EP1152204B1 - Plate type heat exchanger - Google Patents
Plate type heat exchanger Download PDFInfo
- Publication number
- EP1152204B1 EP1152204B1 EP01107118A EP01107118A EP1152204B1 EP 1152204 B1 EP1152204 B1 EP 1152204B1 EP 01107118 A EP01107118 A EP 01107118A EP 01107118 A EP01107118 A EP 01107118A EP 1152204 B1 EP1152204 B1 EP 1152204B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- plate
- ducts
- guide
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
Definitions
- the invention relates to a plate heat exchanger described in the preamble of claim 1 Art.
- a plate heat exchanger is known, for example, from EP 819 907 B1.
- nubs or similar protrusions have been embossed in the heat exchanger plates forming the horizontal channels for the heating or cooling medium.
- the nubs of adjacent heat exchanger plates touch and are soldered together to increase the strength of the plate heat exchanger.
- Such knobs have generally proven themselves and are therefore very often provided because they cause practically no noticeable pressure loss.
- a plate heat exchanger corresponding to the preamble is disclosed in US Pat. No. 4,653,581.
- the inner insert is formed over its entire surface like a corrugated rib.
- the corrugated fin does not offer the desired high pressure stability, because the connecting surfaces between the corrugated fin and the heat exchanger plates are too small.
- an improved durability is achieved, but only between the mentioned plates and the adjacent heat exchanger plates.
- a similar problem situation can be found in DE 197 11 258 A1, in which a reinforcing plate with a board was inserted between the base plate and the lowermost heat exchanger plate.
- the stresses also acting inside the plate heat exchanger can not be met with the teachings of these two publications.
- corresponding inner inserts laamellae
- the object of the invention is to improve the durability of the plate heat exchanger inside without substantially increasing the pressure loss of the medium flowing through the channels.
- the inner insert is an additional plate having guide channels with at least one inlet and one outlet leading from one flow channel of one medium to the other flow channel of the same medium, to which most of the guide channels have a curvature, the Guide channels free portions of the additional plate with the one adjacent heat exchanger plate and the guide channels are metallically connected to the other adjacent heat exchanger plate of the same channel.
- the plate heat exchanger according to the invention leads to the following advantages.
- the provided with at least one inlet and an outlet guide channels and the alignment of the plurality of guide channels from one flow channel to the other cause a very low pressure drop, the height, depending on the operating conditions, is quite comparable, with the nubs described in the prior art.
- the durability against thermal shocks and extreme thermal cycling and mechanical stresses has been significantly improved because the additional plate on both sides, that is, with both heat exchanger plates, is connected.
- the bonding surfaces are much larger than in the prior art, which is crucial for durability, such as solder joints.
- the plurality of guide channels should be directed from a flow channel of one medium to the other flow channel of the same medium. This means that the general orientation of the majority of the guide channels from one flow channel to the other flow channel should be carried out as described, wherein the guide channels, in particular in rectangular plate heat exchangers with arranged in the corners flow channels, may well be arcuate, so not straight from one to another Flow channel must run.
- the additional plates of the plate heat exchanger according to the invention can be located in all its channels.
- the additional plate has four openings which coincide in position with the flow channels forming openings in the heat exchanger plates.
- the two channels connected in the auxiliary plate by means of the guide channels are larger than the corresponding openings in the heat exchanger plates and provided with a shape adapted to the arrangement of the guide channels. It has been determined by extensive experiments that this measure has a significant part in that the pressure loss could be further reduced.
- the shape of the mentioned openings and the arrangement of the guide channels should be adapted to each other. In a preferred embodiment, these openings have a different shape from the circular shape. In particular, the openings are provided with bulges in the direction of the inlets or outlets of selected guide channels.
- the other two openings in the auxiliary plate which are intended for another medium and which are not connected by means of guide channels, may be identical in shape to the openings in the heat exchanger plates.
- branches In particular in the vicinity of the branches, fluidic advantages, for example a more uniform distribution of the flow or the heat exchange, are achieved in that additional inlet and outlet openings are arranged in the guide channels.
- the branches may be located between the edge of the heat exchanger plate and the flow channels.
- the corner portions of the heat exchanger are intensively involved in heat exchange in substantially rectangular heat exchanger plates, whereby the performance thereof is improved.
- Investigations by the applicant show a very homogeneous distribution of heat exchange over all areas of the heat exchanger plates and the additional plates.
- Claim 8 describes an advantageous arrangement of the guide channels, which consists in that some Guiding channels formed continuously from one flow channel to the other flow channel and other guide channels are much shorter, with their exit and entry away from the flow channels is arranged.
- Claim 9 represents an advantageous additional measure and stipulates that the additional plate nubs or the like should have projections which have the same height as the guide channels and which are connected to the adjacent heat exchanger plate.
- the pimples are near the Flow channels or not so closely occupied with guide channels surfaces of the additional plate arranged and therefore additionally support these areas.
- the additional plate according to the invention can be much thinner than the heat exchanger plates and thus be carried out material - and weight saving.
- the thickness of the Heat exchanger plates 0, 5 mm and the additional plates only 0, 3 mm.
- the non-deformed area in the additional plate 6 around the openings 33 and 35 was reinforced by the knobs 14 .
- the design of the guide channels 8 can be seen, which are formed like a sickle.
- the guide channels 8 are connected to the one heat exchanger plate 2 of the channel 5 , while the interposed portions 11 are metallically connected to the other heat exchanger plate 2 .
- the bent edge 13 of the heat exchanger plates 2 has not been drawn. However, this is clearly visible in Figures 4 and 5 described below. In Fig. 4 , the edge 13 of the heat exchanger plates 2, seen in the installed position of the plate heat exchanger 1 , directed upward and in Fig. 5 down.
- Fig. 4 shows a cross section through the plate heat exchanger 1 with a total of four separate circuits.
- the flow channel 4 for the cooling or heating medium K is located in Fig. 4 on the left side.
- the flow channel 4 for oil 1, oil 2 and oil 3 can be seen.
- the flow channels 4 have connecting flanges 3.
- the connecting flange 3 for oil 1 has a connecting channel, not shown, so that the oil 1 enter through this connecting channel and in the upper channels 5 with the coolant K in the heat exchange. All channels 5 for oil 1; Oil 2 and oil 3 have conventional fins 53.
- the oil 2 also enters the flange 3 in the plate heat exchanger 1 through the pipe section 50 with a flange which has been firmly soldered between two heat exchanger plates 2 .
- the oil 3, however, is supplied to or removed from the underside of the plate heat exchanger 1 .
- In the flow channel 4 is a partition plate 51 to keep oil 2 separated from oil 3 . Further information can be found in EP 819 907 B1.
- FIG. 1 In the embodiment of FIG.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
Die Erfindung betrifft einen Plattenwärmetauscher der im Oberbegriff des Anspruchs 1 beschriebenen
Art.
Ein Plattenwärmetauscher ist beispielsweise aus dem EP 819 907 B1 bekannt. Bei diesem
Plattenwärmetauscher sind in den Wärmetauscherplatten, die die horizontalen Kanäle für das Heiz -
oder Kühlmedium bilden, Noppen oder ähnliche Vorsprünge eingeprägt worden. Die Noppen benachbarter
Wärmetauscherplatten berühren sich und sind miteinander verlötet, um die Festigkeit des Plattenwärmetauschers
anzuheben. Solche Noppen haben sich im allgemeinen bewährt und werden auch
deshalb sehr häufig vorgesehen, weil sie praktisch keinen spürbaren Druckverlust verursachen. Es hat
sich jedoch herausgestellt, daß die Haltbarkeit einer solchen Ausgestaltung für extreme Belastungen,
sowohl durch Temperaturschocks als auch durch extreme betriebsbedingte Vibrationen, nicht immer
ausreichend ist.
Ein dem Oberbegriff entsprechender Plattenwärmetauscher geht aus der US 4 653 581 hervor.
Der Inneneinsatz ist dort ganzflächig wie eine Wellrippe ausgebildet. Die Wellrippe bietet nicht die
gewünschte hohe Druckstabilität, weil die Verbindungsflächen zwischen der Wellrippe und den Wärmetauscherplatten
zu klein sind.
Um die Festigkeit beziehungsweise Haltbarkeit gegenüber den genannten Einflüssen anzuheben, wurde
in dem aus dem EP 258 236 B1 bekannten Plattenwärmetauscher vorgesehen, die äußeren, dickeren
Stützplatten (obere und untere Abdeckplatte) mit einer wellenförmigen Struktur auszubilden. Damit
wird eine verbesserte Haltbarkeit erreicht, jedoch nur zwischen den erwähnten Platten und den angrenzenden
Wärmetauscherplatten. Eine ähnliche Problemlage findet sich in der DE 197 11 258 A1, in
der zwischen der Grundplatte und der untersten Wärmetauscherplatte eine Verstärkungsplatte mit
einem Bord eingefügt wurde. Den auch im Inneren des Plattenwärmetauschers wirkenden Belastungen
kann mit den Lehren dieser beiden Veröffentlichungen nicht begegnet werden.
Um die Festigkeit im Inneren anzuheben, aber vor allem, um Turbulenzen im Medium zu erzeugen,
setzt man gewöhnlich entsprechende Inneneinsätze (Lamellen) in die Kanäle ein, die mit den Wärmetauscherplatten
verlötet sind. Diese führen jedoch häufig zu hohem Druckverlust.
Die Aufgabe der Erfindung besteht darin, die Haltbarkeit des Plattenwärmetauschers im Inneren zu verbessern,
ohne den Druckverlust des durch die Kanäle strömenden Mediums wesentlich zu erhöhen.
Die erfindungsgemäße Lösung besteht darin, daß der Inneneinsatz eine Zusatzplatte ist, die Führungskanäle
mit mindestens einem Ein - und einem Austritt besitzt, die von einem Strömungskanal
des einen Mediums zum anderen Strömungskanal desselben Mediums hinführen, wozu die meisten
Führungskanäle eine Krümmung aufweisen, wobei die von Führungskanälen freien Abschnitte der
Zusatzplatte mit der einen angrenzenden Wärmetauscherplatte und die Führungskanäle mit der anderen
angrenzenden Wärmetauscherplatte desselben Kanals metallisch verbunden sind.
Dadurch führt der erfindungsgemäße Plattenwärmetauscher zu folgenden Vorteilen. Die mit mindestens
einem Eintritt und einem Austritt versehenen Führungskanäle und die Ausrichtung der Mehrzahl
der Führungskanäle von einem Strömungskanal auf den anderen, bewirken einen sehr geringen
Druckverlust, dessen Höhe, je nach Betriebsbedingungen, durchaus vergleichbar ist, mit den im Stand
der Technik beschriebenen Noppen. Die Haltbarkeit gegenüber Temperaturschocks und extremen
Temperaturwechselbelastungen sowie mechanischen Beanspruchungen ist wesentlich verbessert
worden, weil die Zusatzplatte beidseitig, das heißt, mit beiden Wärmetauscherplatten, verbunden ist.
Die Verbindungsflächen sind wesentlich größer als beim Stand der Technik, was für die Haltbarkeit,
beispielsweise von Lötverbindungen, entscheidend ist. Die Mehrzahl der Führungskanäle soll von einem
Strömungskanal des einen Mediums zum anderen Strömungskanal desselben Mediums gerichtet
sein. Das bedeutet, daß die allgemeine Ausrichtung der Mehrzahl der Führungskanäle von einem
Strömungskanal zum anderen Strömungskanal wie beschrieben ausgeführt sein soll, wobei die Führungskanäle,
insbesondere bei quaderförmigen Plattenwärmetauschern mit in den Ecken angeordneten
Strömungskanälen, durchaus bogenartig verlaufen können, also nicht geradlinig von einem zum
anderen Strömungskanal verlaufen müssen.
Die Zusatzplatten des erfindungsgemäßen Plattenwärmetauschers können sich in sämtlichen seiner
Kanäle befinden.
Die Zusatzplatte weist vier Öffnungen auf, die bezüglich ihrer Position mit den die Strömungskanäle
bildenden Öffnungen in den Wärmetauscherplatten übereinstimmen. Bezüglich ihrer Funktion sind die
mittels der Führungskanäle verbundenen zwei Öffnungen in der Zusatzplatte größer als die korrespondierenden
Öffnungen in den Wärmetauscherplatten und mit einer an die Anordnung der Führungskanäle
angepaßten Form versehen. Es wurde durch umfangreiche Versuche ermittelt, daß diese Maßnahme
einen wesentlichen Anteil daran hat, daß der Druckverlust weiter gesenkt werden konnte. Die
Form der erwähnten Öffnungen und die Anordnung der Führungskanäle sollen aneinander angepaßt
sein. In einem bevorzugten Ausführungsbeispiel weisen diese Öffnungen eine von der Kreisform abweichende
Gestalt auf. Insbesondere sind die Öffnungen mit Ausbuchtungen in Richtung auf die Ein -
bzw. Austritte ausgewählter Führungskanäle versehen. Die anderen beiden Öffnungen in der Zusatzplatte,
die für ein anderes Medium vorgesehen sind und die nicht mittels Führungskanäle verbunden
sind, können in ihrer Form identisch mit den Öffnungen in den Wärmetauscherplatten sein.The invention relates to a plate heat exchanger described in the preamble of
A plate heat exchanger is known, for example, from EP 819 907 B1. In this plate heat exchanger, nubs or similar protrusions have been embossed in the heat exchanger plates forming the horizontal channels for the heating or cooling medium. The nubs of adjacent heat exchanger plates touch and are soldered together to increase the strength of the plate heat exchanger. Such knobs have generally proven themselves and are therefore very often provided because they cause practically no noticeable pressure loss. However, it has been found that the durability of such a design for extreme loads, both by temperature shocks as well as by extreme operational vibrations, is not always sufficient.
A plate heat exchanger corresponding to the preamble is disclosed in US Pat. No. 4,653,581. The inner insert is formed over its entire surface like a corrugated rib. The corrugated fin does not offer the desired high pressure stability, because the connecting surfaces between the corrugated fin and the heat exchanger plates are too small.
In order to increase the strength or durability against the aforementioned influences, it was provided in the plate heat exchanger known from EP 258 236 B1 to form the outer, thicker support plates (upper and lower cover plate) with a wave-shaped structure. Thus, an improved durability is achieved, but only between the mentioned plates and the adjacent heat exchanger plates. A similar problem situation can be found in DE 197 11 258 A1, in which a reinforcing plate with a board was inserted between the base plate and the lowermost heat exchanger plate. The stresses also acting inside the plate heat exchanger can not be met with the teachings of these two publications.
In order to increase the strength inside, but especially to create turbulence in the medium, it is common to insert corresponding inner inserts (lamellae) into the channels, which are soldered to the heat exchanger plates. However, these often lead to high pressure loss.
The object of the invention is to improve the durability of the plate heat exchanger inside without substantially increasing the pressure loss of the medium flowing through the channels.
The solution according to the invention is that the inner insert is an additional plate having guide channels with at least one inlet and one outlet leading from one flow channel of one medium to the other flow channel of the same medium, to which most of the guide channels have a curvature, the Guide channels free portions of the additional plate with the one adjacent heat exchanger plate and the guide channels are metallically connected to the other adjacent heat exchanger plate of the same channel.
As a result, the plate heat exchanger according to the invention leads to the following advantages. The provided with at least one inlet and an outlet guide channels and the alignment of the plurality of guide channels from one flow channel to the other, cause a very low pressure drop, the height, depending on the operating conditions, is quite comparable, with the nubs described in the prior art. The durability against thermal shocks and extreme thermal cycling and mechanical stresses has been significantly improved because the additional plate on both sides, that is, with both heat exchanger plates, is connected. The bonding surfaces are much larger than in the prior art, which is crucial for durability, such as solder joints. The plurality of guide channels should be directed from a flow channel of one medium to the other flow channel of the same medium. This means that the general orientation of the majority of the guide channels from one flow channel to the other flow channel should be carried out as described, wherein the guide channels, in particular in rectangular plate heat exchangers with arranged in the corners flow channels, may well be arcuate, so not straight from one to another Flow channel must run.
The additional plates of the plate heat exchanger according to the invention can be located in all its channels.
The additional plate has four openings which coincide in position with the flow channels forming openings in the heat exchanger plates. With regard to their function, the two channels connected in the auxiliary plate by means of the guide channels are larger than the corresponding openings in the heat exchanger plates and provided with a shape adapted to the arrangement of the guide channels. It has been determined by extensive experiments that this measure has a significant part in that the pressure loss could be further reduced. The shape of the mentioned openings and the arrangement of the guide channels should be adapted to each other. In a preferred embodiment, these openings have a different shape from the circular shape. In particular, the openings are provided with bulges in the direction of the inlets or outlets of selected guide channels. The other two openings in the auxiliary plate, which are intended for another medium and which are not connected by means of guide channels, may be identical in shape to the openings in the heat exchanger plates.
Der Anspruch 4 sieht vor, daß sich die Zusatzplatte in wenigstens einem der Kanäle für das Heiz -
oder Kühlmedium befindet. Es hat sich in der Praxis erwiesen, daß hauptsächlich die Kanäle für das
Heiz - oder Kühlmedium gegenüber extremen Temperaturschocks und Temperaturwechselbelastungen
bezüglich der Haltbarkeit problematisch waren. Der Anspruch 4 wirkt dem entgegen.
Anspruch 5 sieht vor, daß bei Plattenwärmetauschern für mehr als zwei Medien wenigstens die Kanäle
für das Heiz - oder Kühlmedium, die auf einer Seite an einen Kanal des einen Mediums und auf der
anderen Seite an einen Kanal des anderen Mediums angrenzen mit einer Zusatzplatte ausgerüstet
sind. Das ist deshalb vorteilhaft, weil in den Übergangsbereichen von einem Medium auf ein anderes
die Temperaturdifferenzen und damit die Beanspruchungen am größten sind.The
Nach Anspruch 6 ist von Vorteil, daß einige Führungskanäle Abzweigungen aufweisen und andere
Führungskanäle ohne Abzweigungen ausgebildet sind. Dadurch kann die Anordnung der Führungskanäle
dem jeweiligen Anwendungsfall angepaßt und optimiert werden. According to
Insbesondere in der Nähe der Abzweigungen werden strömungstechnische Vorteile, beispielsweise
eine gleichmäßigere Verteilung der Strömung bzw. des Wärmeaustausches, dadurch erreicht, daß
dort zusätzliche Ein - bzw. Austrittsöffnungen in den Führungskanälen angeordnet sind.
Die Abzweigungen können sich zwischen dem Rand der Wärmetauscherplatte und den Strömungskanälen
befinden. Dadurch werden bei im wesentlichen rechteckigen Wärmetauscherplatten die Eckbereiche
des Wärmetauschers intensiv am Wärmeaustausch beteiligt, wodurch die Leistung desselben
verbessert wird. Von der Anmelderin durchgeführte Untersuchungen zeigen eine sehr homogene Verteilung
des Wärmeaustausches über alle Bereiche der Wärmetauscherplatten und der Zusatzplatten.In particular in the vicinity of the branches, fluidic advantages, for example a more uniform distribution of the flow or the heat exchange, are achieved in that additional inlet and outlet openings are arranged in the guide channels.
The branches may be located between the edge of the heat exchanger plate and the flow channels. As a result, the corner portions of the heat exchanger are intensively involved in heat exchange in substantially rectangular heat exchanger plates, whereby the performance thereof is improved. Investigations by the applicant show a very homogeneous distribution of heat exchange over all areas of the heat exchanger plates and the additional plates.
Anspruch 8 beschreibt eine vorteilhafte Anordnung der Führungskanäle, die darin besteht, daß einige
Führungskanäle von einem Strömungskanal zum anderen Strömungskanal durchgehend ausgebildet
sind und andere Führungskanäle wesentlich kürzer sind, wobei ihr Austritt und ihr Eintritt entfernt von
den Strömungskanälen angeordnet ist.
Anspruch 9 stellt eine vorteilhafte Zusatzmaßnahme dar und schreibt vor, daß die Zusatzplatte Noppen
oder dergleichen Vorsprünge aufweisen soll, die die gleiche Höhe wie die Führungskanäle besitzen
und die mit der angrenzenden Wärmetauscherplatte verbunden sind. Die Noppen sind in der Nähe der
Strömungskanäle bzw. in nicht so eng mit Führungskanälen belegten Flächen der Zusatzplatte angeordnet
und stützen deshalb diese Flächen zusätzlich ab.
Die erfindungsgemäße Zusatzplatte kann wesentlich dünner als die Wärmetauscherplatten und damit
material - und gewichtssparend ausgeführt sein. In einem Ausführungsbeispiel beträgt die Dicke der
Wärmetauscherplatten 0, 5 mm und die der Zusatzplatten lediglich 0, 3 mm.The additional plate according to the invention can be much thinner than the heat exchanger plates and thus
be carried out material - and weight saving. In one embodiment, the thickness of the
Weitere Merkmale und Vorteile sind in der nachfolgenden Beschreibung eines Ausführungsbeispiels enthalten. Die beiliegenden Figuren zeigen Folgendes:
- Fig. 1
- Draufsicht auf die eingelegte Zusatzplatte;
- Fig. 2
- Teil - Schnitt A - A aus Fig. 1;
- Fig. 3
- Teil - Schnitt B - B aus Fig. 1;
- Fig. 4
- Schnitt durch den Plattenwärmetauscher, der Zusatzplatten aufweist;
- Fig. 5
- Variante zu Fig. 4;
In
In der Nähe der Öffnungen 33 und 35
- Fig. 1
- Top view of the inserted additional plate;
- Fig. 2
- Part - section A - A of Fig. 1;
- Fig. 3
- Part - Section B - B of Fig. 1;
- Fig. 4
- Section through the plate heat exchanger having additional plates;
- Fig. 5
- Variant to Fig. 4;
In the
The
In the vicinity of the
Der um die Öffnungen 33 und 35 vorhandene nicht verformte Bereich in der Zusatzplatte 6 wurde
durch die Noppen 14 verstärkt.
Aus der Fig. 2 ist die Gestaltung der Führungskanäle 8 zu erkennen, die sickenartig ausgebildet sind.
Die Führungskanäle 8 sind mit der einen Wärmetauscherplatte 2 des Kanals 5 verbunden, während
die dazwischen angeordneten Abschnitte 11 mit der anderen Wärmetauscherplatte 2 metallisch verbunden
sind. Der abgebogene Rand 13 der Wärmetauscherplatten 2 wurde nicht gezeichnet. Dieser
ist jedoch in den nachfolgend beschriebenen Figuren 4 und 5 gut zu erkennen.
In der Fig. 4 ist der Rand 13 der Wärmetauscherplatten 2, in Einbaulage des Plattenwärmetauschers 1
gesehen, nach oben gerichtet und in Fig. 5 nach unten. Beide Ausführungsbeispiele zeigen unterschiedliche
Varianten eines Retarder - Ölkühlers, der für den Einsatz bei Lastkraftwagen gedacht ist,
um das Bremsöl zu kühlen. In solchen Ölkühlern treten extrem hohe Öltemperaturen von mehr als 200
°C auf. Je nach Betriebssituation treten hohe Temperaturschockbelastungen auf, denen der Ölkühler
gewachsen ist, wie umfangreiche Versuchsreihen bewiesen haben. Die Fig. 4 zeigt einen Querschnitt
durch den Plattenwärmetauscher 1 mit insgesamt vier getrennten Kreisläufen.
Der Strömungskanal 4 für das Kühl - oder Heizmedium K befindet sich in Fig. 4 auf der linken Seite.
Rechts ist der Strömungskanal 4 für Öl 1, Öl 2 und Öl 3 zu erkennen. Es gibt weitere zwei nicht gezeigte
Strömungskanäle 4 für den Austritt der Medien. Die Strömungskanäle 4 besitzen Anschlußflansche
3. Der Anschlußflansch 3 für Öl 1 besitzt einen nicht gezeigten Verbindungskanal, so daß das Öl
1 durch diesen Verbindungskanal eintreten und in den oberen Kanälen 5 mit dem Kühlmittel K im
Wärmeaustausch ist. Sämtliche Kanäle 5 für Öl 1; Öl 2 und Öl 3 besitzen übliche Lamellen 53. Das Öl
2 tritt ebenfalls am Anschlußflansch 3 in den Plattenwärmetauscher 1 ein und zwar durch das Rohrstück
50 mit einem Flansch, der zwischen zwei Wärmetauscherplatten 2 fest eingelötet wurde. Das Öl
3 hingegen wird von der Unterseite des Plattenwärmetauschers 1 zu - bzw. abgeführt. Im Strömungskanal
4 befindet sich eine Trennplatte 51 um Öl 2 von Öl 3 getrennt zu halten. Weitere Informationen
dazu befinden sich im EP 819 907 B1. Im Ausführungsbeispiel der Fig. 4 wurden nun sämtliche Kanäle
5 für das Kühlmittel K mit einer Zusatzplatte 6 ausgerüstet, wodurch die Haltbarkeit des Plattenwärmetauschers
1 deutlich verbessert wurde. Bei einem anderen nicht gezeigten Ausführungsbeispiel sind
nur die Kanäle 5 für das Kühlmittel K, die an die Abschnitte a für Öl 1, b für Öl 2 und c für Öl 3 angrenzen
mit Zusatzplatten 6 ausgerüstet worden.
Im Ausführungsbeispiel nach Fig. 5 ist ein Plattenwärmetauscher 1 mit einem Kreislauf für das Kühlmittel
K und einem Ölkreislauf Öl dargestellt. Nur die beiden oberen und die beiden unteren Kanäle 5
für das Kühlmittel K wurden mit Zusatzplatten 6 versehen, weil sich herausgestellt hat, daß die äußeren
Kanäle 5 den stärksten Temperaturdifferenzen ausgesetzt sind. Die Wärmetauscherplatten 2 der
übrigen Kanäle 5 für das Kühlmittel K wurden wie üblich mit Noppen 52 ausgebildet, die sich berühren
und miteinander verlötet sind.The non-deformed area in the
From Fig. 2, the design of the
In Fig. 4 , the
The
In the embodiment of FIG. 5, a
Claims (9)
- Plate heat exchanger (1) for heat-exchanging media in separate circuits, consisting of metallically connected individual heat exchanger plates (2) which are stacked one in the other and possess orifices (15 - 18) and which form a bundle pierced vertically by flow ducts (4), formed by means of the orifices (15 - 18), for the inflow and outflow of the heating or cooling medium (K) and by flow ducts (4) for the other medium or media, which flow ducts are separated from one another and starting from which the heating or cooling medium (K) and the other medium or media are propagated in ducts (5) which are formed in each case by two heat exchanger plates (2) and at least some of which have an inner insert (6), the inner insert (6) being an additional plate which possesses guide ducts (8) with at least one inlet and one outlet (9; 10), characterized in that the guide ducts lead from one flow duct (4) of the one medium to the other flow duct (4) of the same medium, for which purpose most guide ducts (8) have a curvature, the additional plate (6) of guide ducts (8) possessing free portions (11), and the free portions (11) being metallically connected to one adjacent heat exchanger plate (2) and the guide ducts (8) being metallically connected to the other adjacent heat exchanger plate (2) of the same duct (5).
- Plate heat exchanger according to Claim 1, characterized in that the additional plate (6) has four orifices (32 to 35) which coincide in respect of their position with the orifices (15 to 18), forming the flow ducts (4), in the heat exchanger plates (2).
- Plate heat exchanger according to Claims 1 and 2, characterized in that the two orifices (32; 34) in the additional plate (6) which are connected by means of the guide ducts (8) possess a shape adapted to the arrangement of the guide ducts (8), the orifices (32; 34) having bays (40) in the direction of the inlet or outlet (9; 10) of the guide ducts (8).
- Plate heat exchanger according to one of Claims 1 to 3, characterized in that the additional plate (6) is located in at least one of the ducts (5) for the heating or cooling medium (K).
- Plate heat exchanger according to one of Claims 1 to 4, characterized in that, in the case of plate heat exchangers (1) for more than two media, at least the ducts (5) for the heating or cooling medium which are adjacent on one side to a duct (5) of one medium and on the other side to a duct (5) of the other medium or are located in their vicinity (portions a, b, c) are equipped with an additional plate (6).
- Plate heat exchanger according to one of Claims 1 to 5, characterized in that the guide ducts (8) are of bead-like design, the bead height corresponding to the distance between the heat exchanger plates (2) forming the respective duct (5), and in that some guide ducts (8) have branches (30) and other guide ducts (8) are designed without branches (30).
- Plate heat exchanger according to Claim 6, characterized in that additional inlets or outlets (9a; 10a) in the guide ducts (8) are arranged in the region of the branches (30), and in that (in the case of parallelepipedic plate heat exchangers (1)) at least one branched guide duct (8) is provided between the edge (13) of the heat exchanger plate (2) and the flow ducts (4) or in the corner regions (22 - 25) of the plate heat exchanger (1).
- Plate heat exchanger according to one of the preceding claims, characterized in that some guide ducts (8) are designed to be continuous from one flow duct (4) to the other flow duct (4) and other guide ducts (8) are substantially shorter, their outlet (10) and their inlet (9) being arranged at a distance from the flow ducts (4).
- Plate heat exchanger according to one of the preceding claims, characterized in that the additional plate (6) has bosses (14) or suchlike projections which possess the same height as the guide ducts (8) and which are connected to the adjacent heat exchanger plate (2).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10021481A DE10021481A1 (en) | 2000-05-03 | 2000-05-03 | Plate heat exchanger |
DE10021481 | 2000-05-03 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1152204A2 EP1152204A2 (en) | 2001-11-07 |
EP1152204A3 EP1152204A3 (en) | 2002-06-12 |
EP1152204B1 true EP1152204B1 (en) | 2003-11-19 |
Family
ID=7640610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01107118A Expired - Lifetime EP1152204B1 (en) | 2000-05-03 | 2001-03-22 | Plate type heat exchanger |
Country Status (4)
Country | Link |
---|---|
US (1) | US6530425B2 (en) |
EP (1) | EP1152204B1 (en) |
DE (2) | DE10021481A1 (en) |
ES (1) | ES2211683T3 (en) |
Cited By (2)
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DE102006048305B4 (en) * | 2006-10-12 | 2011-06-16 | Modine Manufacturing Co., Racine | Plate heat exchanger |
DE102014015170B3 (en) * | 2014-10-10 | 2015-10-15 | Modine Manufacturing Company | Soldered heat exchanger and manufacturing process |
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-
2000
- 2000-05-03 DE DE10021481A patent/DE10021481A1/en not_active Withdrawn
-
2001
- 2001-03-22 EP EP01107118A patent/EP1152204B1/en not_active Expired - Lifetime
- 2001-03-22 DE DE50100984T patent/DE50100984D1/en not_active Expired - Lifetime
- 2001-03-22 ES ES01107118T patent/ES2211683T3/en not_active Expired - Lifetime
- 2001-05-01 US US09/846,629 patent/US6530425B2/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006048305B4 (en) * | 2006-10-12 | 2011-06-16 | Modine Manufacturing Co., Racine | Plate heat exchanger |
DE102014015170B3 (en) * | 2014-10-10 | 2015-10-15 | Modine Manufacturing Company | Soldered heat exchanger and manufacturing process |
Also Published As
Publication number | Publication date |
---|---|
EP1152204A3 (en) | 2002-06-12 |
DE10021481A1 (en) | 2001-11-08 |
US6530425B2 (en) | 2003-03-11 |
EP1152204A2 (en) | 2001-11-07 |
ES2211683T3 (en) | 2004-07-16 |
DE50100984D1 (en) | 2003-12-24 |
US20010054501A1 (en) | 2001-12-27 |
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