EP1141564A1 - Axial bearing for high-speed rotors - Google Patents
Axial bearing for high-speed rotorsInfo
- Publication number
- EP1141564A1 EP1141564A1 EP99973582A EP99973582A EP1141564A1 EP 1141564 A1 EP1141564 A1 EP 1141564A1 EP 99973582 A EP99973582 A EP 99973582A EP 99973582 A EP99973582 A EP 99973582A EP 1141564 A1 EP1141564 A1 EP 1141564A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- bearing
- membrane
- axial
- cavity
- axial bearing
- 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.)
- Withdrawn
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/08—Elastic or yielding bearings or bearing supports, for exclusively rotary movement primarily for axial load, e.g. for vertically-arranged shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
Definitions
- the invention relates to an axial bearing for high-speed rotors, with a device for misalignment compensation.
- An axial bearing for high-speed rotors must have sufficient axial rigidity so that the deflection under the maximum axial load does not exceed a certain limit. Due to the manufacturing process, however, when shafts and other rotors are supported, the shaft and thus the bearing crest of the axial bearing are misaligned, as a result of which the bearing's load-bearing capacity decreases. In order to counter this danger, numerous constructive solutions to compensate for the misalignment have been found, e.g. by elastic deformation, with eccentric support or by elastic deformation of a membrane (Dubbel, paperback for mechanical engineering, ISBN 3-540- 57650-9, 18th edition, Springer-Verlag Berlin Heidelberg New York, 1995, G95 / 96).
- turbochargers for example, in turbochargers or other turbomachinery.
- the latter are reinforced if the turbomachine is subjected to additional tilting movements during operation (e.g. for turbochargers for ship engines).
- EP 0 362 327 B1 discloses a solution for misalignment compensation in the case of an axial bearing for a turbomachine.
- the misalignment of the shaft and thus the bearing comb is compensated for by means of elastic webs, which means that the bearing has sufficient elasticity for permissible deformations. tion, but on the other hand is wear-free to prevent excessive deformation.
- the invention has for its object to provide an improved axial bearing for high-speed rotors, which is extremely steep in the axial direction and very soft with respect to misalignment. In addition, space is to be saved in the storage area in the axial direction.
- the load introduction body has a tread body adjoining the bearing comb, a membrane connected to the bearing flange and a central ring connecting the tread body to the membrane.
- the load introduction body is tapered from the tread body to the central ring.
- the membrane is supported on one side on an incompressible medium which fills a cavity arranged on the side of the membrane facing away from the bearing comb between the membrane and an element delimiting the cavity.
- the element delimiting the cavity is either supported on the bearing flange or is formed by the latter.
- the axial flexibility of the membrane can be reduced and an axially very rigid axial bearing can thus be realized.
- the membrane which is very soft in the axial direction
- the torsional stiffness of the axial bearing is significantly reduced, so that the misalignment that occurs can be better compensated for using such a membrane than was previously possible.
- the load capacity of the thrust bearing can be guaranteed over a longer period of time, thus increasing its service life. If the required axial rigidity is maintained, the solution according to the invention can be used to reduce the axially required installation space to approximately one third compared to conventional misalignment compensation.
- the load introduction body is particularly advantageously formed in one piece. In this way, a high wear resistance of the thrust bearing can be achieved.
- the membrane has a central area adjoining the central ring, an edge area connected to the element delimiting the cavity, and an intermediate area, both the central area and the edge area being thickened relative to the intermediate area of the membrane.
- an axial stop projecting into the cavity for the central ring is advantageously arranged on the element delimiting the cavity. This stop prevents the destruction of the thrust bearing in the event of an accident in which there is a loss of the incompressible medium filling the cavity.
- the stop also acts as a hydraulic damper.
- the element delimiting the cavity is advantageously designed as a cover. As a result, both the manufacture and the assembly can be significantly simplified.
- FIG. 1 shows a partial longitudinal section through the bearing of a shaft, with two radial bearings and with an axial bearing, including a device for misalignment compensation.
- FIG. 2 shows an enlarged detail from FIG. 1, in the area of the axial bearing;
- FIG. 3 is a representation analogous to FIG. 2, but in a second embodiment.
- FIG. 1 shows a shaft 4, which is mounted by means of two radial bearings 1, 2 and an axial bearing 3.
- this is the shaft 4 of an exhaust gas turbocharger, not shown here, consisting mainly of a radial compressor and a turbine.
- Both the radial bearings 1, 2 and the axial bearing 3 are arranged in a bearing housing 5.
- Part of the bearing housing 5 is a bearing flange 6, which is used to fasten the bearing housing 5 in the interior of a shaft housing of the exhaust gas turbocharger, also not shown.
- the bearing flange 6 is connected to the bearing housing 5 via fastening elements 7 designed as screws.
- the compressor-side radial bearing 1 is fixed to the bearing flange 6 by means of a cover 8, for which purpose further fastening elements 9 designed as screws are used.
- a lubricating oil supply 10, 11 for the radial bearing 2 or for the radial bearing 1 and for the axial bearing 3 is arranged both in the bearing housing 5 and in the bearing flange 6.
- the axial bearing 3 consists of a rotating bearing comb 12 which is fixedly connected to the shaft 4 and which cooperates with a fixed load introduction body 13.
- the bearing comb 12 and the load introduction body 13 each have a running surface 14, between which a lubricating oil gap 15 of the axial bearing 3 is formed (FIG. 1).
- the load introduction body 13 is formed in one piece. It consists of a tread body 16 adjoining the bearing comb 12, a membrane 17 connected to the bearing flange 6 and a central ring 18 connecting the tread body 16 to the membrane 17 and is tapered from the tread body 16 to the central ring 18
- a cover 19 is arranged between the membrane 17 and the bearing flange 6 such that a cavity 20 is formed between the cover 19 and the membrane 17 in the cover 19, which acts as an element delimiting the cavity 20
- a supply channel 22, which is connected to the cavity 20 and is closed by a stopper 21, is arranged for a mcompressible medium 23 which fills the cavity 20.
- a medium 23 mainly fluids and in particular synthetic oils come into question.
- Fluids such as water, but also solid substances (e.g. low-melting metals) are suitable
- the cover 19 has an axial stop 24 protruding into the cavity 20 for the central ring 18.
- the membrane 17 has a central region 25 adjoining the central ring 18, an edge region 26 connected to the bearing flange 6 and an intermediate region 27 (FIG. 2) the central region 25 and the edge region 26 are thickened with respect to the intermediate region 27 of the membrane 17, so that the actual membrane is formed by the intermediate region 27
- the bearing flange 6 has a corresponding recess 28 for receiving the load introduction body 13, ie for the membrane 17.
- a fit 29 is formed in the region of the recess 28 between the bearing flange 6 and the membrane 17, into which the separately manufactured load introduction body 13 is pressed
- a material connection between the bearing flange 6 and the membrane 17 can also take place.
- a further fit 30 is formed between the cover 19 and the membrane 17, the corresponding connection being welded.
- another material connection can also be made (for example, by soldering), a non-positive or a positive connection can be realized
- the separately manufactured load introduction body 13 can be connected to the cover 19 even before it is installed in the bearing flange 6, and the cavity 20 can be filled with the incompressible medium 23, so that simple and inexpensive manufacture and final assembly is made possible by using a coated tempering steel for the load introduction body 13 is a high strength can be achieved, the axial stop 24 in the cavity 20 prevents d ⁇ e "* ax ⁇ ale rigidity of the thrust bearing 3 in case of loss of the non-compressible medium 23 is lost this security thoughts, by using a material with good emergency running properties (for example spring bronze) for the load introduction body 13 are further taken into account
- the axial thrust of the turbine designated F1 is oriented toward the radial compressor and acts mainly on the axial bearing 3 in the axial direction.
- the axial forces that occur are transmitted via the bearing comb 12, the tread body 16, the central ring 18 and the membrane 17 to the bearing flange 6
- the actual force transmission is supported by the local thickening of the membrane 17 in its central area 25 and in the edge area 26.
- the axial flexibility of the membrane 17 is prevented by the support on the incompressible medium 23 (for example hydraulic), so that only slight deflections in the tenths range can occur.
- the incompressible medium 23 acts as an axial steamer and can therefore counteract a build-up of the axial forces, which could otherwise lead to an accident, which arise due to the design or operation Shoot Positions of the shaft 4 and thus the bearing comb 12 of the thrust bearing 3 are compensated for by the axially very soft membrane 17.
- the misalignment stiffness can be significantly reduced compared to the known solutions of the prior art and the service life of the thrust bearing 3 can be increased accordingly
- the lubricating oil passes through the lubricating oil supply 10, via a circumferential groove 31 arranged in the bearing housing 5, and via a correspondingly designed supply 32 of the radial bearing 2 into its lubricating oil gap 33.
- the lubricating oil gap 34 of the radial bearing 1 or the running surface 14 of the axial bearing 13 are arranged in the bearing flange 6 Lubricating oil supply 1 1 supplied with lubricating oil
- the cavity 20 filled with the incompressible medium 23 is formed between the membrane 17 and the bearing flange 6, so that the latter forms the element delimiting the cavity 20.
- the feed channel 22 for the medium 19 is therefore arranged in the bearing flange 6
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Supercharger (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The aim of the invention is to provide an improved axial bearing for high-speed rotors which is extremely stiff in the axial direction and very soft as regards inclined positions. It also aims to save space in the axial direction in the area of the bearing. To this end the invention provides for the load induction element (13) to comprise a bearing race body (16) adjoining the bearing collar (12), a membrane (17) joined to the bearing flange (6) and a central ring (18) which connects the bearing race body (16) to the membrane (17). The load induction element (13) is configured such that it narrows from the bearing race body (16) towards the central ring (18). The membrane (17) is supported on one side on an incompressible medium (23) which fills a hollow space (20) which is situated on the side of the membrane (17) facing away from the bearing collar (12) and is defined between the membrane (17) and an element (19) delimiting said hollow space (20). The element (19) limiting the hollow space (20) is either supported by the bearing flange (6) or embodied by same.
Description
Axiallagerung für schnellaufende Rotoren Axial bearing for high-speed rotors
Technisches GebietTechnical field
Die Erfindung betrifft eine Axiallagerung für schnellaufende Rotoren, mit einer Einrichtung zur Schiefstellungskompensation.The invention relates to an axial bearing for high-speed rotors, with a device for misalignment compensation.
Stand der TechnikState of the art
Eine Axiallagerung für schnellaufende Rotoren muss eine ausreichende axiale Steifigkeit aufweisen, so dass die Einfederung unter der maximal auftretenden Axiallast einen bestimmten Grenzwert nicht überschreitet. Herstellungsbedingt treten jedoch bei der Abstützung von Wellen und anderen Rotoren Schiefstellungen der Welle und damit des Lagerkammes des Axiallagers auf, in deren Folge die Tragfähigkeit des Lagers sinkt. Um dieser Gefahr zu begegnen wurden zahlreiche konstruktive Lösungen zum Ausgleich der Schiefstellungen gefunden, z.B. durch elastische Verformung, bei exzentrischer Stützung oder durch elastische Verformung einer Membran (Dubbel, Taschenbuch für den Maschinenbau, ISBN 3-540- 57650-9, 18. Aufl., Springer- Verlag Berlin Heidelberg New York, 1995, G95/96).An axial bearing for high-speed rotors must have sufficient axial rigidity so that the deflection under the maximum axial load does not exceed a certain limit. Due to the manufacturing process, however, when shafts and other rotors are supported, the shaft and thus the bearing crest of the axial bearing are misaligned, as a result of which the bearing's load-bearing capacity decreases. In order to counter this danger, numerous constructive solutions to compensate for the misalignment have been found, e.g. by elastic deformation, with eccentric support or by elastic deformation of a membrane (Dubbel, paperback for mechanical engineering, ISBN 3-540- 57650-9, 18th edition, Springer-Verlag Berlin Heidelberg New York, 1995, G95 / 96).
Zudem kommt es aufgrund von Rotorunwuchten solcher schnellaufenden Rotoren, wie sie beispielsweise bei Turboladern oder anderen Turbomaschinen Verwendung finden, zu betriebsbedingten Schiefstellungen. Letztere werden noch verstärkt, wenn die Turbomaschine im Betrieb zusätzlichen Kippbewegungen ausgesetzt ist (z.B. bei Turboladern für Schiffsmotoren).In addition, operational imbalances occur due to rotor imbalances of such high-speed rotors, as are used, for example, in turbochargers or other turbomachinery. The latter are reinforced if the turbomachine is subjected to additional tilting movements during operation (e.g. for turbochargers for ship engines).
Mit dem EP 0 362 327 B1 ist eine Lösung zur Schiefstellungskompensation bei einer Axiallagerung für eine Turbomaschine bekannt. Dabei wird die Schiefstellung der Welle und damit des Lagerkammes mittels elastischer Stege kompensiert, wodurch die Lagerung einerseits eine ausreichende Elastizität für zulässige Deforma-
tionen besitzt, andererseits jedoch verschleissfrei ist, um zu grosse Deformationen zu verhindern.EP 0 362 327 B1 discloses a solution for misalignment compensation in the case of an axial bearing for a turbomachine. The misalignment of the shaft and thus the bearing comb is compensated for by means of elastic webs, which means that the bearing has sufficient elasticity for permissible deformations. tion, but on the other hand is wear-free to prevent excessive deformation.
Eine solche Schiefstellungskompensation ist jedoch immer ein Kompromiss zwischen der erforderlichen axialen Steifigkeit und der gewünschten Nachgiebigkeit für Schiefstellungen. Zudem wird axial relativ viel Bauraum benötigt.However, such misalignment compensation is always a compromise between the required axial stiffness and the desired flexibility for misalignments. In addition, a relatively large amount of installation space is required axially.
Darstellung der ErfindungPresentation of the invention
Der Erfindung liegt die Aufgabe zugrunde, eine verbesserte Axiallagerung für schnellaufende Rotoren zu schaffen, die in axialer Richtung extrem steil und bezüglich Schiefstellung sehr weich ausgebildet ist. Zudem soll im Lagerbereich in axialer Richtung Bauraum eingespart werden.The invention has for its object to provide an improved axial bearing for high-speed rotors, which is extremely steep in the axial direction and very soft with respect to misalignment. In addition, space is to be saved in the storage area in the axial direction.
Erfindungsgemäss wird dies dadurch erreicht, dass bei einer Vorrichtung gemäss dem Oberbegriff des Anspruchs 1 , der Lasteinleitungskörper einen an den Lagerkamm anschliessenden Laufflächenkörper, eine mit dem Lagerflansch verbundene Membran sowie einen den Laufflächenkörper mit der Membran verbindenden Zentralring aufweist. Der Lasteinleitungskörper ist vom Laufflächenkörper zum Zentral- ring verjüngt ausgebildet. Die Membran ist einseitig auf einem inkompressiblen Medium abgestützt, welches einen auf der dem Lagerkamm abgewandten Seite der Membran angeordneten Hohlraum zwischen der Membran und einem den Hohlraum begrenzenden Element füllt. Dabei ist das den Hohlraum begrenzende Element entweder am Lagerflaπsch abgestützt oder wird von letzterem gebildet.This is achieved according to the invention in that, in a device according to the preamble of claim 1, the load introduction body has a tread body adjoining the bearing comb, a membrane connected to the bearing flange and a central ring connecting the tread body to the membrane. The load introduction body is tapered from the tread body to the central ring. The membrane is supported on one side on an incompressible medium which fills a cavity arranged on the side of the membrane facing away from the bearing comb between the membrane and an element delimiting the cavity. The element delimiting the cavity is either supported on the bearing flange or is formed by the latter.
Aufgrund dieser Abstützung der Membran auf einem inkompressiblen Medium kann die axiale Nachgiebigkeit der Membran vermindert und damit ein axial sehr steifes Axiallager realisiert werden. Durch die Verwendung der in axialer Richtung sehr weichen Membran wird jedoch vor allem die Verdreh steifigkeit des Axiallagers deutlich gesenkt, so dass die auftretenden Schiefstellungen über eine solche Membran besser kompensiert werden können, als das bisher möglich war. In der Folge kann die Tragfähigkeit des Axiallagers über einen längeren Zeitraum gewährleistet und so dessen Lebensdauer erhöht werden.
Bei Einhaltung der geforderten Axialsteifigkeit kann mit der erfindungsgemässen Lösung der axial benötigte Bauraum gegenüber einer konventionellen Schiefstellungskompensation auf etwa ein Drittel reduziert werden.Due to this support of the membrane on an incompressible medium, the axial flexibility of the membrane can be reduced and an axially very rigid axial bearing can thus be realized. However, by using the membrane, which is very soft in the axial direction, the torsional stiffness of the axial bearing is significantly reduced, so that the misalignment that occurs can be better compensated for using such a membrane than was previously possible. As a result, the load capacity of the thrust bearing can be guaranteed over a longer period of time, thus increasing its service life. If the required axial rigidity is maintained, the solution according to the invention can be used to reduce the axially required installation space to approximately one third compared to conventional misalignment compensation.
Besonders vorteilhaft ist der Lasteinleitungskörper einstückig ausgebildet. Auf diese Weise kann eine hohe Verschleissfestigkeit des Axiallagers erreicht werden.The load introduction body is particularly advantageously formed in one piece. In this way, a high wear resistance of the thrust bearing can be achieved.
Es ist besonders zweckmässig, wenn die Membran einen zentralen, an den Zentralring anschliessenden Bereich, einen mit dem den Hohlraum begrenzenden Element verbundenen Randbereich sowie einen Zwischenbereich aufweist, wobei sowohl der zentrale Bereich als auch der Randbereich gegenüber dem Zwischenbereich der Membran verdickt ausgebildet sind. Mit dieser Verstärkung der Bereiche, welche die Axialkräfte der entsprechenden Maschine aufnehmen bzw. übertragen müssen, kann die Standzeit des Axiallagers weiter erhöht werden.It is particularly expedient if the membrane has a central area adjoining the central ring, an edge area connected to the element delimiting the cavity, and an intermediate area, both the central area and the edge area being thickened relative to the intermediate area of the membrane. With this reinforcement of the areas that have to absorb or transmit the axial forces of the corresponding machine, the service life of the axial bearing can be increased further.
Weiterhin vorteilhaft ist am den Hohlraum begrenzenden Element ein in den Hohlraum hineinragender Axialanschlag für den Zentralring angeordnet. Dieser Anschlag verhindert die Zerstörung des Axiallagers in einem Havariefall, bei dem ein Verlust des den Hohlraum füllenden inkompressiblen Mediums eintritt. Zudem wirkt der Anschlag als hydraulischer Dämpfer.Furthermore, an axial stop projecting into the cavity for the central ring is advantageously arranged on the element delimiting the cavity. This stop prevents the destruction of the thrust bearing in the event of an accident in which there is a loss of the incompressible medium filling the cavity. The stop also acts as a hydraulic damper.
Schliesslich wird das den Hohlraum begrenzende Element mit Vorteil als ein Dek- kel ausgebildet. Dadurch können sowohl die Herstellung als auch die Montage deutlich vereinfacht werden.Finally, the element delimiting the cavity is advantageously designed as a cover. As a result, both the manufacture and the assembly can be significantly simplified.
Kurze Beschreibung der ZeichnungBrief description of the drawing
Die Erfindung wird nachstehend anhand von Ausführungsbeispielen näher erläutert. Es zeigen:The invention is explained in more detail below on the basis of exemplary embodiments. Show it:
Fig. 1 einen Teillängsschnitt durch die Lagerung einer Welle, mit zwei Radiallagern sowie mit einer Axiallagerung, einschliesslich einer Einrichtung zur Schiefstellungskompensation;
Fig. 2 einen vergrösserten Ausschnitt aus Fig. 1 , im Bereich der Axiallagerung;1 shows a partial longitudinal section through the bearing of a shaft, with two radial bearings and with an axial bearing, including a device for misalignment compensation. FIG. 2 shows an enlarged detail from FIG. 1, in the area of the axial bearing;
Fig. 3 eine Darstellung analog der Fig. 2, jedoch in einem zweiten Ausführungsbeispiel.Fig. 3 is a representation analogous to FIG. 2, but in a second embodiment.
Es sind nur die für das Verständnis der Erfindung wesentlichen Elemente gezeigt. Nicht dargestellt ist beispielsweise der mit der Welle verbundene, eigentliche Rotor der Maschine.Only the elements essential for understanding the invention are shown. For example, the actual rotor of the machine connected to the shaft is not shown.
Weg zur Ausführung der ErfindungWay of carrying out the invention
Die Figur 1 zeigt eine mittels zwei Radiallagern 1 , 2 sowie mit einem Axiallager 3 gelagerte Welle 4. Beispielsweise handelt es sich dabei um die Welle 4 eines hauptsächlich aus einem Radialverdichter sowie einer Turbine bestehenden, hier nicht dargestellten Abgasturboladers. Sowohl die Radiallager 1 , 2 als auch das Axiallager 3 sind in einem Lagergehäuse 5 angeordnet. Teil des Lagergehäuses 5 ist ein Lagerflansch 6, welcher zur Befestigung des Lagergehäuses 5 im Inneren eines ebenfalls nicht dargestellten Wellengehäuses des Abgasturboladers dient. Der Lagerflansch 6 ist über als Schrauben ausgebildete Befestigungselemente 7 mit dem Lagergehäuse 5 verbunden. Das verdichterseitige Radiallager 1 ist am Lagerflansch 6 mittels eines Deckels 8 fixiert, wozu weitere als Schrauben ausgebildete Befestigungselemente 9 dienen. Sowohl im Lagergehäuse 5 als auch im Lagerflansch 6 ist eine Schmierölzuführung 10, 11 für das Radiallager 2 bzw. für das Radiallager 1 sowie für das Axiallager 3 angeordnet.FIG. 1 shows a shaft 4, which is mounted by means of two radial bearings 1, 2 and an axial bearing 3. For example, this is the shaft 4 of an exhaust gas turbocharger, not shown here, consisting mainly of a radial compressor and a turbine. Both the radial bearings 1, 2 and the axial bearing 3 are arranged in a bearing housing 5. Part of the bearing housing 5 is a bearing flange 6, which is used to fasten the bearing housing 5 in the interior of a shaft housing of the exhaust gas turbocharger, also not shown. The bearing flange 6 is connected to the bearing housing 5 via fastening elements 7 designed as screws. The compressor-side radial bearing 1 is fixed to the bearing flange 6 by means of a cover 8, for which purpose further fastening elements 9 designed as screws are used. A lubricating oil supply 10, 11 for the radial bearing 2 or for the radial bearing 1 and for the axial bearing 3 is arranged both in the bearing housing 5 and in the bearing flange 6.
Das Axiallager 3 besteht aus einem mit der Welle 4 fest verbundenen, drehenden Lagerkamm 12, der mit einem feststehenden Lasteinleitungskörper 13 zusammenwirkt. Der Lagerkamm 12 und der Lasteinleitungskörper 13 weisen jeweils eine Lauffläche 14 auf, zwischen denen ein Schmierölspalt 15 des Axiallagers 3 ausgebildet ist (Fig. 1).
Der Lasteinleitungskorper 13 ist einstuckig ausgebildet Er besteht aus einem an den Lagerkamm 12 anschliessenden Laufflachenkorper 16, aus einer mit dem Lagerflansch 6 verbundenen Membran 17 sowie aus einem den Laufflachenkorper 16 mit der Membran 17 verbindenden Zentralring 18 und ist vom Laufflachenkorper 16 zum Zentralπng 18 verjungt ausgebildetThe axial bearing 3 consists of a rotating bearing comb 12 which is fixedly connected to the shaft 4 and which cooperates with a fixed load introduction body 13. The bearing comb 12 and the load introduction body 13 each have a running surface 14, between which a lubricating oil gap 15 of the axial bearing 3 is formed (FIG. 1). The load introduction body 13 is formed in one piece. It consists of a tread body 16 adjoining the bearing comb 12, a membrane 17 connected to the bearing flange 6 and a central ring 18 connecting the tread body 16 to the membrane 17 and is tapered from the tread body 16 to the central ring 18
An der dem Laufflachenkorper 16 abgewandten Seite des Lasteinleitungskorpers 13 ist ein Deckel 19 derart zwischen der Membran 17 und dem Lagerflansch 6 angeordnet, dass zwischen dem Deckel 19 und der Membran 17 ein Hohlraum 20 entsteht Im Deckel 19, der als ein den Hohlraum 20 begrenzendes Element ausgebildet ist, ist ein mit dem Hohlraum 20 verbundener, durch einen Stopfen 21 verschlossener Zufuhrkanal 22 für ein den Hohlraum 20 füllendes, mkompressibles Medium 23 angeordnet Als ein solches Medium 23 kommen hauptsächlich Fluide und insbesondere synthetische Ole in Frage Natürlich sind zu diesem Zweck auch andere Fluide, wie beispielsweise Wasser, aber auch feste Stoffe (z B niedrig schmelzende Metalle) geeignetOn the side of the load introduction body 13 facing away from the tread body 16, a cover 19 is arranged between the membrane 17 and the bearing flange 6 such that a cavity 20 is formed between the cover 19 and the membrane 17 in the cover 19, which acts as an element delimiting the cavity 20 a supply channel 22, which is connected to the cavity 20 and is closed by a stopper 21, is arranged for a mcompressible medium 23 which fills the cavity 20. As such a medium 23 mainly fluids and in particular synthetic oils come into question. Of course, others are also suitable for this purpose Fluids, such as water, but also solid substances (e.g. low-melting metals) are suitable
Der Deckel 19 besitzt einen in den Hohlraum 20 hineinragenden Axialanschlag 24 für den Zentralring 18 Die Membran 17 weist einen zentralen, an den Zentralring 18 anschliessenden Bereich 25, einen mit dem Lagerflansch 6 verbundenen Randbereich 26 sowie einen Zwischenbereich 27 auf (Fig 2) Sowohl der zentrale Bereich 25 als auch der Randbereich 26 sind gegenüber dem Zwischenbereich 27 der Membran 17 verdickt ausgebildet, so dass die eigentliche Membran vom Zwischenbereich 27 gebildet wirdThe cover 19 has an axial stop 24 protruding into the cavity 20 for the central ring 18. The membrane 17 has a central region 25 adjoining the central ring 18, an edge region 26 connected to the bearing flange 6 and an intermediate region 27 (FIG. 2) the central region 25 and the edge region 26 are thickened with respect to the intermediate region 27 of the membrane 17, so that the actual membrane is formed by the intermediate region 27
Der Lagerflansch 6 weist eine entsprechende Ausnehmung 28 zur Aufnahme des Lasteinleitungskorpers 13, d h für die Membran 17 auf Dazu ist im Bereich der Ausnehmung 28, zwischen dem Lagerflansch 6 und der Membran 17 eine Passung 29 ausgebildet, in welche der separat gefertigte Lasteinleitungskorper 13 eingepresst wird Ebenso kann auch eine stoffschlussige Verbindung von Lagerflansch 6 und Membran 17 erfolgen Eine weitere Passung 30 ist zwischen dem Deckel 19 und der Membran 17 ausgebildet, wobei die entsprechende Verbindung verschweisst ist Natürlich kann auch eine andere stoffschlussige Verbindung
(beispielsweise durch Verlöten) eine kraftschlussige oder eine formschlussige Verbindung realisiert werdenThe bearing flange 6 has a corresponding recess 28 for receiving the load introduction body 13, ie for the membrane 17. For this purpose, a fit 29 is formed in the region of the recess 28 between the bearing flange 6 and the membrane 17, into which the separately manufactured load introduction body 13 is pressed Likewise, a material connection between the bearing flange 6 and the membrane 17 can also take place. A further fit 30 is formed between the cover 19 and the membrane 17, the corresponding connection being welded. Of course, another material connection can also be made (for example, by soldering), a non-positive or a positive connection can be realized
Der separat gefertigte Lasteinleitungskorper 13 kann bereits vor seiner Montage in den Lagerflansch 6 mit dem Deckel 19 verbunden und der Hohlraum 20 mit dem inkompressiblen Medium 23 gefüllt werden, so dass eine einfache und kostengünstige Herstellung und Endmontage ermöglicht wird Durch Verwendung eines beschichteten Vergütungsstahls für den Lasteinleitungskorper 13 kann eine hohe Festigkeit erreicht werden Der im Hohlraum 20 befindliche Axialanschlag 24 verhindert, dass dιe"*axιale Steifigkeit des Axiallagers 3 im Falle des Verlustes des inkompressiblen Mediums 23 verlorengeht Diesem Sicherheitsgedanken kann durch Verwendung eines Materials mit guten Notlaufeigenschaften (z B Federbronze) für den Lasteinleitungskorper 13 weiter Rechnung getragen werdenThe separately manufactured load introduction body 13 can be connected to the cover 19 even before it is installed in the bearing flange 6, and the cavity 20 can be filled with the incompressible medium 23, so that simple and inexpensive manufacture and final assembly is made possible by using a coated tempering steel for the load introduction body 13 is a high strength can be achieved, the axial stop 24 in the cavity 20 prevents dιe "* axιale rigidity of the thrust bearing 3 in case of loss of the non-compressible medium 23 is lost this security thoughts, by using a material with good emergency running properties (for example spring bronze) for the load introduction body 13 are further taken into account
Beim Betrieb des Abgasturboladers ist der mit F1 bezeichnete Axialschub der Turbine zum Radialverdichter hin ausgerichtet und beaufschlagt das Axiallager 3 hauptsächlich in axialer Richtung Dabei werden die auftretenden Axialkrafte über den Lagerkamm 12, den Laufflachenkorper 16, den Zentralring 18 und die Membran 17 auf den Lagerflansch 6 übertragen Durch die lokalen Verdickungen der Membran 17 in ihrem zentralen Bereich 25 und im Randbereich 26, wird die eigentliche Kraftübertragung unterstutzt Dagegen wird die axiale Nachgiebigkeit der Membran 17 durch die Abstutzung auf dem inkompressiblen Medium 23 (z B Hy- draulikol) verhindert, so dass es lediglich zu geringen Einfederungen im Zehntel- bereich kommen kann Auch bei pulsierenden Axialkraften wirkt das inkompressi- ble Medium 23 als ein axialer Dampfer und kann somit einem Aufschaukeln der Axialkrafte, welches ansonsten bis hin zu einer Havarie fuhren konnte, entgegenwirken Die konstruktiv bzw betriebsbedingt entstehenden Schiefstellungen der Welle 4 und damit des Lagerkammes 12 des Axiallagers 3 werden über die axial sehr weiche Membran 17 ausgeglichen Damit kann die Schiefstellungssteifigkeit gegenüber den bekannten Losungen des Standes der Technik deutlich gesenkt und somit die Standzeit des Axiallagers 3 entsprechend erhöht werden
Das Schmieröl gelangt über die Schmierolzufuhrung 10, über eine im Lagergehause 5 angeordnete Umfangsnut 31 sowie über eine dementsprechend ausgebildete Zufuhrung 32 des Radiallagers 2 in dessen Schmierolspalt 33 Der Schmierolspalt 34 des Radiallagers 1 bzw die Laufflache 14 des Axiallagers 13 werden über die im Lagerflansch 6 angeordnete Schmierolzufuhrung 1 1 mit Schmieröl versorgtDuring operation of the exhaust gas turbocharger, the axial thrust of the turbine designated F1 is oriented toward the radial compressor and acts mainly on the axial bearing 3 in the axial direction. The axial forces that occur are transmitted via the bearing comb 12, the tread body 16, the central ring 18 and the membrane 17 to the bearing flange 6 The actual force transmission is supported by the local thickening of the membrane 17 in its central area 25 and in the edge area 26. On the other hand, the axial flexibility of the membrane 17 is prevented by the support on the incompressible medium 23 (for example hydraulic), so that only slight deflections in the tenths range can occur. Even with pulsating axial forces, the incompressible medium 23 acts as an axial steamer and can therefore counteract a build-up of the axial forces, which could otherwise lead to an accident, which arise due to the design or operation Shoot Positions of the shaft 4 and thus the bearing comb 12 of the thrust bearing 3 are compensated for by the axially very soft membrane 17. As a result, the misalignment stiffness can be significantly reduced compared to the known solutions of the prior art and the service life of the thrust bearing 3 can be increased accordingly The lubricating oil passes through the lubricating oil supply 10, via a circumferential groove 31 arranged in the bearing housing 5, and via a correspondingly designed supply 32 of the radial bearing 2 into its lubricating oil gap 33. The lubricating oil gap 34 of the radial bearing 1 or the running surface 14 of the axial bearing 13 are arranged in the bearing flange 6 Lubricating oil supply 1 1 supplied with lubricating oil
In einem zweiten Ausfuhrungsbeispiel wird der mit dem inkompressiblen Medium 23 gefüllte Hohlraum 20 zwischen der Membran 17 und dem Lagerflansch 6 ausgeformt, so dass letzerer das den Hohlraum 20 begrenzende Element bildet Daher ist der Zufuhrkanal 22 für das Medium 19 im Lagerflansch 6 angeordnet Ebenso ist statt dem Deckel 19 der Lagerflansch 6 mit dem Axialanschlag 24 für den Zentralring 18 der Membran 17 versehen (Fig 3) Durch den Wegfall des Deckels 19 kann bei nahezu analoger Funktion eine einfachere und damit kostengünstigere Konstruktion realisiertIn a second exemplary embodiment, the cavity 20 filled with the incompressible medium 23 is formed between the membrane 17 and the bearing flange 6, so that the latter forms the element delimiting the cavity 20. The feed channel 22 for the medium 19 is therefore arranged in the bearing flange 6 Provide the cover 19 of the bearing flange 6 with the axial stop 24 for the central ring 18 of the membrane 17 (FIG. 3). By eliminating the cover 19, a simpler and thus more cost-effective construction can be realized with an almost analogous function
BezugszeichenlisteReference list
1 Radiallager1 radial bearing
2 Radiallager2 radial bearings
3 Axiallager3 thrust bearings
4 Welle4 wave
5 Lagergehause5 warehouse
6 Lagerflansch, Element6 bearing flange, element
7 Befestigungselement, Schraube7 fastener, screw
8 Deckel8 lids
9 Befestigungselement, Schraube9 fastener, screw
10 Schmierolzufuhrung, in 510 lubricating oil supply, in 5
1 1 Schmierolzufuhrung, in 61 1 lubricating oil supply, in 6
12 Lagerkamm12 bearing comb
13 Lasteinleitungskorper13 load introduction body
14 Laufflache
Schmierolspalt14 tread Lube oil gap
LaufflächenkörperTread body
Membranmembrane
ZentralringCentral ring
Deckel, ElementCover, element
Hohlraumcavity
StopfenPlug
ZufuhrkanalFeed channel
Mediummedium
Axialanschlag zentraler Bereich, von 17Axial stop central area, from 17
Randbereich, von 17Border area, from 17th
Zwischenbereich, von 17Intermediate area, from 17th
AusnehmungRecess
Passung, zwischen 6 und 17Fit, between 6 and 17
Passung, zwischen 19 und 17Fit, between 19 and 17
UmfangsnutCircumferential groove
ZuführungFeed
Schmierölspalt, von 2Lube oil gap, from 2
Schmierölspalt, von 1
Lube oil gap, from 1
Claims
1. Axiallagerung für schnellaufende Rotoren, mit einer Einrichtung zur Schiefstellungskompensation und mit einem Axiallager, welches aus einem mit einer Welle (4) fest verbundenen, drehenden Lagerkamm (12) sowie aus einem feststehenden Lasteinleitungskorper (13) besteht, wobei der Lasteinleitungskorper (13) von einem Lagerflansch (6) aufgenommen wird, dadurch gekennzeichnet, dass der Lasteinleitungskorper (13) einen an den Lagerkamm (12) anschliessenden Laufflächenkörper (16), eine mit dem Lagerflansch (6) verbundene Membran (17) sowie einen den Laufflächenkörper (16) mit der Membran (17) verbindenden Zentralring (18) aufweist, wobei der Lasteinleitungskorper (13) vom Laufflächenkörper (16) zum Zentralring (18) verjüngt ausgebildet ist und wobei die Membran (17) einseitig auf einem inkompressiblen Medium (23) abgestützt ist, welches einen auf der dem Lagerkamm (12) abgewandten Seite der Membran (17) angeordneten Hohlraum (20) zwischen der Membran (17) und einem den Hohlraum (20) begrenzenden Element (19) füllt, wobei das den Hohlraum (20) begrenzende Element (19) entweder am Lagerflansch (6) abgestützt ist oder von letzterem gebildet wird.1. axial bearing for high-speed rotors, with a device for misalignment compensation and with an axial bearing, which consists of a shaft (4) fixedly connected, rotating bearing comb (12) and a fixed load introduction body (13), the load introduction body (13) is received by a bearing flange (6), characterized in that the load introduction body (13) has a tread body (16) adjoining the bearing crest (12), a membrane (17) connected to the bearing flange (6) and a tread body (16) having a central ring (18) connecting the membrane (17), the load introduction body (13) tapering from the tread body (16) to the central ring (18) and the membrane (17) being supported on one side on an incompressible medium (23), which has a cavity (20) arranged on the side of the membrane (17) facing away from the bearing comb (12) between the membrane (17) and a cavity (2 0) delimiting element (19), the element (19) delimiting the cavity (20) either being supported on the bearing flange (6) or being formed by the latter.
2. Axiallagerung nach Anspruch 1 , dadurch gekennzeichnet, dass der Lasteinleitungskorper (13) einstückig ausgebildet ist.2. Axial bearing according to claim 1, characterized in that the load introduction body (13) is integrally formed.
3. Axiallagerung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Membran (17) einen zentralen, an den Zentralring (18) anschliessenden Bereich (25), einen mit dem den Hohlraum (20) begrenzenden Element (19, 6) verbundenen Randbereich (26) sowie einen Zwischenbereich (27) aufweist und sowohl der zentrale Bereich (25) als auch der Randbereich (26) gegenüber dem Zwischenbereich (27) der Membran (17) verdickt ausgebildet sind. 3. Axial bearing according to claim 1 or 2, characterized in that the membrane (17) has a central region (25) adjoining the central ring (18), an edge region connected to the element (19, 6) delimiting the cavity (20) (26) and an intermediate region (27) and both the central region (25) and the edge region (26) are thickened relative to the intermediate region (27) of the membrane (17).
4. Axiallagerung nach Anspruch 3, dadurch gekennzeichnet, dass am den Hohlraum (20) begrenzenden Element (19, 6) ein in den Hohlraum (20) hineinragender Axialanschlag (24) für den Zentralring (18) angeordnet ist.4. Axial bearing according to claim 3, characterized in that on the cavity (20) delimiting element (19, 6) in the cavity (20) projecting axial stop (24) for the central ring (18) is arranged.
5. Axiallagerung nach Anspruch 4, dadurch gekennzeichnet, dass das den Hohlraum (20) begrenzende Element (19) als ein Deckel ausgebildet ist.5. Axial bearing according to claim 4, characterized in that the cavity (20) delimiting element (19) is designed as a cover.
6. Axiallagerung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das lnkompressible Medium (23) ein Fluid, vorzugsweise ein syntheti- sches Öl, ist.6. Axial bearing according to one of claims 1 to 5, characterized in that the incompressible medium (23) is a fluid, preferably a synthetic oil.
7. Axiallagerung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Lasteinleitungskorper (13) aus einem Vergütungsstahl mit guter Wechselfestigkeit besteht.7. Axial bearing according to one of claims 1 to 5, characterized in that the load introduction body (13) consists of a tempered steel with good fatigue strength.
8. Axiallagerung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Lasteinleitungskorper (13) aus einer Bronze mit hoher Festigkeit und guten Notlaufeigenschaften besteht. 8. Axial bearing according to one of claims 1 to 5, characterized in that the load introduction body (13) consists of a bronze with high strength and good emergency running properties.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19860783 | 1998-12-30 | ||
DE19860783A DE19860783A1 (en) | 1998-12-30 | 1998-12-30 | Axial bearing for high-speed rotors |
PCT/CH1999/000616 WO2000040870A1 (en) | 1998-12-30 | 1999-12-21 | Axial bearing for high-speed rotors |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1141564A1 true EP1141564A1 (en) | 2001-10-10 |
Family
ID=7893157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99973582A Withdrawn EP1141564A1 (en) | 1998-12-30 | 1999-12-21 | Axial bearing for high-speed rotors |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1141564A1 (en) |
JP (1) | JP2002534647A (en) |
DE (1) | DE19860783A1 (en) |
TW (1) | TW418291B (en) |
WO (1) | WO2000040870A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016119682A1 (en) * | 2016-10-14 | 2018-04-19 | Abb Turbo Systems Ag | Thrust bearing arrangement for turbocharger |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH422437A (en) * | 1964-08-19 | 1966-10-15 | Escher Wyss Ag | Shaft bearing for a rotor sliding on the bearing segments that adjust themselves |
SE325755B (en) * | 1967-08-10 | 1970-07-06 | Skf Svenska Kullagerfab Ab | |
DE2052079A1 (en) * | 1970-10-23 | 1972-04-27 | Motoren Turbinen Union | Axial plain bearings for high-speed shafts |
DE2357881A1 (en) * | 1973-11-16 | 1975-05-22 | Mannesmann Meer Ag | HYDRAULICALLY FEEDED THRUST BEARING |
DE2604889A1 (en) * | 1976-02-07 | 1977-08-11 | Polysius Ag | HYDROSTATIC BEARING POINT AS WELL AS HYDROSTATIC BEARING POINT WITH SEVERAL SUCH POINTING POINTS |
DE2805711A1 (en) * | 1978-02-10 | 1979-08-16 | Polysius Ag | HYDROSTATIC WAREHOUSE |
CH631523A5 (en) * | 1978-09-14 | 1982-08-13 | Bbc Brown Boveri & Cie | CHAMBER BEARING. |
US4288128A (en) * | 1979-10-01 | 1981-09-08 | Caterpillar Tractor Co. | Self-aligning thrust bearing |
FR2547878B1 (en) * | 1983-06-27 | 1985-10-25 | Alsthom Atlantique | AXIAL SUPPORT DEVICE FOR A SHAFT WITH RIGID SLIDING RINGS |
FR2576647B1 (en) * | 1985-01-28 | 1990-08-10 | Europ Propulsion | BEARING, ESPECIALLY FOR A ROTATING SHAFT |
US5620260A (en) * | 1987-05-29 | 1997-04-15 | Ide; Russell D. | Variable characteristic thrust bearing |
US5531522A (en) * | 1987-05-29 | 1996-07-02 | Kmc, Inc. | Fluid dampened support having variable stiffness and damping |
CH675283A5 (en) * | 1988-03-25 | 1990-09-14 | Asea Brown Boveri | |
JPH0216820U (en) * | 1988-07-19 | 1990-02-02 | ||
EP0757186B1 (en) * | 1995-08-02 | 2003-09-03 | Renk Aktiengesellschaft | Sliding pad with a compression spring for a plain bearing |
-
1998
- 1998-12-30 DE DE19860783A patent/DE19860783A1/en not_active Withdrawn
-
1999
- 1999-12-21 WO PCT/CH1999/000616 patent/WO2000040870A1/en not_active Application Discontinuation
- 1999-12-21 EP EP99973582A patent/EP1141564A1/en not_active Withdrawn
- 1999-12-21 JP JP2000592547A patent/JP2002534647A/en active Pending
- 1999-12-23 TW TW088122765A patent/TW418291B/en not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO0040870A1 * |
Also Published As
Publication number | Publication date |
---|---|
TW418291B (en) | 2001-01-11 |
JP2002534647A (en) | 2002-10-15 |
WO2000040870A1 (en) | 2000-07-13 |
DE19860783A1 (en) | 2000-07-20 |
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