EP0974804A2 - Heat exchanger, more particularly heat exchanger for exhaust gases - Google Patents

Heat exchanger, more particularly heat exchanger for exhaust gases Download PDF

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Publication number
EP0974804A2
EP0974804A2 EP99113222A EP99113222A EP0974804A2 EP 0974804 A2 EP0974804 A2 EP 0974804A2 EP 99113222 A EP99113222 A EP 99113222A EP 99113222 A EP99113222 A EP 99113222A EP 0974804 A2 EP0974804 A2 EP 0974804A2
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EP
European Patent Office
Prior art keywords
heat exchanger
flow channels
plates
channels
exhaust gas
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
EP99113222A
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German (de)
French (fr)
Other versions
EP0974804A3 (en
EP0974804B1 (en
Inventor
Roland Dipl.-Ing. Strähle
Wolfgang Dipl.-Ing. Knecht
Viktor Brost
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Modine Manufacturing Co
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Modine Manufacturing Co
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Publication date
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Publication of EP0974804A2 publication Critical patent/EP0974804A2/en
Publication of EP0974804A3 publication Critical patent/EP0974804A3/en
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Publication of EP0974804B1 publication Critical patent/EP0974804B1/en
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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
    • F28F3/044—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 the deformations being pontual, e.g. dimples
    • 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
    • F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • F28F2240/00—Spacing means
    • 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
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the invention relates to a heat exchanger, in particular an exhaust gas heat exchanger, consisting of a stack of heat exchanger plates that separate flow form channels that run parallel to each other, with collecting spaces, inlet and outlet for the exhaust gas and for the preferably liquid coolant.
  • exhaust gas heat exchangers were often designed as so-called tube bundle heat exchangers, which consist of a bundle of round tubes that end at both ends in tube sheets.
  • the exhaust gas inlets and outlets are on opposite ends. Collection rooms are also formed there, from which the exhaust gas is distributed to the individual tubes of the bundle and flows through it.
  • the inlets and outlets are arranged in relative proximity to the other inlets and outlets so that the flow directions of the two media intersect in this area.
  • Such tube heat exchangers, as exhaust gas heat exchangers were later removed because their performance is unsatisfactory and too large.
  • the plate package is designed according to the so-called rod-plate construction, which means that there are many individual components that have to be joined together. This can be seen as expensive.
  • the object of the invention is to propose a compact and efficient heat exchanger which is inexpensive to manufacture and which should have better flexibility with regard to the installation space and the connection positions.
  • the solution according to the invention results from the patent claims.
  • lamellae In the flow channels for the exhaust gas, lamellae are inserted, which can be rectangular lamellae or can also have a shape other than rectangular. Rectangular fins on the one hand ensure good heat transfer without, on the other hand, offering the exhaust gas possibilities to deposit and over time to close off the flow channels.
  • the heat exchanger plates have knobs on the coolant side. The knobs of one heat exchanger plate touch the knobs of the next heat exchanger plate, so that they can be connected to each other and contribute to the compactness of the heat exchanger.
  • lamellae or other turbulence-generating elements can also be provided instead of these knobs.
  • Both flow channels are formed by joining heat exchanger plates, all of which have the same shape, which is very advantageous in terms of production technology and helps to reduce costs.
  • the different length of the flow channels has also been realized by this type of heat exchanger plate.
  • the heat exchanger plates have edges that are formed on one side over the entire length of the plates, for example downwards with respect to the plate level, and that have an edge configuration over the length of the shorter flow channels, which is opposite to the deformation, i.e. above the plate level (Front) is formed.
  • An advantageous embodiment also has the knobs already mentioned on the same plate side (front side). Two heat exchanger plates are placed together with their edges that extend over the entire length, i.e. with the rear, and form the one flow channel between them.
  • the other flow channel is realized by placing the next heat exchanger plate on the front side on the front side, which is then followed by the back side on the back side, etc.
  • the inventive idea with shorter and longer flow channels can of course also be realized - in contrast to the above - by instead of the edge reshaping and edge embossing rods are inserted, which have the length of the shorter flow channels and which are connected to the plates.
  • the plates are preferably only folded over at the opposite longitudinal edges. Two such plates are then put together like a box and form within a flow channel.
  • the adjacent flow channel is formed by the rods mentioned or delimited on the long sides.
  • the water-cooled exhaust gas heat exchanger 1 is shown in FIGS. 1 to 6 in a first embodiment.
  • the exhaust gas heat exchanger consists entirely of a suitable stainless steel. All connections between the parts are made by soldering.
  • Fig. 1 the left collecting space 4 for the cooling water and the collecting space 7 for the exhaust gas was drawn in section to show details.
  • the exhaust gas flows through the inlet 14 into the collecting space 7 and via the flow channels 2 in a straight path through the heat exchanger 1 in order to leave it again via the outlet 15.
  • the inlets and outlets 14, 15 have suitable connections, which have been shown here simply as connecting flanges.
  • the cooling water flows at the inlet 8 into the collecting space 4 and is distributed over the flow channels 3, which run parallel to the flow channels 2 and alternate with them.
  • the collecting spaces 4 have been formed from the tube sheets 5 and 6, the jacket 5 of the collecting spaces 4 being produced in this exemplary embodiment by the erected edge 12 of the tube sheet 5, which forms a connecting surface 13 with the edge of the tube sheet 6.
  • the stack consisting of identical heat exchanger plates P1 and P2 has shorter flow channels 3 and longer flow channels 2, which is explained in more detail below.
  • the different lengths L and I of the flow channels 2 and 3 were shown in FIG. 1.
  • the longer flow channels 2 pass through the collecting spaces 4 and are sealingly fastened in the openings 17 of the second tube sheet 6. (see also FIG. 4, in which three openings 17 for the three flow channels 2 are shown)
  • FIG. 4 and also FIG. 3 further show that 2 rectangular lamellae 25 have been inserted in the flow channels in order to improve the heat exchange.
  • the fins 25 are connected to the heat exchanger plates P1 and P2 or to the walls of the flow channels 2.
  • the tube sheet 5 merely has an opening 16, as shown in FIG. 7.
  • the opening 16 is a rectangle. 6 shows, in an enlarged section, the fastening of the heat exchanger plates P1 and P2 in this opening 16.
  • an end plate 11 has been drawn.
  • An identical plate 11 is located at the lower edge of the opening 16, not shown.
  • the end plates 11 cover the heat exchanger plates P1; P2 completely (Fig. 2) and limit the upper and lower flow channel 3, which is intended for cooling water.
  • identical heat exchanger plates P1 and P2 were used, which have been shown in FIGS. 10 to 12.
  • the heat exchanger plates P1; P2 are rectangular here and consequently have two opposite longitudinal edges 21. On these longitudinal edges 21 there is a deformation 22 which extends over the entire plate length L and is directed towards the rear side R of the plate plane. Directed to the front F, the heat exchanger plates P1 and P2 have on the two longitudinal edges 21 an edge configuration 23 which extends only over the length l of the heat exchanger plates P1 and P2. In connection with FIG. 6 it can be seen that two heat exchanger plates P1 and P2 are placed against one another with their rear sides R and form within the flow channel 2, which extends over the total length L. The heat exchanger plates P 1 and P2 are connected at their edge deformations 22.
  • knobs 20 extend into these flow channels 3.
  • the knobs 20 have the same height as the edge features 23 and are otherwise arranged such that they touch the knobs 20 on the adjacent heat exchanger plate P1 or P2 in order to also be connected to become.
  • 8 shows another embodiment in which the edge 21 of the heat exchanger plates P1 and P2 has simply been folded over the entire length L, so that the heat exchanger plates P1 and P2 can be placed one inside the other in a box-like manner to form the flow channels 2.
  • the length of the rods 24 corresponds to the length l, so that the flow channels 3 can be formed in this way.
  • FIG. 9 A further exemplary embodiment is shown in FIG. 9, which makes it clear that all possible variants can be implemented with regard to the flow through the heat exchanger, the basic principle proposed not being abandoned.
  • the inlet 14 and the outlet 15 are arranged on this collecting space 7, so that the exhaust gas flows, for example, via two flow channels 3 into the deflection collecting space 18 arranged on the opposite side and after the deflection the other two flow channels 3 can return to the outlet 15.

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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)
  • Separation By Low-Temperature Treatments (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Abstract

The flow channels (2) of the heat exchanger are longer than the flow channels (3) and extend through the collection chamber (4) having inlets and outlets (8, 9). In region (l), in which both flow channels run parallel to each other, the heat exchanger does not have a housing. Heat exchanger , especially waste gas heat exchanger, consists of a stack of heat exchange plates forming divided flow channels running parallel to each other, with collection chambers, and inlet and outlet for the waste gas and for liquid coolant. The flow channels (2) of the heat exchanger are longer than the flow channels (3) and extend through the collection chamber (4) having inlets and outlets (8, 9). In region (l), in which both flow channels run parallel to each other, the heat exchanger does not have a housing.

Description

Die Erfindung betrifft einen Wärmetauscher, insbesondere Abgaswärmetauscher, bestehend aus einem Stapel von Wärmetauscherplatten, die getrennte Strömungs kanäle ausbilden, die parallel zueinander verlaufen, mit Sammelräumen, Einlaß und Auslaß für das Abgas sowie für das vorzugsweise flüssige Kühlmittel.The invention relates to a heat exchanger, in particular an exhaust gas heat exchanger, consisting of a stack of heat exchanger plates that separate flow form channels that run parallel to each other, with collecting spaces, inlet and outlet for the exhaust gas and for the preferably liquid coolant.

Wie das deutsche Gebrauchsmuster Nr. 83 19 866 nur exemplarisch zeigt, hat man zu Beginn der 80-er Jahre Abgaswärmetauscher häufig als sogenannte Röhrenbündelwärmetauscher konzipiert, die aus einem Bündel von Rundrohren bestehen, das beidendig in Rohrböden mündet. Die Ein - und Auslässe für das Abgas befinden sich an gegenüberliegenden Enden. Dort sind auch Sammelräume ausgebildet, von denen aus sich das Abgas auf die einzelnen Rohre des Bündels verteilt und dieses durchströmt. Die Ein-und Auslässe sind in relativer Nähe zu den anderen Ein-und Auslässen so angeordnet, daß sich die Strömungsrichtungen der beiden Medien in diesem Bereich kreuzen.
Von solchen Röhrenwärmetauschern, als Abgaswärmetauscher, hat man sich später wieder entfernt, weil sie leistungsmäßig unbefriedigend und zu großbauend sind. Letzteres vor allem wegen des erforderlichen äußeren Gehäuses - meist in Zylinderform - welches das Bündel einschließt und die Strömungskanäle für das Kühlmittel außen begrenzt. Insbesondere für Kraftfahrzeuge benötigt man Abgaswärmetauscher, die sehr platzsparend sein müssen, bei gleichzeitig hohen Leistungsparametern. Runde Querschnittsformen haben einen niedrigeren RaumAs the German utility model No. 83 19 866 only shows by way of example, at the beginning of the 1980s, exhaust gas heat exchangers were often designed as so-called tube bundle heat exchangers, which consist of a bundle of round tubes that end at both ends in tube sheets. The exhaust gas inlets and outlets are on opposite ends. Collection rooms are also formed there, from which the exhaust gas is distributed to the individual tubes of the bundle and flows through it. The inlets and outlets are arranged in relative proximity to the other inlets and outlets so that the flow directions of the two media intersect in this area.
Such tube heat exchangers, as exhaust gas heat exchangers, were later removed because their performance is unsatisfactory and too large. The latter mainly because of the required outer housing - usually in the form of a cylinder - which encloses the bundle and limits the flow channels for the coolant on the outside. Exhaust gas heat exchangers, which have to be very space-saving and at the same time have high performance parameters, are required in particular for motor vehicles. Round cross-sectional shapes have a lower space

nutzungsgrad. Deshalb und auch aus Kostengründen, ist man später dazu übergegangen, sogenannte gehäuselose Plattenwärmetauscher als Abgaswärmetauscher vorzusehen, wie es z.B. in dem deutschen Gebrauchsmuster Nr. 296 16 354, das von der Anmelderin stammt, gezeigt ist.
Das EP 677 715 A1 stellt den Stand der Technik dar, von dem der Oberbegriff abgeleitet worden ist. Der dortige Abgaswärmetauscher ist vorteilhaft, weil das Abgas ohne wesentliche Umlenkungen, die Druckverluste verursachen, den Wärmetauscher durchströmen kann. Allerdings ist für den Fall, daß das Abgas mit Wasser gekühlt wird, der Stapel der Wärmetauscherplatten von einem Gehäuse umschlossen, was zu den schon erwähnten Nachteilen führt. Ferner ist die Flexibilität des Wärmetauschers bezüglich verschiedener Anschlußlagen, insbesondere für die Kühlmittelanschlüsse, verbesserungsbedürftig. Das Plattenpaket ist nach der sogenannten Stab-Platten-Bauweise ausgeführt, wodurch viele einzelne Bauteile vorhanden sind, die zusammengefügt werden müssen. Das kann als aufwendig angesehen werden.
Die Aufgabe der Erfindung besteht darin, einen kompakten und effizienten Wärmetauscher vorzuschlagen, der kostengünstig herzustellen ist und eine bessere Flexibilität bezüglich des Einbauraumes und der Anschlußlagen aufweisen soll. Die erfindungsgemäße Lösung ergibt sich aus den Patentansprüchen.
Das Vorsehen eines oder zweier gegenüberliegender Sammelräume für das eine Medium, vorzugsweise für das Kühlwasser, die von den Strömungskanälen für das andere Medium, also dem Abgas, durchdrungen sind, führt zu sehr flexiblen Anschlußmöglichkeiten für die Ein-und/oder Austrittsstutzen, denn diese können sich an beliebigen Stellen am gesamten Umfang des Sammelraumes befinden, ohne daß dadurch wesentlicher Aufwand erforderlich ist. Wenn eine bessere Flexibilität der Anschlußlage auf der Abgasseite gewünscht wird, liegt es selbstverständlich im Rahmen der Erfindung, die Kühlmittelseite mit der Abgasseite zu vertauschen und die Strömungskanäle entsprechend anzupassen. Das Hindurchgehen der Strömungskanäle des einen Mittels durch den Sammelraum des anderen Mittels führt zu dem Nebeneffekt, daß in dem Sammelraum selbst bereits ein Wärmeaustausch stattfindet, der zur hohen Effizienz des Gesamtwärmeaustausches beiträgt.
Damit konnte den Forderungen der Automobilindustrie und der anderen Anwender in bester Weise entsprochen werden.
Das trifft auch auf die kompakte, raumsparende Gestalt des Wärmetauschers zu, die durch die gehäuselose Bauweise im überwiegenden Bereich des Wärmetauschers, nämlich dort wo die Strömungskanäle parallel zueinander verlaufen, erzielt worden ist. Der erfindungsgemäße Wärmetauscher hat Strömungskanäle unterschiedlicher Länge. Der zuvor erwähnte Bereich entspricht etwa der Länge der kürzeren Strömungskanäle.
In den Strömungskanälen für das Abgas sind Lamellen eingelegt, die Rechtecklamellen sein können, oder auch eine andere als rechteckige Ausbildung haben können. Rechtecklamellen sorgen einerseits für guten Wärmeübergang, ohne andererseits dem Abgas Möglichkeiten zu bieten, sich abzulagern und im Laufe der Zeit die Strömungskanäle zu verschließen.
Auf der Kühlmittelseite weisen die Wärmetauscherplatten Noppen auf. Die Noppen der einen Wärmetauscherplatte berühren die Noppen der nächsten Wärmetauscherplatte, so daß sie miteinander verbunden werden können und zur Kompaktheit des Wärmetauschers beitragen. Es versteht sich jedoch, daß anstelle dieser Noppen ebenfalls Lamellen oder andere turbulenzerzeugende Elemente vorgesehen werden können. Beide Strömungskanäle werden durch Zusammenfügen von Wärmetauscherplatten ausgebildet, die alle die gleiche Form aufweisen, was fertigungstechnisch sehr vorteilhaft ist und zur Kostensenkung beiträgt. Auch die unterschiedliche Länge der Strömungskanäle ist durch diese eine Art Wärmetauscherplatten realisiert worden. Die Wärmetauscherplatten besitzen Ränder, die über die Gesamtlänge der Platten, zu einer Seite umgeformt sind, beispielsweise bezüglich der Plattenebene nach unten, (Rückseite) und die über die Länge der kürzeren Strömungskanäle eine Randausprägung aufweisen, die entgegengesetzt zur Umformung, also nach oberhalb der Plattenebene (Frontseite) ausgebildet ist. Eine vorteilhafte Ausführungsform hat auf der gleichen Plattenseite (Frontseite) auch die bereits erwähnten Noppen. Jeweils zwei Wärmetauscherplatten werden mit ihren über die Gesamtlänge reichenden Rändern, also mit der Rückseite, aneinandergelegt und bilden dazwischen den einen Strömungskanal aus. Der andere Strömungskanal wird dadurch realisiert, daß die nächste Wärmetauscherplatte Frontseite auf Frontseite aufgelegt wird, worauf dann wieder Rückseite auf Rückseite folgt usw.. Die erfinderische Idee mit kürzeren und längeren Strömungskanälen kann selbstverständlich auch - anders als vorstehend geschildert - dadurch realisiert werden, daß anstelle der Randumformungen und Randausprägungen Stäbe eingelegt werden, die die Länge der kürzeren Strömungskanäle aufweisen und die mit den Platten verbunden sind. In diesem Fall sind die Platten vorzugsweise an den gegenüberliegeden Längsrändern nur umgekantet. Zwei solche Platten werden dann schachtelartig zusammengelegt und bilden innerhalb einen Strömungskanal aus. Der angrenzende Strömungskanal wird durch die genannten Stäbe gebildet bzw. an den Längsseiten begrenzt. efficiency. For this reason and also for reasons of cost, it was later adopted to provide so-called plate heat exchangers without a housing as exhaust gas heat exchangers, as is shown, for example, in German Utility Model No. 296 16 354, which comes from the applicant.
EP 677 715 A1 represents the prior art from which the preamble has been derived. The exhaust gas heat exchanger there is advantageous because the exhaust gas can flow through the heat exchanger without significant deflections which cause pressure losses. However, in the event that the exhaust gas is cooled with water, the stack of heat exchanger plates is enclosed in a housing, which leads to the disadvantages already mentioned. Furthermore, the flexibility of the heat exchanger with regard to various connection positions, in particular for the coolant connections, is in need of improvement. The plate package is designed according to the so-called rod-plate construction, which means that there are many individual components that have to be joined together. This can be seen as expensive.
The object of the invention is to propose a compact and efficient heat exchanger which is inexpensive to manufacture and which should have better flexibility with regard to the installation space and the connection positions. The solution according to the invention results from the patent claims.
The provision of one or two opposite collecting spaces for one medium, preferably for the cooling water, which are penetrated by the flow channels for the other medium, that is to say the exhaust gas, leads to very flexible connection options for the inlet and / or outlet connections, since these can are located anywhere along the entire circumference of the collecting space, without any significant effort being required. If a better flexibility of the connection position on the exhaust side is desired, it is of course within the scope of the invention to interchange the coolant side with the exhaust side and to adapt the flow channels accordingly. The passage of the flow channels of one agent through the collecting space of the other means leads to the side effect that a heat exchange is already taking place in the collecting space itself, which contributes to the high efficiency of the overall heat exchange.
This was the best way to meet the demands of the automotive industry and other users.
This also applies to the compact, space-saving design of the heat exchanger, which has been achieved by the housingless design in the predominant area of the heat exchanger, namely where the flow channels run parallel to one another. The heat exchanger according to the invention has flow channels of different lengths. The area mentioned above corresponds approximately to the length of the shorter flow channels.
In the flow channels for the exhaust gas, lamellae are inserted, which can be rectangular lamellae or can also have a shape other than rectangular. Rectangular fins on the one hand ensure good heat transfer without, on the other hand, offering the exhaust gas possibilities to deposit and over time to close off the flow channels.
The heat exchanger plates have knobs on the coolant side. The knobs of one heat exchanger plate touch the knobs of the next heat exchanger plate, so that they can be connected to each other and contribute to the compactness of the heat exchanger. However, it goes without saying that lamellae or other turbulence-generating elements can also be provided instead of these knobs. Both flow channels are formed by joining heat exchanger plates, all of which have the same shape, which is very advantageous in terms of production technology and helps to reduce costs. The different length of the flow channels has also been realized by this type of heat exchanger plate. The heat exchanger plates have edges that are formed on one side over the entire length of the plates, for example downwards with respect to the plate level, and that have an edge configuration over the length of the shorter flow channels, which is opposite to the deformation, i.e. above the plate level (Front) is formed. An advantageous embodiment also has the knobs already mentioned on the same plate side (front side). Two heat exchanger plates are placed together with their edges that extend over the entire length, i.e. with the rear, and form the one flow channel between them. The other flow channel is realized by placing the next heat exchanger plate on the front side on the front side, which is then followed by the back side on the back side, etc. The inventive idea with shorter and longer flow channels can of course also be realized - in contrast to the above - by instead of the edge reshaping and edge embossing rods are inserted, which have the length of the shorter flow channels and which are connected to the plates. In this case, the plates are preferably only folded over at the opposite longitudinal edges. Two such plates are then put together like a box and form within a flow channel. The adjacent flow channel is formed by the rods mentioned or delimited on the long sides.

Nach dem vorgeschlagenen erfinderischen Prinzip kann der Wärmetauscher sowohl mit gegenüberliegenden Sammelräumen für das Abgas und/oder für das Kühlmittel und Durchströmung auf einem geraden Weg angewendet werden, als auch bei Wärmetauschern, die nur an einer Seite einen Sammelraum für das Abgas und/oder für das Kühlmittel haben und am gegenüberliegenden Ende einen Umlenkraum aufweisen. Dabei ist, wie an sich bekannt, in dem einen Sammelraum eine Trennplatte angeordnet. Die Nutzung dieser Varianten verbessert die Flexibilität der Anschlußlagen auf der Abgasseite und auf der Kühlmittelseite. Vorzugsweise sind die äußeren Strömungskanäle für das Kühlmittel gedacht, weil dadurch die Strahlungswärme des Wärmetauschers geringer gehalten werden kann. Das ist bei Abgastemperaturen von 700°C und mehr nicht unwesentlich und trägt zur Reduzierung der Motorenerwärmung bei, inbesondere bei Motoren in Kapselbauweise. Bei dieser Variante befindet sich je eine Abschlußplatte auf und unter dem Stapel der Wärmetauscherplatten, die den Kühlmittelkanal nach außen begrenzen. Dadurch entsteht darüber hinaus der Vorteil, daß die Verbindung des Stapels der Wärmetauscherplatten mit dem einen Rohrboden einfacher ausgeführt werden kann, weil die Öffnung im Rohrboden als Viereck ausgebildet ist. Weitere unter Umständen wichtige Merkmale, die sich auch als erfindungswesentlich herausstellen könnten, gehen aus der nachfolgenden Beschreibung von Ausführungsbeispielen hervor. Dazu wird Bezug auf die beiliegenden Zeichnungen genommen, die folgendes zeigen:

  • Fig. 1 Seitenansicht einer ersten Ausführungsform
  • Fig. 2 Draufsicht von Fig. 1
  • Fig. 3 Ansicht aus Richtung des Pfeiles III in Fig. 1
  • Fig. 4 Ähnlich Fig. 3, aber ohne Abgaseinlaß gezeichnet
  • Fig. 5 Längsschnitt durch einen Sammelraum
  • Fig. 6 Schnitt A in Fig. 5, vergrößert
  • Fig. 7 Ansicht auf einen Rohrboden
  • Fig. 8 Ähnlich Ansicht A in Fig. 5 - andere Ausführungsform
  • Fig. 9 Seitenansicht einer weiteren Ausführungsform
  • Fig. 10 Draufsicht auf eine Wärmetauscherplatte
  • Fig. 11 Ansicht nach Pfeil XI in Fig. 10
  • Fig. 12 Vergrößerter Ausschnitt des Randes der Platte nach Pfeil XII in Fig. 10
    • According to the proposed inventive principle, the heat exchanger can be used both with opposite collection spaces for the exhaust gas and / or for the coolant and flow in a straight path, as well as with heat exchangers that have a collection space for the exhaust gas and / or for only on one side Have coolant and have a deflection space at the opposite end. As is known per se, a separating plate is arranged in the collecting space. The use of these variants improves the flexibility of the connection positions on the exhaust side and on the coolant side. The outer flow channels are preferably intended for the coolant because the radiant heat of the heat exchanger can thereby be kept lower. This is not insignificant at exhaust gas temperatures of 700 ° C and more and contributes to the reduction of engine heating, especially in engines with a capsule design. In this variant, there is an end plate on and below the stack of heat exchanger plates that limit the coolant channel to the outside. This also has the advantage that the connection of the stack of heat exchanger plates with the one tube sheet can be carried out more simply because the opening in the tube sheet is designed as a square. Other possibly important features, which could also prove to be essential to the invention, appear from the following description of exemplary embodiments. Reference is made to the accompanying drawings, which show the following:
  • Fig. 1 side view of a first embodiment
  • 2 top view of FIG. 1st
  • 3 view from the direction of arrow III in Fig. 1st
  • Fig. 4 Similar to Fig. 3, but drawn without an exhaust gas inlet
  • Fig. 5 longitudinal section through a collecting space
  • Fig. 6 section A in Fig. 5, enlarged
  • Fig. 7 view of a tube sheet
  • Fig. 8 Similar to view A in Fig. 5 - different embodiment
  • Fig. 9 side view of another embodiment
  • Fig. 10 plan view of a heat exchanger plate
  • 11 view according to arrow XI in FIG. 10
  • 12 enlarged section of the edge of the plate according to arrow XII in FIG. 10

    • Der wassergekühlte Abgaswärmetauscher 1 ist in den Fig. 1 bis 6 in einem ersten Ausführungsbeispiel dargestellt.
    Der Abgaswärmetauscher besteht komplett aus einem geeigneten Edelstahl. Sämtliche Verbindungen zwischen den Teilen werden mittels Löten hergestellt. In der Fig. 1 wurde der linke Sammelraum 4 für das Kühlwasser und der Sammelraum 7 für das Abgas im Schnitt gezeichnet, um Einzelheiten zu zeigen. Das Abgas strömt durch den Einlaß 14 in den Sammelraum 7 und über die Strömungskanäle 2 auf geradem Weg durch den Wärmetauscher 1, um diesen über den Auslaß 15 wieder zu verlassen. Die Ein-und Auslässe 14, 15 besitzen geeignete Anschlüsse, die hier einfach als Anschlußflansche dargestellt worden sind. Das Kühlwasser strömt am Einlaß 8 in den Sammelraum 4 und verteilt sich auf die Strömungskanäle 3, die parallel mit den Strömungskanälen 2 verlaufen und sich mit diesen abwechseln. Die Sammelräume 4 sind aus den Rohrböden 5 und 6 gebildet worden, wobei der Mantel 5 der Sammelräume 4 durch den aufgerichteten Rand 12 des Rohrbodens 5, der mit dem Rand des Rohrbodens 6 eine Verbindungsfläche 13 bildet, in diesem Ausführungsbeispiel hergestellt worden ist. Der aus identischen Wärmetauscherplatten P1 und P2 bestehende Stapel weist kürzere Strömungskanäle 3 auf und längere Strömungskanäle 2, was weiter unten genauer erläutert ist. Die unterschiedliche Länge L und I der Strömungskanäle 2 und 3 wurde in Fig. 1 eingezeichnet. Die längeren Strömungskanäle 2 gehen durch die Sammelräume 4 hindurch und sind in den Öffnungen 17 des zweiten Rohrbodens 6 abdichtend befestigt. ( siehe auch Fig. 4, in der drei Öffnungen 17 für die drei Strömungskanäle 2 gezeigt sind)
    Die Fig. 4 und auch die Fig. 3 zeigen ferner, daß in den Strömungskanälen 2 Rechtecklamellen 25 eingelegt worden sind, um den Wärmeaustausch zu verbessern. Die Lamellen 25 sind mit den Wärmetauscherplatten P1 und P2 bzw. mit den Wandungen der Strömungskanäle 2 verbunden.
    Der Rohrboden 5 hat bloß eine Öffnung 16, wie die Fig. 7 zeigt. Die Öffnung 16 ist ein Rechteck. Die Fig. 6 zeigt in einem vergrößerten Schnitt die Befestigung der Wärmetauscherplatten P1 und P2 in dieser Öffnung 16. Am oberen Rand der Öffnung 16 ist eine Abschlußplatte 11 eingezeichnet worden. Eine identische Platte 11 befindet sich am nicht gezeichneten unteren Rand der Öffnung 16. Die Abschlußplatten 11 decken die Wärmetauscherplatten P1; P2 vollständig ab (Fig. 2) und begrenzen den oberen und unteren Strömungskanal 3, der für Kühlwasser vorgesehen ist. In diesem Ausführungsbeispiel wurden identische Wärmetauscherplatten P1 und P2 verwendet, die in den Fig. 10 bis 12 dargestellt worden sind. Die Wärmetauscherplatten P1; P2 sind hier rechteckförmig und haben demzufolge zwei gegenüberliegende Längsränder 21. An diesen Längsrändern 21 befindet sich eine über die gesamte Plattenlänge L reichende Umformung 22, die zur Rückseite R der Plattenebene gerichtet ist. Zur Frontseite F gerichtet, weisen die Wärmetauscherplatten P1 und P2 an den beiden Längsrändern 21 eine Randausprägung 23 auf, die sich nur über die Länge l der Wärmetauscherplatten P1 und P2 erstreckt. Im Zusammenhang mit der Fig. 6 ist zu erkennen, daß jeweils zwei Wärmetauscherplatten P1 und P2 mit ihren Rückseiten R aneinandergelegt sind und innerhalb den Strömungskanal 2 ausbilden, der über die Gesamtlänge L geht. Die Wärmetauscherplatten P 1 und P2 sind an ihren Randumformungen 22 verbunden. An der Frontseite F der Wämetauscherplatte P1 oder P 2 befindet sich die nächste Wärmetauscherplatte P1 oder P2, die ebenfalls mit der Frontseite F dazu angeordnet worden ist, wobei die Wärmetauscherplatten P1; P2 mit ihren Randausprägungen 23 verbunden sind und die Strömungskanäle 3 ausbilden. In diese Strömungakanäle 3 hinein erstrecken sich in diesem Ausführungsbeispiel Noppen 20. Die Noppen 20 haben die gleiche Höhe wie die Randausprägungen 23 und sind im übrigen so angeordnet, daß sie sich mit den Noppen 20 an der benachbarten Wärmetauscherplatte P1 oder P2 berühren, um ebenfalls verbunden zu werden.
    Die Fig. 8 zeigt ein anderes Ausführungsbeispiel, bei dem der Rand 21 der Wärmetauscherplatten P1 und P2 über die Gesamtlänge L einfach abgekantet worden ist, so daß die Wärmetauscherplatten P1 und P2 schachtelartig ineinandergelegt werden können, zur Bildung der Strömungskanäle 2. Zwischen diesen Strömungskanälen 2 liegt an beiden Rändern 21 je ein Stab 24, der die doppelte Höhe der Noppen 20 aufweist. Die Länge der Stäbe 24 entspricht der Länge l, so daß auf diese Weise die Strömungskanäle 3 ausgebildet werden können.
    Eine weiteres Ausführungabeispiel zeigt die Fig. 9, die deutlich macht, daß hinsichtlich der Durchströmung des Wärmetauschers alle möglichen Varianten realisierbar sind, wobei das vorgeschlagene Grundprinzip nicht verlassen wird. Im Sammelraum für das Abgas 7 befindet sich eine Trennwand 19. Der Einlaß 14 und der Auslaß 15 sind an diesem Sammelraum 7 angeordnet, so daß das Abgas beispielsweise über zwei Strömungskanäle 3 in den auf der gegenüberliegenden Seite angeordneten Umlenksammelraum 18 strömen und nach der Umlenkung über die anderen beiden Strömungskanäle 3 wieder zurück zum Auslaß 15 gelangen kann.
    Ohne besondere Darstellung sei darauf hingewiesen, daß selbstverständlich auch auf der Kühlwasserseite solche Varianten ganz einfach möglich sind, beispielsweise dadurch, daß der Kühlwasserauslaß 9 an den im Bild unteren Sammelraum 4 angeordnet wird, eine Trennplatte im Sammelraum 4 eingesetzt und am gegenüberliegenden Ende ein vergleichbarer Umlenksammelraum für das Kühlwasser vorgesehen wird.
    Eine weitere nicht gezeigte Ausführungsform hat den Einlaß und den Auslaß für das Kühlmittel auf einer Seite des Wärmetauschers sowie den Einlaß und den Auslaß für das Abgas auf der gegenüberliegenden Seite des Wärmetauschers.     The water-cooled exhaust gas heat exchanger 1 is shown in FIGS. 1 to 6 in a first embodiment.
    The exhaust gas heat exchanger consists entirely of a suitable stainless steel. All connections between the parts are made by soldering. In Fig. 1, the left collecting space 4 for the cooling water and the collecting space 7 for the exhaust gas was drawn in section to show details. The exhaust gas flows through the inlet 14 into the collecting space 7 and via the flow channels 2 in a straight path through the heat exchanger 1 in order to leave it again via the outlet 15. The inlets and outlets 14, 15 have suitable connections, which have been shown here simply as connecting flanges. The cooling water flows at the inlet 8 into the collecting space 4 and is distributed over the flow channels 3, which run parallel to the flow channels 2 and alternate with them. The collecting spaces 4 have been formed from the tube sheets 5 and 6, the jacket 5 of the collecting spaces 4 being produced in this exemplary embodiment by the erected edge 12 of the tube sheet 5, which forms a connecting surface 13 with the edge of the tube sheet 6. The stack consisting of identical heat exchanger plates P1 and P2 has shorter flow channels 3 and longer flow channels 2, which is explained in more detail below. The different lengths L and I of the flow channels 2 and 3 were shown in FIG. 1. The longer flow channels 2 pass through the collecting spaces 4 and are sealingly fastened in the openings 17 of the second tube sheet 6. (see also FIG. 4, in which three openings 17 for the three flow channels 2 are shown)
    FIG. 4 and also FIG. 3 further show that 2 rectangular lamellae 25 have been inserted in the flow channels in order to improve the heat exchange. The fins 25 are connected to the heat exchanger plates P1 and P2 or to the walls of the flow channels 2.
    The tube sheet 5 merely has an opening 16, as shown in FIG. 7. The opening 16 is a rectangle. 6 shows, in an enlarged section, the fastening of the heat exchanger plates P1 and P2 in this opening 16. At the upper edge of the opening 16, an end plate 11 has been drawn. An identical plate 11 is located at the lower edge of the opening 16, not shown. The end plates 11 cover the heat exchanger plates P1; P2 completely (Fig. 2) and limit the upper and lower flow channel 3, which is intended for cooling water. In this embodiment, identical heat exchanger plates P1 and P2 were used, which have been shown in FIGS. 10 to 12. The heat exchanger plates P1; P2 are rectangular here and consequently have two opposite longitudinal edges 21. On these longitudinal edges 21 there is a deformation 22 which extends over the entire plate length L and is directed towards the rear side R of the plate plane. Directed to the front F, the heat exchanger plates P1 and P2 have on the two longitudinal edges 21 an edge configuration 23 which extends only over the length l of the heat exchanger plates P1 and P2. In connection with FIG. 6 it can be seen that two heat exchanger plates P1 and P2 are placed against one another with their rear sides R and form within the flow channel 2, which extends over the total length L. The heat exchanger plates P 1 and P2 are connected at their edge deformations 22. On the front F of the heat exchanger plate P1 or P 2 there is the next heat exchanger plate P1 or P2, which has also been arranged with the front F, with the heat exchanger plates P1; P2 are connected to their edge features 23 and form the flow channels 3. In this exemplary embodiment, knobs 20 extend into these flow channels 3. The knobs 20 have the same height as the edge features 23 and are otherwise arranged such that they touch the knobs 20 on the adjacent heat exchanger plate P1 or P2 in order to also be connected to become.
    8 shows another embodiment in which the edge 21 of the heat exchanger plates P1 and P2 has simply been folded over the entire length L, so that the heat exchanger plates P1 and P2 can be placed one inside the other in a box-like manner to form the flow channels 2. Between these flow channels 2 is on both edges 21 a rod 24, which has twice the height of the knobs 20. The length of the rods 24 corresponds to the length l, so that the flow channels 3 can be formed in this way.
    A further exemplary embodiment is shown in FIG. 9, which makes it clear that all possible variants can be implemented with regard to the flow through the heat exchanger, the basic principle proposed not being abandoned. In the collecting space for the exhaust gas 7 there is a partition 19. The inlet 14 and the outlet 15 are arranged on this collecting space 7, so that the exhaust gas flows, for example, via two flow channels 3 into the deflection collecting space 18 arranged on the opposite side and after the deflection the other two flow channels 3 can return to the outlet 15.
    Without a special illustration, it should be noted that such variants are of course also very easily possible on the cooling water side, for example by arranging the cooling water outlet 9 on the lower collecting chamber 4 in the picture, inserting a separating plate in the collecting chamber 4 and a comparable deflecting collecting chamber at the opposite end is provided for the cooling water.
    Another embodiment, not shown, has the inlet and outlet for the coolant on one side of the heat exchanger and the inlet and outlet for the exhaust gas on the opposite side of the heat exchanger.

    Liste der BezugszeichenList of reference numbers

    11
    AbgaswärmetauscherExhaust gas heat exchanger
    22nd
    längere Strömungskanälelonger flow channels
    33rd
    kürzere Strömungskanäleshorter flow channels
    44th
    Sammelraum, KühlwasserStorage room, cooling water
    55
    erster Rohrbodenfirst tube sheet
    66
    zweiter Rohrbodensecond tube sheet
    77
    Sammelraum, AbgasCollection room, exhaust gas
    88th
    Einlaß, KühlwasserInlet, cooling water
    99
    Auslaß, KühlwasserOutlet, cooling water
    1010th
    Mantel, Sammelraum 4Coat, collecting room 4
    1111
    AbschlußplatteEnd plate
    1212th
    Bord am Rohrboden 5Board on tube sheet 5
    1313
    VerbindungsflächeInterface
    1414
    Einlaß, AbgasIntake, exhaust gas
    1515
    Auslaß, AbgasExhaust, exhaust
    1616
    Öffnung, Rohrboden 5Opening, tube sheet 5
    1717th
    Öffnungen, Rohrboden 6Openings, tube sheet 6
    1818th
    Umlenkraum, AbgasDeflection chamber, exhaust gas
    1919th
    TrennplattePartition plate
    2020th
    NoppenPimples
    2121
    Rand der WärmetauscherplattenEdge of the heat exchanger plates
    2222
    Umformung am RandForming on the edge
    2323
    RandausprägungEdge design
    2424th
    StäbeRods
    2525th
    LamellenSlats
    P1;P2P1; P2
    WärmetauscherplattenHeat exchanger plates
    R;FR; F
    Rückseite, Frontseite der PlattenBack, front of the panels
    LL
    Länge der langen StrömungskanäleLength of the long flow channels
    ll
    Länge der kurzen Strömungskanäle, = Bereich in dem beide Kanäle parallel laufenLength of the short flow channels, = area in which both channels run in parallel

    Claims (12)

    Wärmetauscher, insbesondere Abgaswärmetauscher, bestehend aus einem Stapel von Wärmetauscherplatten, die getrennte Strömungskanäle ausbilden, die parallel zueinander verlaufen, mit Sammelräumen, Einlaß und Auslaß für das Abgas sowie für das vorzugsweise flüssige Kühlmittel,
    dadurch gekennzeichnet, daß
    die aus Wärmetauscherplatten (P1; P2) gebildeten Strömungskanäle (2) für das eine Mittel länger (L) sind, als die Strömungskanäle (3) für das andere Mittel und durch den Ein-und/oder Auslässe (8; 9) aufweisenden wenigstens einen Sammelraum (4) für dieses andere Mittel hindurchgehen und daß in dem Bereich (l), in dem beide Strömungskanäle (2; 3) parallel zueinander verlaufen, der Wärmetauscher (1) ohne Gehäuse ausgeführt ist.    Heat exchangers, in particular exhaust gas heat exchangers, consisting of a stack of heat exchanger plates which form separate flow channels which run parallel to one another, with collecting spaces, inlet and outlet for the exhaust gas and for the preferably liquid coolant,
    characterized in that
    the flow channels (2) formed from heat exchanger plates (P1; P2) for one medium are longer (L) than the flow channels (3) for the other medium and have at least one through the inlets and / or outlets (8; 9) Collect space (4) for this other means and that in the area (l) in which both flow channels (2; 3) run parallel to each other, the heat exchanger (1) is designed without a housing.         Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß der Sammelraum (4) von zwei gegenüberliegenden Rohrböden (5; 6) begrenzt und von einem Mantel (10) umgeben ist, an dem sich die Ein-und/oder Auslässe (8; 9) befinden.Heat exchanger according to claim 1, characterized in that the collecting space (4) bounded by two opposite tube sheets (5; 6) and by one Sheath (10) is surrounded, on which the inlets and / or outlets (8; 9) are located. Wärmetauscher nach Anspruch 2, dadurch gekennzeichnet, daß der Mantel durch den Bord (12) des einen Rohrbodens (5) gebildet ist, der mit dem Bord des anderen Rohrbodens (6) eine Verbindungsfläche (13) ausbildet.Heat exchanger according to claim 2, characterized in that the jacket is formed by the board (12) of a tube sheet (5) which with the board of the another tube sheet (6) forms a connecting surface (13). Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der erste Rohrboden (5) eine Öffnung (16) aufweist, in der der beide Strömungskanäle (2; 3) aufweisende Stapel von Wärmetauscherplatten (P1; P2) mündet und der zweite Rohrboden (6) Öffnungen (17) aufweist, in denen die längeren Strömungskanäle (2) münden.Heat exchanger according to one of the preceding claims, characterized in that that the first tube sheet (5) has an opening (16) in which the two Flow channels (2; 3) having stacks of heat exchanger plates (P1; P2) opens and the second tube sheet (6) has openings (17) in which the longer flow channels (2) open. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Einlaß (14) und der Auslaß (15) für das Abgas und/oder für das Kühlmittel an gegenüberliegenden Enden des Wärmetauschers (1) angeordnet sind. Heat exchanger according to one of the preceding claims, characterized in that that the inlet (14) and the outlet (15) for the exhaust gas and / or for the Coolant arranged at opposite ends of the heat exchanger (1) are. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Einlaß (14) und der Auslaß (15) für das Abgas und/oder für das Kühlmittel an einer Seite des Wärmetauschers (1) angeordnet sind und am gegenüberliegenden Ende ein Umlenksammelraum (16) vorgesehen ist.Heat exchanger according to one of claims 1 to 4, characterized in that the inlet (14) and the outlet (15) for the exhaust gas and / or for the coolant are arranged on one side of the heat exchanger (1) and on the opposite A deflection collecting space (16) is provided at the end. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Wärmetauscherplatten (P1; P2) vorzugsweise an den gegenüberliegenden Längsrändern (21) über die Gesamtlänge der Platten zu einer Plattenseite (Rückseite R) hin umgeformt (22) sind und über einen Teil (l) der Gesamtlänge (L) zur anderen Plattenseite (Frontseite F) hin eine Randausprägung (23) aufweisen.Heat exchanger according to one of the preceding claims, characterized in that that the heat exchanger plates (P1; P2) preferably on the opposite longitudinal edges (21) over the total length of the plates a plate side (rear side R) are formed (22) and over a part (l) the total length (L) towards the other side of the panel (front F) Have edge (23). Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Wärmetauscherplatten (P1; P2) Rückseite (R) an Rückseite (R) liegend die längeren Strömungskanäle (2) ausbilden, an die sich mit Frontseite (F) an Frontseite (F) liegende Wärmetauscherplatten (P1; P2) anschließen, die die kürzeren Strömungskanäle (3) ausformen, auf die wieder Rückseite (R) an Rückseite (R) liegende Wärmetauscherplatten (P1; P2) folgen.Heat exchanger according to one of the preceding claims, characterized in that that the heat exchanger plates (P1; P2) rear (R) to rear (R) Form the longer flow channels (2) horizontally, to which the front (F) Connect the heat exchanger plates (P1; P2) lying on the front (F) Form shorter flow channels (3), on the back (R) on the back (R) Follow lying heat exchanger plates (P1; P2). Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die kürzeren Strömungskanäle (3) vorzugsweise Kühlwasserkanäle sind und die längeren Kanäle (2) für das Abgas gedacht sind.Heat exchanger according to one of the preceding claims, characterized in that that the shorter flow channels (3) preferably cooling water channels are and the longer channels (2) are intended for the exhaust gas. Wärmetauscher nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die äußeren Kanäle (3) Kühlwasserkanäle sind, die durch je eine Abschlußplatte (11) begrenzt sind, wobei der eine Rohrboden (5) eine etwa rechteckförmige Öffnung (16) aufweist um den Stapel der Wärmetauscherplatten (P1; P2) mit beiden Strömungskanälen (2; 3) und die Enden der Abschlußplatten (11) aufzunehmen.Heat exchanger according to one of the preceding claims, characterized in that that the outer channels (3) are cooling water channels, each by one End plate (11) are limited, one of the tube sheets (5) approximately Rectangular opening (16) has around the stack of heat exchanger plates (P1; P2) with both flow channels (2; 3) and the ends of the end plates (11) record. Wärmetauscher nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die äußeren Kanäle (2) Abgaskanäle sind, wobei der eine Rohrboden (5) eine Öffnung besitzt, die in den Ecken Ausschnitte aufweist, für die Randausprägungen (23) der obersten und untersten Wärmetauscherplatte (P1; P2), um den gesamten Stapel der Wärmetauscherplatten (P1; P2) aufzunehmen.Heat exchanger according to one of claims 1 to 9, characterized in that that the outer channels (2) are exhaust channels, the one tube sheet (5) one Has opening, which has cutouts in the corners, for the edges (23) the top and bottom heat exchanger plates (P1; P2) to the entire Pick up stack of heat exchanger plates (P1; P2). Wärmetauscher nach einem der Ansprüche 1 bis 6 und 9 bis 10, dadurch gekennzeichnet, daß die Wärmetauscherplatten (P1; P2) an den Rändern (21) eine über die Gesamtlänge (L) reichende Abkantung aufweisen und zur Bildung der Strömungskanäle (2) schachtelartig ineinandergelegt sind sowie zur Bildung der Strömungskanäle (3), Stäbe (24) zwischen den Plattenpaaren angeordnet sind, deren Länge etwa der Länge (l) der kürzeren Strömungskanäle (3) entspricht.Heat exchanger according to one of claims 1 to 6 and 9 to 10, characterized characterized in that the heat exchanger plates (P1; P2) on the edges (21) have a bevel over the entire length (L) and for formation the flow channels (2) are interlaced like a box and for formation the flow channels (3), rods (24) arranged between the plate pairs are, whose length corresponds approximately to the length (l) of the shorter flow channels (3).
    EP99113222A 1998-07-24 1999-07-08 Heat exchanger, more particularly heat exchanger for exhaust gases Expired - Lifetime EP0974804B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE19833338A DE19833338A1 (en) 1998-07-24 1998-07-24 Heat exchangers, in particular exhaust gas heat exchangers
    DE19833338 1998-07-24

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    Publication Number Publication Date
    EP0974804A2 true EP0974804A2 (en) 2000-01-26
    EP0974804A3 EP0974804A3 (en) 2000-06-07
    EP0974804B1 EP0974804B1 (en) 2002-10-09

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    ID=7875170

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    Country Status (6)

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    US (1) US6293337B1 (en)
    EP (1) EP0974804B1 (en)
    JP (1) JP2000097578A (en)
    AT (1) ATE225926T1 (en)
    DE (2) DE19833338A1 (en)
    ES (1) ES2185276T3 (en)

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    JP2000097578A (en) 2000-04-04
    EP0974804A3 (en) 2000-06-07
    ATE225926T1 (en) 2002-10-15
    ES2185276T3 (en) 2003-04-16
    DE19833338A1 (en) 2000-01-27
    DE59902999D1 (en) 2002-11-14
    EP0974804B1 (en) 2002-10-09
    US6293337B1 (en) 2001-09-25

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