exchanger plates 1 or smaller than the area enclosed by the edge 10 . The area enclosed by the peripheral configuration 8 includes the inlet openings 3 and the outlet openings 3 for the cooling water and consists of sections 9 running in the vicinity of the edge 10 and sections 11 which cross the heat exchanger plates 1. This crossing can run at any angle to the longitudinal axis of the heat exchanger plates 1 and is arranged perpendicular to the longitudinal axis in FIG. 1. The circumferential shape 8 is embossed in a U-shape in the heat exchanger plates 1, as the sketchy FIGS. 1a and 1b show. 1b also shows that the flow channels 5 for the cooling water W end at the circumferential configuration 8, but they continue to flow channels 7 for the exhaust gas G into the collecting space 6 or into the tube sheet 15. The sketch 1c shows the cross section of the flow channels 7 in this area. Inside the flow channels 7 there are inner inserts 17 which extend over the entire length of the flow channels 7, even if they have not been shown in FIG. 1a. Where the circumferential features 8 of two heat exchanger plates 1 are connected to one another, both the flow channel 5 is sealed off from the flow channel 7, and both channels 5 and 7 to the outside, so that no outer housing has to enclose the stack of heat exchanger plates 1. 1c shows that the flow channels 7 each have two longitudinal walls 16. In the exemplary embodiment shown, the tube sheet 15 has individual openings which correspond to the cross section of the flow channels 7 in order to be able to accommodate them. In an embodiment not shown, the ends of the flow channels 7 are widened, so that the longitudinal walls 16 of the adjacent channels 7 can be connected to one another, as a result of which the tube sheet 15 can be omitted because an opening is present directly in the collecting space 6 which can accommodate all of the flow channels 7 .
Studs 20 have been drawn in on the uppermost heat exchanger plate of FIG. 1. These knobs 20 can also be found in FIG. 3, which shows the section C - C from FIG. 1, with the difference that the cover plate 22, which delimits a space 24 to the first heat exchanger plate 1, has been drawn in the section C - C . The knobs 20 extend into the flow channel 5, in which water W flows. The knobs 16 of the one heat exchanger plate 1 are connected to the knobs 16 of the next heat exchanger plate 1. 3 also shows the design of the collecting or distribution rooms 4. Pot-like depressions 14 are formed around the openings 3 in the heat exchanger plates 1 and, lying on a vertical line, form the collecting and distribution space 4, which is in connection with the flow channels 5, so that the water W can flow in accordance with the flow arrows shown . The formation of the edges 2 with the circumferential shape 8 in the area of the collecting and distribution spaces 4 can also be seen in FIG. 3. The cover plate 22 makes it possible to freely select the position of the connecting pieces 19 for the water W, and that at any point on the entire plate 22.
4 shows a view from the direction of a collecting space 6 for the exhaust gas G. A part of the tube sheet 15 can be seen, in which the flow channels 7 with inner inserts 17 open. The connection to the exhaust pipe, not shown, can be made here by means of a clamping ring 21. The exhaust gas heat exchanger is fastened, for example in a vehicle, by suitable brackets 23
The side view of the exhaust gas heat exchanger shown in FIG. 2 shows another embodiment in which the inlet and outlet connections 19 for the water W have been arranged on a common side 12 of the exhaust gas heat exchanger, in the drawing on the rear side, not shown. This has the advantage that all heat exchanger plates 1 can be designed the same. From this side view, the area B emerges, which is determined by the peripheral shape 8. Within this area B, the flow channels 5 and 7 run in parallel. Outside of this area, the flow channels 7 open into the collecting spaces 6. The flow channels 5 end where the circumferential shape 8 crosses the heat exchanger plates 1.
5 to 9 show two other embodiments in which inner inserts 17 have been completely dispensed with. As a result, the number of individual parts is lower, with the result that the manufacturing process can be made simpler. The top views in FIGS. 5 and 7 were each drawn without a cover plate 22. The heat exchanger plates 1 are provided with an undulating wall, which have been realized by alternating longitudinal beads 25 and 26.
The embodiment shown in FIGS. 5 and 6 differs from the embodiment of FIGS. 7 to 9 in that the first-mentioned embodiment has no continuous first beads 25. These beads 25 have been replaced by support knobs 20 arranged in a row. As a result, the flow resistance for the cooling water W in the channels 5 has been reduced.
5 it has been made clear by flow arrows that the water can flow in and out more easily, as a comparison with FIG. 7 shows. Another difference between these two embodiments lies in the arrangement of the collecting and distribution spaces 4. FIGS. 5 and 6 show no projecting areas 13 of the heat exchanger plates 1. The collecting and distribution spaces 4 are arranged within the rectangular basic shape of the heat exchanger plates 1. 7 to 9 projecting areas 13 are provided, in which the collection and distribution spaces 4 are located. The last two embodiments described allow an even more compact design of the exhaust gas heat exchanger.

BezugszeichenlisteReference list

11
WärmetauscherplattenHeat exchanger plates
22nd
RandflanschEdge flange
33rd
Öffnungen in PlattenOpenings in plates
44th
Sammelräume und VerteilerräumeCollection rooms and distribution rooms
55
Strömungskanäle für WasserFlow channels for water
66
Sammelräume für AbgasCollection rooms for exhaust gas
77
Strömungskanäle für AbgasFlow channels for exhaust gas
88th
umlaufende Ausprägungall-round expression
99
Abschnitt der umlaufenmden AusprägungSection of the circulating expression
1010th
Randedge
1111
anderer Abschnitt von 8other section of 8
1212th
eine Seite des Wärmetauschersone side of the heat exchanger
1313
auskragender Bereichcantilevered area
1414
topfartige Vertiefungpot-like depression
1515
RohrbödenTube sheets
1616
LängswändeLongitudinal walls
1717th
InneneinsätzeInserts
1818th
1919th
AnschlußstutzenConnecting piece
2020th
NoppenPimples
2121
SpannringTension ring
2222
AbdeckplatteCover plate
2323
Halterungbracket
2424th
Raumroom
2525th
1. Sicken1. beads
2626
2. Sicken2. beads
BB
BereichArea
GG
AbgasExhaust gas
WW
Wasserwater

Claims (14)

Wärmetauscher, insbesondere für den Wärmeaustausch zwischen einem Gas und einer Flüssigkeit, beispielsweise mit Wasser gekühlte Ladeluft - oder Abgaswärmetauscher, umfassend einen Stapel aus schalenförmigen Wärmetauscherplatten (1), die spiegelbildlich zusammengefügt und am Randflansch (2) und um ihren auf einer Linie liegenden Öffnungen (3) so verbunden sind, daß sie Sammel-und Verteilerräume (4) für eines der Mittel und dessen horizontale Strömungskanäle (5) in sich einschließen, sowie mit Sammelräumen (6), in denen die Strömungskanäle (7) für das andere Mittel münden,
dadurch gekennzeichnet, daß der Stapel schalenförmiger Wärmetauscherplatten (1) getrennte Strömungskanäle (7) für das zweite Mittel in sich einschließt, daß die Wärmetauscherplatten (1) eine umlaufende Ausprägung (8) aufweisen, die wenigstens eine Einlaß-und eine Auslaßöffnung (3) für das eine Mittel umfassen, daß die umlaufende Ausprägung (8) der einen Wärmetauscherplatte (1) mit der Ausprägung (8) der nächsten Wärmetauscherplatte (1) verbunden ist und beide innerhalb des von der umlaufenden Ausprägung (8) eingeschlossenen Bereiches (B) angeordneten parallelen Strömungskanäle (5; 7) voneinander und nach außen hin trennt und daß die Strömungskanäle (7) für das zweite Mittel außerhalb der umlaufenden Ausprägung (8) in wenigstens einen Sammelraum (6) münden. Heat exchanger, in particular for the exchange of heat between a gas and a liquid, for example charge air or exhaust gas heat exchanger cooled with water, comprising a stack of shell-shaped heat exchanger plates (1) which are assembled in mirror image and at the edge flange (2) and around their openings lying in a line ( 3) are connected in such a way that they include collection and distribution spaces (4) for one of the means and its horizontal flow channels (5), as well as with collection spaces (6) in which the flow channels (7) open for the other means,
characterized in that the stack of bowl-shaped heat exchanger plates (1) includes separate flow channels (7) for the second agent, that the heat exchanger plates (1) have a circumferential shape (8) which comprise at least one inlet and one outlet opening (3) for the one agent, that the peripheral shape (8) of one heat exchanger plate (1) is connected to the shape (8) of the next heat exchanger plate (1) and both parallel flow channels (5; 7) arranged within the area (B) enclosed by the peripheral shape (8) ) separates from each other and towards the outside and that the flow channels (7) for the second agent open outside the circumferential shape (8) in at least one collecting space (6). Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die umlaufende Ausprägung (8) eine geeignete Querschnittsform aufweist, vorzugsweise etwa u-förmig ausgebildet ist und Abschnitte (9) besitzt, die in der Nähe des Randes (10) der Wärmetauscherplatten (1) verlaufen und weitere Abschnitte (11), die die Wärmetauscherplatten (1) kreuzen.Heat exchanger according to claim 1, characterized in that the rotating Expression (8) has a suitable cross-sectional shape, preferably is approximately U-shaped and has sections (9) in the vicinity of the Edge (10) of the heat exchanger plates (1) and further sections (11), which cross the heat exchanger plates (1). Wärmetauscher nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß samtliche Warmetauscherplatten (1) gleich sind und der Sammel-und der Verteilerraum (4) für das eine Mittel an der gleichen Seite (12) des Wärmetauschers angeordnet sind. Heat exchanger according to claims 1 and 2, characterized in that all heat exchanger plates (1) are the same and the collection and distribution space (4) for the one agent on the same side (12) of the heat exchanger are arranged. Wärmetauscher nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß zwei Arten Wärmetauscherplatten (1) vorgesehen sind und der Sammelraum (4) an einer Seite (12) und der Verteilerraum (4) an der gegenüberliegenden Seite (12) des Wärmetauschers angeordnet sind.Heat exchanger according to claims 1 and 2, characterized in that two types of heat exchanger plates (1) are provided and the collecting space (4) on one side (12) and the distribution space (4) on the opposite side (12) of the heat exchanger are arranged. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Sammel-und der Verteilerraum (4) innerhalb des Bereiches (B) beider Strömungskanäle (5; 7) angeordnet sind.Heat exchanger according to one of claims 1 to 4, characterized in that the collection and distribution space (4) within the area (B) of both Flow channels (5; 7) are arranged. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Sammel-und der Verteilerraum (4) außerhalb des Bereiches (B) beider Strömungskanäle (5; 7) in auskragenden Bereichen (13) angeordnet sind.Heat exchanger according to one of claims 1 to 4, characterized in that the collection and distribution space (4) outside the area (B) of both Flow channels (5; 7) are arranged in projecting areas (13). Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Sammel-und der Verteilerraum (4) durch in die Wärmetauscherplatten (1), um die Öffnungen (3) herum, eingeprägte topfartige Vertiefungen (14) gebildet sind, die mit den topfartigen Vertiefungen (14) folgenden Wärmetauscherplatte (1) verbunden sind.Heat exchanger according to one of the preceding claims, characterized in that that the collection and distribution space (4) through in the heat exchanger plates (1), around the openings (3), embossed pot-like depressions (14) are formed, with the pot-like depressions (14) following the heat exchanger plate (1) are connected. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Strömungskanäle (7) für das andere Mittel in Rohrböden (15) münden, deren Öffnungen dem Querschnitt der Strömungskanäle (7) angepaßt sind, um dieselben in sich aufzunehmen und mit Sammelräumen (6) an den Rohrböden (15).Heat exchanger according to one of the preceding claims, characterized in that that the flow channels (7) for the other agent in tube sheets (15) open, the openings of which are adapted to the cross section of the flow channels (7) are in order to take them in and with collection rooms (6) to the Tube sheets (15). Wärmetauscher nach einem der vorstehenden Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Enden der Strömungskanäle (7) für das andere Mittel derart umgeformt sind, daß ihre Längswände (16) aneinanderliegen und dicht zu verbinden sind und daß die Strömungskanäle (7) ohne Rohrboden (15) in einer Öffnung der Sammelräume (6) münden. Heat exchanger according to one of the preceding claims 1 to 7, characterized characterized in that the ends of the flow channels (7) for the other agent are reshaped such that their longitudinal walls (16) abut one another and close together connect and that the flow channels (7) without a tube sheet (15) in one Opening of the collection rooms (6) open. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß in die Wärmetauscherplatten (1) Abstütznoppen (20) eingeprägt sind, die mit den Abstütznoppen (20) der benachbarten Platte (1) verbunden sind und deren Höhe gleich der Höhe der umlaufenden Ausprägung (8) ist und daß der die Abstütznoppen (20) aufweisende Strömungskanal (5) für die Kühlflüssigkeit vorgesehen ist.Heat exchanger according to one of the preceding claims, characterized in that that in the heat exchanger plates (1) support knobs (20) are stamped are connected to the support knobs (20) of the adjacent plate (1) and whose height is equal to the height of the peripheral expression (8) and that the the flow channel (5) for the cooling liquid which has support knobs (20) is provided. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Strömungskanäle (7) für das Gas Inneneinsätze (17) aufweisen.Heat exchanger according to one of the preceding claims, characterized in that that the flow channels (7) for the gas have inner inserts (17). Wärmeaustauscher nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß beide Strömungskanäle (5, 7) frei von Inneneinsätzen (17) sind und die Wärmetauscherplatten (1) mit längsverlaufenden Sicken (25; 26)versehen sind, die, in Querrichtung gesehen, alternieren, so daß sich beim Stapeln der Wärmetauscherplatten (1) Strömungskanäle (5, 7) mit einer wellenförmigen Wandung herausbilden, derart, daß sich jede zweite Sicke (25) mit jeder zweiten Sicke (25) der benachbarten Wärmetauscherplatte (1) berührt und verbunden ist, wodurch die Strömungskanäle (5) für das eine Mittel, vorzugsweise für das Kühlwasser gebildet sind
und daß jede erste Sicke (26) der Wärmetauscherplatte (1) mit jeder ersten Sicke (26) der benachbarten Wärmetauscherplatte (1) den benachbarten Strömungskanal (7) für das andere Mittel, vorzugsweise für das Abgas, bildet, wobei die gegenüberliegenden ersten Sicken (26) den Strömungskanal (7) jeweils einengen sich aber nicht berühren.Heat exchanger according to one of claims 1 to 10, characterized in that both flow channels (5, 7) are free of internal inserts (17) and the heat exchanger plates (1) are provided with longitudinal beads (25; 26) which, viewed in the transverse direction, alternate so that when the heat exchanger plates (1) are stacked, flow channels (5, 7) with a corrugated wall form in such a way that every other bead (25) touches and connects with every second bead (25) of the adjacent heat exchanger plate (1) , whereby the flow channels (5) are formed for the one means, preferably for the cooling water
and that each first bead (26) of the heat exchanger plate (1) with each first bead (26) of the adjacent heat exchanger plate (1) forms the adjacent flow channel (7) for the other agent, preferably for the exhaust gas, the opposite first beads ( 26) narrow the flow channel (7) but do not touch each other. Wärmetauscher nach Anspruch 12, dadurch gekennzeichnet, daß die Sickenhöhe jeder zweiten Sicke (25) identisch mit der Höhe der umlaufenden Ausprägung (8) ist und die jeweils zweiten Sicken entweder über die Länge des von der umlaufenden Ausprägung (8) eingeschlossenen Bereiches (B) der Wärmetauscherplatten (1) durchlaufen oder unterbrochen sind und lediglich einzelne in Reihe liegende Abstütznoppen (20) bilden. Heat exchanger according to claim 12, characterized in that the bead height every second bead (25) is identical to the height of the circumferential Characteristic (8) and the respective second beads either over the length of the area (B) of the heat exchanger plates enclosed by the peripheral shape (8) (1) run through or interrupted and only individual form support knobs (20) in line. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Stapel der Wärmetauscherplatten (1) eine Abdeckplatte (22) aufweist, die zur obersten Wärmetauscherplatte (1) des Stapels hin einen Raum (24) für das flüssige Kühlmittel ausbildet und die der Flexibilität der Anschlußlage dient, indem sie mindestens einen Anschlußstutzen (19) an beliebiger Stelle aufweist.Heat exchanger according to one of the preceding claims, characterized in that that the stack of heat exchanger plates (1) has a cover plate (22) has a space to the top heat exchanger plate (1) of the stack (24) for the liquid coolant and the flexibility of the connection position serves by having at least one connecting piece (19) at any point.
EP99119392A 1998-10-09 1999-09-29 Heat exchanger, more particularly for gases and liquids Expired - Lifetime EP0992756B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19846518 1998-10-09
DE19846518A DE19846518B4 (en) 1998-10-09 1998-10-09 Heat exchangers, in particular for gases and liquids

Publications (3)

Publication Number Publication Date
EP0992756A2 true EP0992756A2 (en) 2000-04-12
EP0992756A3 EP0992756A3 (en) 2000-12-13
EP0992756B1 EP0992756B1 (en) 2002-11-27

Family

ID=7883908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99119392A Expired - Lifetime EP0992756B1 (en) 1998-10-09 1999-09-29 Heat exchanger, more particularly for gases and liquids

Country Status (6)

Country Link
US (1) US6250380B1 (en)
EP (1) EP0992756B1 (en)
JP (1) JP2000121278A (en)
AT (1) ATE228639T1 (en)
DE (2) DE19846518B4 (en)
ES (1) ES2188080T3 (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001098723A1 (en) * 2000-06-21 2001-12-27 Serck Heat Transfert Limited Exhaust gas cooler
EP1376043A2 (en) 2002-06-28 2004-01-02 Modine Manufacturing Company Heat exchanger with diffuser
WO2004106834A2 (en) * 2003-05-27 2004-12-09 Valeo Thermique Moteur Plate heat exchanger in particular a cooler for recirculated exhaust gases
EP1489373A2 (en) 2003-06-18 2004-12-22 Modine Manufacturing Company Plate heat exchanger without casing and with headers
EP1626238A1 (en) * 2004-08-14 2006-02-15 Modine Manufacturing Company Heat exchanger having flat tubes
US7036565B2 (en) 2003-06-26 2006-05-02 Modine Manufacturing Company Exhaust heat exchanger
EP1710526A1 (en) * 2005-03-26 2006-10-11 Modine Manufacturing Company Heat exchanger, in particular intercooler
US7159650B2 (en) 2002-06-28 2007-01-09 Modine Manufacturing Company Heat exchanger
DE102009012509A1 (en) 2009-03-10 2010-09-16 Modine Manufacturing Co., Racine Heat exchanger e.g. charge air cooler, for internal combustion engine, has tubular plate comprising four edge sides in which one of edge sides is flexible and establishes operative connection with end portion of side part at rear side
WO2011023825A1 (en) * 2009-08-31 2011-03-03 Valeo Systemes Thermiques Heat exchanger
EP2410277A1 (en) * 2002-07-04 2012-01-25 Behr GmbH & Co. KG Heat exchanger, in particular charge air cooler for motor vehicles

Families Citing this family (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10120483A1 (en) * 2001-04-25 2002-10-31 Modine Mfg Co Arrangement for cooling
US6629561B2 (en) * 2001-06-08 2003-10-07 Visteon Global Technologies, Inc. Module for a heat exchanger having improved thermal characteristics
SE519306C2 (en) * 2001-07-09 2003-02-11 Alfa Laval Corp Ab Heat transfer plate, plate package and plate heat exchanger
US7077190B2 (en) * 2001-07-10 2006-07-18 Denso Corporation Exhaust gas heat exchanger
DE10302948A1 (en) * 2003-01-24 2004-08-05 Behr Gmbh & Co. Kg Heat exchanger, in particular exhaust gas cooler for motor vehicles
EP1657512B2 (en) * 2004-11-10 2010-06-16 Modine Manufacturing Company Heat exchanger with open profile as housing
DE102004056592A1 (en) * 2004-11-23 2006-05-24 Behr Gmbh & Co. Kg Low-temperature coolant radiator
KR100579560B1 (en) * 2004-12-10 2006-05-15 엘지전자 주식회사 Exhaust Gas Heat Exchanger of Cogeneration System
JP4527557B2 (en) * 2005-01-26 2010-08-18 株式会社ティラド Heat exchanger
JP2006284165A (en) * 2005-03-07 2006-10-19 Denso Corp Exhaust gas heat exchanger
GB2426322B (en) * 2005-07-22 2007-09-05 Michael Tate Exhaust gas heat exchanger
US7992628B2 (en) * 2006-05-09 2011-08-09 Modine Manufacturing Company Multi-passing liquid cooled charge air cooler with coolant bypass ports for improved flow distribution
US8985198B2 (en) * 2006-08-18 2015-03-24 Modine Manufacturing Company Stacked/bar plate charge air cooler including inlet and outlet tanks
US20080041556A1 (en) * 2006-08-18 2008-02-21 Modine Manufacutring Company Stacked/bar plate charge air cooler including inlet and outlet tanks
US7610949B2 (en) * 2006-11-13 2009-11-03 Dana Canada Corporation Heat exchanger with bypass
US20080141985A1 (en) * 2006-12-18 2008-06-19 Schernecker Jeff L Layered core EGR cooler
DE102007040793A1 (en) 2007-08-28 2009-03-05 Behr Gmbh & Co. Kg heat exchangers
US20090056909A1 (en) * 2007-08-30 2009-03-05 Braun Catherine R Heat exchanger having an internal bypass
EP2136175B1 (en) * 2008-06-21 2016-06-22 Joachim Schult Heat transfer plate, plate pair, plate stack, compact plate heat exchanger and its manufacturing process
DE102009010039B4 (en) 2009-02-21 2012-09-20 Modine Manufacturing Co. heat exchangers
EP2228615B1 (en) * 2009-03-12 2018-04-25 MAHLE Behr GmbH & Co. KG Plate heat exchanger, in particular for heat recovery from exhaust gases of a motor vehicle
US9250019B2 (en) * 2009-07-27 2016-02-02 Korea Delphi Automotive Systems Corporation Plate heat exchanger
JP5620685B2 (en) * 2010-02-02 2014-11-05 国立大学法人東京大学 Heat exchanger
AU2011201083B2 (en) * 2010-03-18 2013-12-05 Modine Manufacturing Company Heat exchanger and method of manufacturing the same
ITBO20100474A1 (en) * 2010-07-27 2012-01-28 Magneti Marelli Spa SILENCER WITH INTEGRATED HEAT EXCHANGER
DE202011002197U1 (en) * 2011-02-01 2012-02-02 Dana Gmbh heat exchangers
WO2012151398A1 (en) * 2011-05-03 2012-11-08 Meadwestvaco Calmar, Inc. Liquid dispenser containers
CN103906987B (en) 2011-09-09 2016-08-24 达纳加拿大公司 Plywood exhaust recovery device
WO2014052309A1 (en) 2012-09-25 2014-04-03 Modine Manufacturing Company Heat exchanger
US9989322B2 (en) 2013-03-01 2018-06-05 Dana Canada Corporation Heat recovery device with improved lightweight flow coupling chamber and insertable valve
KR101749059B1 (en) * 2015-09-04 2017-06-20 주식회사 경동나비엔 Wave plate heat exchanger
US20170089643A1 (en) * 2015-09-25 2017-03-30 Westinghouse Electric Company, Llc. Heat Exchanger
US11255615B2 (en) * 2018-01-23 2022-02-22 Hamilton Sundstrand Corporation Heat exchanger flexible manifold
JP7182395B2 (en) * 2018-08-09 2022-12-02 リンナイ株式会社 Heat exchanger
US11280559B2 (en) * 2020-05-12 2022-03-22 Hanon Systems Dumbbell shaped plate fin
JP7534976B2 (en) * 2021-02-05 2024-08-15 三菱重工業株式会社 Heat exchange core and heat exchanger

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0677715A1 (en) 1994-04-14 1995-10-18 Behr GmbH & Co. Heat exchanger for cooling of the exhaust gas from an automotive engine

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE128287C (en) *
FR850948A (en) * 1938-09-08 1939-12-29 Advanced blade radiator
US3240268A (en) * 1962-01-02 1966-03-15 Gen Motors Corp Stacked caseless heat exchangers
US4310960A (en) * 1973-04-16 1982-01-19 The Garrett Corporation Method of fabrication of a formed plate, counterflow fluid heat exchanger and apparatus thereof
FR2575279B1 (en) * 1984-12-21 1989-07-07 Barriquand PLATE HEAT EXCHANGER
DE3832013C2 (en) * 1987-09-17 1996-08-01 Dancho Zochev Dipl Ing Donkov Reciprocating piston internal combustion engine with crankcase charge air pumps
GB2211283B (en) * 1987-10-20 1992-04-15 Rolls Royce Plc Heat exchanger
JPH02277920A (en) * 1989-04-20 1990-11-14 Honda Motor Co Ltd Water-cooled inter-cooler
DE4223321A1 (en) * 1992-07-16 1994-01-20 Tenez A S Welded plate heat exchanger
DE4301629A1 (en) * 1993-01-22 1994-07-28 Behr Gmbh & Co Liq. evaporator with enhanced efficiency
JP3359946B2 (en) * 1993-03-04 2002-12-24 東京ラヂエーター製造株式会社 Stacked heat exchanger
DE4307503C2 (en) * 1993-03-10 1995-01-19 Mtu Friedrichshafen Gmbh Heat exchanger, in particular charge air cooler of an internal combustion engine
DE4307504C1 (en) * 1993-03-10 1994-09-22 Mtu Friedrichshafen Gmbh Heat exchanger, in particular charge air cooler of an internal combustion engine
DE19511991C2 (en) * 1995-03-31 2002-06-13 Behr Gmbh & Co Plate heat exchanger
US5964280A (en) * 1996-07-16 1999-10-12 Modine Manufacturing Company Multiple fluid path plate heat exchanger
DE19836889A1 (en) * 1998-08-14 2000-02-17 Modine Mfg Co Exhaust gas heat exchanger

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0677715A1 (en) 1994-04-14 1995-10-18 Behr GmbH & Co. Heat exchanger for cooling of the exhaust gas from an automotive engine

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001098723A1 (en) * 2000-06-21 2001-12-27 Serck Heat Transfert Limited Exhaust gas cooler
GB2380253A (en) * 2000-06-21 2003-04-02 Serck Heat Transfer Ltd Exhaust gas cooler
GB2380253B (en) * 2000-06-21 2005-01-19 Serck Heat Transfer Ltd Exhaust gas cooler
EP1376043A2 (en) 2002-06-28 2004-01-02 Modine Manufacturing Company Heat exchanger with diffuser
DE10229083A1 (en) * 2002-06-28 2004-01-15 Modine Manufacturing Co., Racine Heat exchanger with a diffuser
EP1376043A3 (en) * 2002-06-28 2008-05-28 Modine Manufacturing Company Heat exchanger with diffuser
US7159650B2 (en) 2002-06-28 2007-01-09 Modine Manufacturing Company Heat exchanger
EP2410277A1 (en) * 2002-07-04 2012-01-25 Behr GmbH & Co. KG Heat exchanger, in particular charge air cooler for motor vehicles
WO2004106834A2 (en) * 2003-05-27 2004-12-09 Valeo Thermique Moteur Plate heat exchanger in particular a cooler for recirculated exhaust gases
WO2004106834A3 (en) * 2003-05-27 2005-03-24 Valeo Thermique Moteur Sa Plate heat exchanger in particular a cooler for recirculated exhaust gases
US7055584B2 (en) 2003-06-18 2006-06-06 Modine Manufacturing Company Heat exchanger with valve
EP1489373A3 (en) * 2003-06-18 2009-09-30 Modine Manufacturing Company Plate heat exchanger without casing and with headers
EP1489373A2 (en) 2003-06-18 2004-12-22 Modine Manufacturing Company Plate heat exchanger without casing and with headers
US7036565B2 (en) 2003-06-26 2006-05-02 Modine Manufacturing Company Exhaust heat exchanger
EP1491837A3 (en) * 2003-06-26 2008-05-14 Modine Manufacturing Company Plate heat exchanger without casing
EP1626238A1 (en) * 2004-08-14 2006-02-15 Modine Manufacturing Company Heat exchanger having flat tubes
EP1710526A1 (en) * 2005-03-26 2006-10-11 Modine Manufacturing Company Heat exchanger, in particular intercooler
DE102009012509A1 (en) 2009-03-10 2010-09-16 Modine Manufacturing Co., Racine Heat exchanger e.g. charge air cooler, for internal combustion engine, has tubular plate comprising four edge sides in which one of edge sides is flexible and establishes operative connection with end portion of side part at rear side
WO2011023825A1 (en) * 2009-08-31 2011-03-03 Valeo Systemes Thermiques Heat exchanger
FR2949554A1 (en) * 2009-08-31 2011-03-04 Valeo Systemes Thermiques HEAT EXCHANGER
US9494369B2 (en) 2009-08-31 2016-11-15 Valeo Systemes Thermiques Heat exchanger

Also Published As

Publication number Publication date
JP2000121278A (en) 2000-04-28
DE59903529D1 (en) 2003-01-09
DE19846518A1 (en) 2000-04-13
ES2188080T3 (en) 2003-06-16
DE19846518B4 (en) 2007-09-20
EP0992756A3 (en) 2000-12-13
EP0992756B1 (en) 2002-11-27
ATE228639T1 (en) 2002-12-15
US6250380B1 (en) 2001-06-26

Similar Documents

Publication Publication Date Title
DE19846518B4 (en) Heat exchangers, in particular for gases and liquids
DE3017701C2 (en) Plate heat exchanger in stack design for at least three heat exchanger media
EP0974804B1 (en) Heat exchanger, more particularly heat exchanger for exhaust gases
DE69409647T2 (en) PLATE HEAT EXCHANGER
DE68902783T2 (en) HEAT EXCHANGER.
DE69316121T2 (en) Plate heat exchanger
DE60010227T2 (en) HOUSING-FREE HEAT EXCHANGER
EP1910764B2 (en) Plate element for a plate cooler
WO2004036134A1 (en) Stacked plate heat exchanger
EP1273864B1 (en) Heat exchanger
DE2701633A1 (en) HEAT EXCHANGER
DE2951352C2 (en) Flat tube heat exchanger
DE10152363A1 (en) Caseless plate heat exchanger
EP1256772A2 (en) Heat exchanger
DE19543234C2 (en) Finned heat exchanger
EP0044561A2 (en) Heat exchanger, in particular for heat exchange between gaseous fluids
EP0826941A2 (en) Tubular heat exchange core
EP1657512B1 (en) Heat exchanger with open profile as housing
DE4305945A1 (en) Heat exchanger, in particular for motor vehicles
DE2639371A1 (en) PLATE HEAT EXCHANGER
EP0633444B1 (en) Heat exchanger with several parallel exchange tubes
DE10153877A1 (en) Heat exchanger
DE69903895T2 (en) heat exchangers
DE60024723T2 (en) Plate with beads for heat exchangers and their manufacture
DE102004007510B4 (en) Heat exchangers, in particular oil coolers for motor vehicles

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20010613

17Q First examination report despatched

Effective date: 20010719

AKX Designation fees paid

Free format text: AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20021127

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20021127

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20021127

REF Corresponds to:

Ref document number: 228639

Country of ref document: AT

Date of ref document: 20021215

Kind code of ref document: T

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 59903529

Country of ref document: DE

Date of ref document: 20030109

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030227

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030227

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20030210

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2188080

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

Ref document number: 0992756E

Country of ref document: IE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030929

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030929

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030929

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030828

BERE Be: lapsed

Owner name: *MODINE MFG CY

Effective date: 20030930

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20110920

Year of fee payment: 13

Ref country code: ES

Payment date: 20110926

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20110927

Year of fee payment: 13

Ref country code: IT

Payment date: 20110922

Year of fee payment: 13

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20130401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120930

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120929

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130401

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20131021

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120930

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20130925

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20130920

Year of fee payment: 15

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20140929

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150529

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140929

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140930

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20150929

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59903529

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170401