EP1777417B1 - Turbocharger - Google Patents

Turbocharger Download PDF

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Publication number
EP1777417B1
EP1777417B1 EP05023173A EP05023173A EP1777417B1 EP 1777417 B1 EP1777417 B1 EP 1777417B1 EP 05023173 A EP05023173 A EP 05023173A EP 05023173 A EP05023173 A EP 05023173A EP 1777417 B1 EP1777417 B1 EP 1777417B1
Authority
EP
European Patent Office
Prior art keywords
bearing housing
sealing ring
turbocharger
sealing
end faces
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.)
Active
Application number
EP05023173A
Other languages
German (de)
French (fr)
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EP1777417A1 (en
Inventor
Dirk Frankenstein
Markus Schwerdtfeger
Bruno Ferling
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kaco GmbH and Co KG
BorgWarner Inc
Original Assignee
Kaco GmbH and Co KG
BorgWarner Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kaco GmbH and Co KG, BorgWarner Inc filed Critical Kaco GmbH and Co KG
Priority to EP05023173A priority Critical patent/EP1777417B1/en
Priority to DE502005004418T priority patent/DE502005004418D1/en
Priority to JP2008536947A priority patent/JP5106406B2/en
Priority to PCT/EP2006/004908 priority patent/WO2007048451A1/en
Priority to US12/091,123 priority patent/US8096774B2/en
Publication of EP1777417A1 publication Critical patent/EP1777417A1/en
Application granted granted Critical
Publication of EP1777417B1 publication Critical patent/EP1777417B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic

Definitions

  • the invention relates to a turbocharger according to the preamble of claim 1.
  • Such a turbocharger is for example from the US 4,420,160 known.
  • This turbocharger has a sealing device for sealing a bearing housing oil space with respect to a compressor chamber, which is provided with a sealing ring which is fixedly mounted in the bearing housing.
  • the sealing ring has frontal sealing surfaces, which bear against rotating mating surfaces to build up the sealing effect. Since a mechanical contact between the end faces of the sealing ring and the opposite with the compressor shaft rotating counter surfaces is thus required to build a sealing effect, mechanical wear and thus deterioration of the sealing effect, at least after a certain period of turbocharger inevitable.
  • an engine blower unit having a housing of an electric motor wherein a number of substantially axial bores extend through a scar of the blower impeller between a recess thereof and a low pressure portion.
  • turbocharger specified in the preamble of claim 1 way, which is provided with a sealing device, the at least significantly longer life reduced wear of the sealing surfaces and thus makes a better sealing effect possible.
  • the turbocharger according to the invention has in detail a sealing device, which has a sealing ring for sealing the bearing housing oil space with respect to the compressor chamber.
  • This sealing ring is arranged in the bearing housing and is provided with two end faces, which are used to construct the Sealing effect are provided with associated end faces of a disc on one side and a sealing bushing on another side, wherein the disc and the sealing bushing are mounted on the rotor shaft.
  • the sealing ring characterized in that the sealing ring is arranged with axial clearance on the rotor shaft between the disc and the sealing bush, the sealing ring usually places during assembly on one of the two end faces (ie either to the end face of the disc or to that of the sealing bushing).
  • the sealing ring separates from the contact position and forms depending on the existing pressure difference between the compressor and bearing housing side with the respective associated end face a conveying gap. It arises mainly through the conveyor, which forms the conveying gap with the respectively associated end face of the sealing ring, an air flow, which leads to the construction of air cushions between each of the non-rotating fixed end faces of the sealing ring and the associated rotating end faces of the disc or the sealing bushing.
  • this air flow prevents oil from flowing out of the bearing housing in the direction of the compressor and, on the other hand, direct mechanical contact between the end surfaces causing the seal is avoided, which at least considerably reduces the wear of the turbocharger according to the invention.
  • the mentioned air flow is achieved by the arranged in the two end faces of the sealing ring conveyors or conveyor structures which are oppositely oriented, which means that substantially either the compressor side conveyor promotes air from the outer periphery to the inner circumference, or the bearing housing side conveyor an air delivery from inner circumference to the outer periphery causes.
  • the air is directed into an axial gap between the inner circumference of the sealing ring and the sealing bush and can thus reach the bearing housing side from the compressor side. This creates an approximately U-shaped forced air flow, which, as said, the sealing effect and the avoidance of mechanical contact between the opposing fixed and rotating faces achieved.
  • the sealing device according to the invention is defined as an independently tradeable object.
  • a part of a turbocharger 15 according to the invention is shown, which has a bearing housing 7, which supports a rotor shaft 12 and which is connected to a compressor housing, of which only the compressor chamber 14 is visible.
  • the turbocharger has, as usual, a turbine with a turbine housing, which, however, as well as the entire compressor side, in Fig. 1 not shown, since these parts are not required for the explanation of the present invention.
  • Fig. 1 further shows a sealing device, which is illustrated in its entirety by the reference numeral 20.
  • the sealing device 20 is used to seal a bearing housing oil chamber 13 with respect to the compressor chamber 14 of the compressor housing of the turbocharger 15, not shown.
  • the sealing device 20 has a sealing ring 1 which is stationary, ie not rotating, arranged in the bearing housing 7 and has two end faces 17 and 17 '. These end faces 17 and 17 'act to build up the sealing effect of the sealing device 20 with end faces 10 and 11 of a disc 9 and a sealing bushing 16 together.
  • Fig. 1 illustrates here that the disc 9 is disposed adjacent to the compressor chamber 14, and that the sealing bush 16 has two flanges 16A and 16B, which according to the in Fig. 1 chosen representation arranged right from the sealing ring 1 and spaced from each other.
  • the flanges 16A and 16B guide a thrust bearing 21.
  • the flange 16A, together with the disc 9, further defines a groove in which the sealing ring 1 is inserted with axial clearance, that is, play in the longitudinal direction of the rotor shaft 12.
  • conveyors 2 and 3 are arranged, wherein the conveyor 2 is the compressor side, while on the bearing housing side 3, the conveyor 3 is arranged.
  • These conveyors are from the FIGS. 2 and 3 seen. They are formed in the example of by webs 18 and 18 'limited grooves 19 and 19', which are oppositely oriented, which means that the compressor-side conveyor 2 promotes air from the outer periphery to the inner periphery, while the bearing housing side conveyor 3 air from inner circumference promotes the outer circumference.
  • the sealing ring 1 is floatingly mounted in the bearing housing 7 for this purpose. At the in Fig. 1 illustrated particularly preferred embodiment, the sealing ring 1 is connected to an end portion 5A of an elastomeric molded part 5, which is fixed with its other end portion 5B in the bearing housing 7.
  • connection between the sealing ring and the end region 5 A can be designed positively, non-positively or frictionally. A combination of these types of connections is possible.
  • Fig. 1 further clarifies that the end portion 5 A is pressed by a first locking ring 4 to the sealing ring 1.
  • the other end portion 5B of the elastomeric molded part 5 is fixed by a second locking ring 6 in a bore of the bearing housing 7 or in an attachment 8, which is a kind of cover with which the opening of the bearing housing 7 is closed, as can be seen in detail from the graphic representation of the Fig. 1 opens.
  • the above-described sealing device 20 seals the bearing housing oil chamber 13 from the compressor chamber 14.
  • the sealing function is achieved here by the sealing ring 1, which is disposed between the simultaneously rotating end faces 10 and 11 of the disc 9 and the annular flange 16A.
  • the sealing ring 1 usually sets to one of the two said end faces 10 and 11 at.
  • an air cushion between the fixed end face 17 of the sealing ring 1 and the rotating end face 11 constructed or the air cushion is through the Conveying effect between the fixed end face 17 'and the rotating end face 10 is formed.
  • the conveyors or conveyor structures 2 and 3 an air flow in the direction of the bearing housing oil space 13, which prevents ⁇ 1 from flowing from the bearing housing 7 in the direction of the compressor.
  • the locking ring 4 which presses the elastomeric molded part 5 to the sealing ring 1, can be additionally used by appropriate design (recesses, tabs, cams, etc.) for the positive torque transmission between the sealing ring 1 and the bearing housing 7.

Description

Die Erfindung betrifft einen Turbolader gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a turbocharger according to the preamble of claim 1.

Ein derartiger Turbolader ist beispielsweise aus der US 4,420,160 bekannt.Such a turbocharger is for example from the US 4,420,160 known.

Dieser Turbolader weist eine Dichtungseinrichtung zur Abdichtung eines Lagergehäuseölraumes gegenüber einem Verdichterraum auf, die mit einem Dichtring versehen ist, der im Lagergehäuse feststehend montiert ist. Der Dichtring weist stirnseitige Dichtflächen auf, die an rotierenden Gegenflächen zum Aufbau der Dichtwirkung anliegen. Da somit zum Aufbau einer Dichtwirkung eine mechanische Anlage zwischen den Stirnseiten des Dichtringes und den gegenüberliegenden mit der Verdichterwelle rotierenden Gegenflächen erforderlich ist, ist ein mechanischer Verschleiß und damit eine Verschlechterung der Dichtwirkung zumindestens nach gewisser Laufzeit des Turboladers unvermeidlich.This turbocharger has a sealing device for sealing a bearing housing oil space with respect to a compressor chamber, which is provided with a sealing ring which is fixedly mounted in the bearing housing. The sealing ring has frontal sealing surfaces, which bear against rotating mating surfaces to build up the sealing effect. Since a mechanical contact between the end faces of the sealing ring and the opposite with the compressor shaft rotating counter surfaces is thus required to build a sealing effect, mechanical wear and thus deterioration of the sealing effect, at least after a certain period of turbocharger inevitable.

Aus der GB 12 10 388 A ist eine Motorgebläseeinheit mit einem Gehäuse eines Elektromotors bekannt, wobei sich eine Anzahl von im Wesentlichen axialen Bohrungen durch eine Narbe des Gebläse-Impellers zwischen einer Ausnehmung derselben und einem Niedrigdruckabschnitt erstreckt.From the GB 12 10 388 A For example, an engine blower unit having a housing of an electric motor is known, wherein a number of substantially axial bores extend through a scar of the blower impeller between a recess thereof and a low pressure portion.

Aus der US 4 986 733 A ist ferner ein Verdichterrad für einen Turbolader bekannt, das mit einer bohrungslosen Narbe versehen ist, um die Lebensdauer des Verdichterrades zu verbessern.From the US 4 986 733 A Further, a compressor wheel for a turbocharger is known, which is provided with a bore without a scar, in order to improve the life of the compressor wheel.

Es ist daher Aufgabe der vorliegenden Erfindung, einen Turbolader der im Oberbegriff des Anspruches 1 angegeben Art zu schaffen, der mit einer Dichtungseinrichtung versehen ist, die eine höhere Lebensdauer aufgrund zumindestens deutlich verringerten Verschleißes der Dichtflächen und damit eine bessere Dichtwirkung möglich macht.It is therefore an object of the present invention to provide a turbocharger specified in the preamble of claim 1 way, which is provided with a sealing device, the at least significantly longer life reduced wear of the sealing surfaces and thus makes a better sealing effect possible.

Die Lösung dieser Aufgabe erfolgt durch die Merkmale des Anspruches 1 bzw. des Anspruches 10.The solution of this object is achieved by the features of claim 1 and of claim 10.

Der erfindungsgemäße Turbolader weist im Einzelnen eine Dichtungseinrichtung auf, die zur Abdichtung des Lagergehäuseölraumes gegenüber dem Verdichterraum einen Dichtring aufweist. Dieser Dichtring ist im Lagergehäuse angeordnet und ist mit zwei Stirnflächen versehen, die zum Aufbau der Dichtwirkung mit zugeordneten Stirnflächen einer Scheibe auf einer Seite und einer Dichtungsbuchse auf einer anderen Seite versehen sind, wobei die Scheibe und die Dichtungsbuchse auf der Läuferwelle befestigt sind.The turbocharger according to the invention has in detail a sealing device, which has a sealing ring for sealing the bearing housing oil space with respect to the compressor chamber. This sealing ring is arranged in the bearing housing and is provided with two end faces, which are used to construct the Sealing effect are provided with associated end faces of a disc on one side and a sealing bushing on another side, wherein the disc and the sealing bushing are mounted on the rotor shaft.

Dadurch dass der Dichtring mit axialem Spiel auf der Läuferwelle zwischen der Scheibe und der Dichtungsbuchse angeordnet ist, legt sich der Dichtring bei der Montage üblicherweise an eine der beiden Stirnflächen (also entweder an die Stirnfläche der Scheibe oder an diejenige der Dichtungsbuchse) an. Beim Betrieb des Turboladers löst sich der Dichtring aus der Anlagestellung und bildet je nach vorliegender Druckdifferenz zwischen Verdichter- und Lagergehäuseseite mit der jeweiligen zugeordneten Stirnseite einen Förderspalt. Es entsteht hauptsächlich durch die Fördereinrichtung, die mit der jeweils zugeordneten Stirnfläche des Dichtringes den Förderspalt bildet, eine Luftströmung, die zum Aufbau von Luftpolstern zwischen jeder der nicht rotierenden feststehenden Stirnflächen des Dichtringes und den zugeordneten rotierenden Stirnflächen der Scheibe bzw. der Dichtungsbuchse führt. Durch diese Luftströmung wird zum einen verhindert, dass Öl aus dem Lagergehäuse in Richtung Verdichter fließt und zum anderen wird ein direkter mechanischer Kontakt zwischen den die Dichtung bewirkenden Stirnflächen vermieden, was den Verschleiß des erfindungsgemäßen Turboladers zumindestens erheblich reduziert.Characterized in that the sealing ring is arranged with axial clearance on the rotor shaft between the disc and the sealing bush, the sealing ring usually places during assembly on one of the two end faces (ie either to the end face of the disc or to that of the sealing bushing). During operation of the turbocharger, the sealing ring separates from the contact position and forms depending on the existing pressure difference between the compressor and bearing housing side with the respective associated end face a conveying gap. It arises mainly through the conveyor, which forms the conveying gap with the respectively associated end face of the sealing ring, an air flow, which leads to the construction of air cushions between each of the non-rotating fixed end faces of the sealing ring and the associated rotating end faces of the disc or the sealing bushing. On the one hand, this air flow prevents oil from flowing out of the bearing housing in the direction of the compressor and, on the other hand, direct mechanical contact between the end surfaces causing the seal is avoided, which at least considerably reduces the wear of the turbocharger according to the invention.

Die erwähnte Luftströmung wird durch die in den beiden Stirnflächen des Dichtrings angeordneten Fördereinrichtungen bzw. Förderstrukturen erreicht, welche entgegengesetzt ausgerichtet sind, was bedeutet, dass im Wesentlichen entweder die verdichterseitige Fördereinrichtung Luft vom äußeren Umfang zum inneren Umfang fördert, oder die lagergehäuseseitige Fördereinrichtung eine Luftförderung vom inneren Umfang zum äußeren Umfang bewirkt. Im Einzelnen bedeutet dies, dass die verdichterseitige Fördereinrichtung mit kleiner werdendem Spalt die Luft vom Verdichtergehäuse von radial außen nach radial innen pumpt oder die lagergehäuseseitige Fördereinrichtung mit kleiner werdendem Spalt die Luft von innen nach radial außen leitet. In beiden Fällen wird die Luft in einen axialen Spalt zwischen dem Innenumfang des Dichtringes und der Dichtungsbuchse geleitet und kann somit von der Verdichterseite zur Lagergehäuseseite gelangen. Hierdurch entsteht eine in etwa U-förmige erzwungene Luftströmung, die wie gesagt, die Dichtwirkung und die Vermeidung einer mechanischen Anlage zwischen den einander gegenüberstehenden festen und rotierenden Stirnflächen erzielt.The mentioned air flow is achieved by the arranged in the two end faces of the sealing ring conveyors or conveyor structures which are oppositely oriented, which means that substantially either the compressor side conveyor promotes air from the outer periphery to the inner circumference, or the bearing housing side conveyor an air delivery from inner circumference to the outer periphery causes. In detail, this means that the compressor-side conveyor with decreasing Gap pumps the air from the compressor housing from radially outside to radially inside or the bearing housing side conveyor with decreasing gap passes the air from the inside to the outside radially. In both cases, the air is directed into an axial gap between the inner circumference of the sealing ring and the sealing bush and can thus reach the bearing housing side from the compressor side. This creates an approximately U-shaped forced air flow, which, as said, the sealing effect and the avoidance of mechanical contact between the opposing fixed and rotating faces achieved.

Die Unteransprüche 2 bis 9 haben vorteilhafte Weiterbildungen des erfindungsgemäßen Turboladers zum Inhalt.The dependent claims 2 to 9 have advantageous developments of the turbocharger invention to the content.

In den Ansprüchen 10 und 11 ist die erfindungsgemäße Dichtungseinrichtung als selbständig handelbares Objekt definiert.In claims 10 and 11, the sealing device according to the invention is defined as an independently tradeable object.

Weitere Einzelheiten, Merkmale und Vorteile der Erfindung ergeben sich aus nachfolgender Beschreibung von Ausführungsbeispielen anhand der Zeichnung.Further details, features and advantages of the invention will become apparent from the following description of exemplary embodiments with reference to the drawing.

Es zeigt:

Fig. 1
eine schematisch vereinfachte Darstellung eines erfindungsgemäßen Turboladers,
Fig. 2
eine Draufsicht auf den Dichtring von der Lagergehäuseseite her, und
Fig. 3
eine der Fig. 2 entsprechende Darstellung des Dichtrings der erfindungsgemäßen Dichtungseinrichtung von der Verdichterseite her.
It shows:
Fig. 1
a schematically simplified representation of a turbocharger according to the invention,
Fig. 2
a plan view of the sealing ring from the bearing housing side, and
Fig. 3
one of the Fig. 2 corresponding representation of the sealing ring of the sealing device according to the invention from the compressor side.

In Fig. 1 ist ein Teil eines erfindungsgemäßen Turboladers 15 dargestellt, der ein Lagergehäuse 7 aufweist, das eine Läuferwelle 12 lagert und das mit einem Verdichtergehäuse verbunden ist, von dem lediglich der Verdichterraum 14 sichtbar ist. Der Turbolader weist natürlich wie üblich auch eine Turbine mit einem Turbinengehäuse auf, was jedoch, wie ebenfalls die komplette Verdichterseite, in Fig. 1 nicht dargestellt ist, da diese Teile für die Erläuterung vorliegender Erfindung nicht erforderlich sind.In Fig. 1 a part of a turbocharger 15 according to the invention is shown, which has a bearing housing 7, which supports a rotor shaft 12 and which is connected to a compressor housing, of which only the compressor chamber 14 is visible. Of course, the turbocharger has, as usual, a turbine with a turbine housing, which, however, as well as the entire compressor side, in Fig. 1 not shown, since these parts are not required for the explanation of the present invention.

Fig. 1 zeigt ferner eine Dichtungseinrichtung, die in ihrer Gesamtheit mit der Bezugsziffer 20 verdeutlicht ist. Die Dichtungseinrichtung 20 dient zur Abdichtung eines Lagergehäuseölraumes 13 gegenüber dem Verdichterraum 14 des nicht näher dargestellten Verdichtergehäuses des Turboladers 15. Fig. 1 further shows a sealing device, which is illustrated in its entirety by the reference numeral 20. The sealing device 20 is used to seal a bearing housing oil chamber 13 with respect to the compressor chamber 14 of the compressor housing of the turbocharger 15, not shown.

Die Dichtungseinrichtung 20 weist hierfür einen Dichtring 1 auf, der feststehend, d.h. nicht rotierend, im Lagergehäuse 7 angeordnet ist und zwei Stirnflächen 17 und 17' aufweist. Diese Stirnflächen 17 und 17' wirken zum Aufbau der Dichtwirkung der Dichtungseinrichtung 20 mit Stirnflächen 10 bzw. 11 einer Scheibe 9 bzw. einer Dichtungsbuchse 16 zusammen. Fig. 1 verdeutlicht hierbei, dass die Scheibe 9 benachbart zum Verdichterraum 14 angeordnet ist, und dass die Dichtungsbuchse 16 zwei Flansche 16A und 16B aufweist, die gemäß der in Fig. 1 gewählten Darstellung rechts vom Dichtring 1 angeordnet und beabstandet zueinander sind.For this purpose, the sealing device 20 has a sealing ring 1 which is stationary, ie not rotating, arranged in the bearing housing 7 and has two end faces 17 and 17 '. These end faces 17 and 17 'act to build up the sealing effect of the sealing device 20 with end faces 10 and 11 of a disc 9 and a sealing bushing 16 together. Fig. 1 illustrates here that the disc 9 is disposed adjacent to the compressor chamber 14, and that the sealing bush 16 has two flanges 16A and 16B, which according to the in Fig. 1 chosen representation arranged right from the sealing ring 1 and spaced from each other.

Die Flansche 16A und 16B führen ein Axiallager 21. Der Flansch 16A begrenzt zusammen mit der Scheibe 9 ferner eine Nut, in der der Dichtring 1 mit axialem Spiel, also mit Spiel in der Längsrichtung der Läuferwelle 12 eingesetzt ist.The flanges 16A and 16B guide a thrust bearing 21. The flange 16A, together with the disc 9, further defines a groove in which the sealing ring 1 is inserted with axial clearance, that is, play in the longitudinal direction of the rotor shaft 12.

Innerhalb der von der Scheibe 9 und dem Flansch 16A begrenzten Nut ist der Dichtring 1 ebenfalls mit einem einen Ringspalt bildenden radialen Spiel S eingesetzt.Within the limited by the disc 9 and the flange 16A groove of the sealing ring 1 is also used with an annular gap forming radial clearance S.

In den Stirnflächen 17 und 17' des Dichtringes 1 sind Fördereinrichtungen 2 bzw. 3 angeordnet, wobei die Fördereinrichtung 2 die verdichterseitige ist, während auf der Lagergehäuseseite 3 die Fördereinrichtung 3 angeordnet ist. Diese Fördereinrichtungen sind aus der Fig. 2 und 3 ersichtlich. Sie werden im Beispielsfalle von durch Stege 18 bzw. 18' begrenzte Nuten 19 bzw. 19' gebildet, die entgegengesetzt ausgerichtet sind, was bedeutet, dass die verdichterseitige Fördereinrichtung 2 Luft vom äußeren Umfang zum inneren Umfang fördert, während die lagergehäuseseitige Fördereinrichtung 3 Luft vom inneren Umfang zum äußeren Umfang fördert.In the end faces 17 and 17 'of the sealing ring 1 conveyors 2 and 3 are arranged, wherein the conveyor 2 is the compressor side, while on the bearing housing side 3, the conveyor 3 is arranged. These conveyors are from the FIGS. 2 and 3 seen. They are formed in the example of by webs 18 and 18 'limited grooves 19 and 19', which are oppositely oriented, which means that the compressor-side conveyor 2 promotes air from the outer periphery to the inner periphery, while the bearing housing side conveyor 3 air from inner circumference promotes the outer circumference.

Der Dichtring 1 ist hierzu schwimmend im Lagergehäuse 7 gelagert. Bei der in Fig. 1 dargestellten besonders bevorzugten Ausführungsform ist der Dichtring 1 mit einem Endbereich 5A eines Elastomerformteils 5 verbunden, das mit seinem anderen Endbereich 5B im Lagergehäuse 7 fixiert ist.The sealing ring 1 is floatingly mounted in the bearing housing 7 for this purpose. At the in Fig. 1 illustrated particularly preferred embodiment, the sealing ring 1 is connected to an end portion 5A of an elastomeric molded part 5, which is fixed with its other end portion 5B in the bearing housing 7.

Die Verbindung zwischen dem Dichtring und dem Endbereich 5A kann form-, kraft- oder reibschlüssig ausgeführt sein. Auch eine Kombination dieser Verbindungsarten ist möglich.The connection between the sealing ring and the end region 5 A can be designed positively, non-positively or frictionally. A combination of these types of connections is possible.

Fig. 1 verdeutlicht ferner, dass der Endbereich 5A durch einen ersten Sicherungsring 4 an den Dichtring 1 angepresst wird. Fig. 1 further clarifies that the end portion 5 A is pressed by a first locking ring 4 to the sealing ring 1.

Der andere Endbereich 5B des Elastomerformteils 5 wird durch einen zweiten Sicherungsring 6 in einer Bohrung des Lagergehäuses 7 bzw. in einem Anbauteil 8 fixiert, das eine Art Deckel darstellt, mit dem die Öffnung des Lagergehäuses 7 verschließbar ist, wie sich dies im Einzelnen aus der zeichnerischen Darstellung der Fig. 1 erschließt.The other end portion 5B of the elastomeric molded part 5 is fixed by a second locking ring 6 in a bore of the bearing housing 7 or in an attachment 8, which is a kind of cover with which the opening of the bearing housing 7 is closed, as can be seen in detail from the graphic representation of the Fig. 1 opens.

Die zuvor erläuterte Dichtungseinrichtung 20 dichtet den Lagergehäuseölraum 13 gegenüber dem Verdichterraum 14 ab. Die Dichtfunktion wird hierbei durch den Dichtring 1 erzielt, welcher zwischen den gleichzeitig rotierenden Stirnflächen 10 bzw. 11 der Scheibe 9 bzw. des Ringflansches 16A angeordnet ist. Bei der Montage legt sich der Dichtring 1 üblicherweise an eine der beiden besagten Stirnflächen 10 bzw. 11 an. Bei Betrieb des Turboladers wird je nach Druckdifferenz zwischen Verdichter- und Lagergehäuseseite durch die im Förderspalt von der jeweiligen Fördereinrichtung 2 bzw. 3 erzeugte Strömung ein Luftpolster zwischen der feststehenden Stirnfläche 17 des Dichtringes 1 und der rotierenden Stirnfläche 11 aufgebaut bzw. das Luftpolster wird durch die Förderwirkung zwischen feststehender Stirnfläche 17' und der rotierenden Stirnfläche 10 gebildet. Durch die Fördereinrichtungen bzw. Förderstrukturen 2 bzw. 3 entsteht eine Luftströmung in Richtung auf den Lagergehäuseölraum 13, was Ö1 daran hindert, aus dem Lagergehäuse 7 in Richtung Verdichter zu fließen.The above-described sealing device 20 seals the bearing housing oil chamber 13 from the compressor chamber 14. The sealing function is achieved here by the sealing ring 1, which is disposed between the simultaneously rotating end faces 10 and 11 of the disc 9 and the annular flange 16A. During assembly, the sealing ring 1 usually sets to one of the two said end faces 10 and 11 at. During operation of the turbocharger, depending on the pressure difference between compressor and bearing housing side through the flow generated in the conveying gap of the respective conveyor 2 and 3, an air cushion between the fixed end face 17 of the sealing ring 1 and the rotating end face 11 constructed or the air cushion is through the Conveying effect between the fixed end face 17 'and the rotating end face 10 is formed. By the conveyors or conveyor structures 2 and 3, an air flow in the direction of the bearing housing oil space 13, which prevents Ö1 from flowing from the bearing housing 7 in the direction of the compressor.

Genauer gesagt entsteht durch die Fördereinrichtung 2 eine Luftströmung vom Verdichtergehäuse 7 von radial außen nach radial innen. Danach wird die Luft in den axialen Spalt S eingeleitet und im Bereich des Ringflansches 16a von innen nach außen geleitet, so dass sich eine erzwungene Luftströmung ergibt, die in etwa U-förmig ist.More precisely, by the conveyor 2, an air flow from the compressor housing 7 from radially outside to radially inside. Thereafter, the air is introduced into the axial gap S and guided in the region of the annular flange 16 a from the inside outward, so that there is a forced air flow, which is approximately U-shaped.

Hierdurch wird, wie zuvor erläutert, ein Austreten von Öl Richtung Verdichter verhindert und zum anderen wird eine mechanische Anlage der feststehenden Stirnflächen 17 bzw. 17' des Dichtringes 1 an den gegenüberstehenden rotierenden Dichtflächen des Läuferwellenverbundes, der von der Läuferwelle 12, der Scheibe 9 und Dichtungsbuchse 16 gebildet wird, vermieden.As a result, as previously explained, leakage of oil toward the compressor is prevented and, secondly, mechanical engagement of the stationary end faces 17 or 17 'of the sealing ring 1 against the opposing rotating sealing surfaces of the rotor shaft assembly, that of the rotor shaft 12, the disk 9 and Sealing bush 16 is formed, avoided.

Der Sicherungsring 4, der das Elastomerformteil 5 an den Dichtring 1 anpresst, kann zusätzlich durch entsprechenden Gestaltung (Aussparungen, Laschen, Nocken usw.) zur formschlüssigen Drehmomentübertragung zwischen dem Dichtring 1 und dem Lagergehäuse 7 verwendet werden.The locking ring 4, which presses the elastomeric molded part 5 to the sealing ring 1, can be additionally used by appropriate design (recesses, tabs, cams, etc.) for the positive torque transmission between the sealing ring 1 and the bearing housing 7.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Dichtringseal
2,32.3
Fördereinrichtungen/FörderstrukturenConveyors / support structures
44
Erster SicherungsringFirst circlip
55
ElastomerformteilElastomer molding
5A, 5B5A, 5B
Endbereicheend regions
66
Zweiter SicherungsringSecond circlip
77
Lagergehäusebearing housing
88th
Anbauteil/DeckelAttachment / cap
99
Scheibedisc
10,1110.11
Gleichzeitig rotierende StirnflächenAt the same time rotating faces
1212
Läuferwelle/LäuferverbundRotor shaft / stretching bond
1313
LagergehäuseölraumBearing housing oil space
1414
Verdichterraumcompressor room
1515
Teil eines TurboladersPart of a turbocharger
1616
Dichtungsbuchsesealing bush
16A, 16B16A, 16B
Flanscheflanges
17, 17'17, 17 '
Stirnflächen von 1End faces of 1
18, 18'18, 18 '
Stege/LuftleitstegeStege / air guide bars
19,19'19.19 '
Nuten/LuftleitnutenGrooves / air conduction
2020
Dichtungseinrichtungseal means
SS
Spiel zwischen 1 und 16Game between 1 and 16

Claims (11)

  1. Turbocharger (15),
    - with a bearing housing (7) which supports a rotor shaft (12) and has a bearing housing oil chamber (13);
    - with a compressor casing which is connected to the bearing housing (7) and has a compressor chamber (14); and
    - with a sealing device (20) which is provided for sealing the bearing housing oil chamber (13) in relation to the compressor chamber (14) and which has a sealing ring (1) which is arranged in the bearing housing (7) and has two end faces (17, 17') which interact with associated end faces (10 or 11, as the case may be) of a disc (9) or of a packing sleeve (16), as the case may be, which are fastened on the rotor shaft (12),
    characterized in that
    - the sealing ring (1) is arranged with an axial clearance on the rotor shaft (12) between the disc (9) and the packing sleeve (16); and
    - oppositely orientated air feed devices (2, 3) are arranged in or on the end faces (17, 17') of the sealing ring (1).
  2. Turbocharger according to Claim 1, characterized in that the disc (9) and the packing sleeve (16) define a slot in which the sealing ring (1) is arranged.
  3. Turbocharger according to Claim 1 or 2, characterized in that the sealing ring (1) is supported in the bearing housing (7) in a floating manner.
  4. Turbocharger according to Claim 3, characterized in that the sealing ring (1) is connected to an end region (5A) of an elastomer moulded part (5) which by its other end region (5B) is fixable in the bearing housing (7).
  5. Turbocharger according to Claim 4, characterized in that the sealing ring (1) is connected to the one end region (5A) of the elastomer moulded part (5) in a positive locking, non-positive locking or frictional locking manner, or by means of a combination of these types of connection.
  6. Turbocharger according to one of Claims 3 to 5, characterized in that the one end region (5A) is pressed on the sealing ring (1) by means of a first locking ring (4).
  7. Turbocharger according to one of Claims 4 to 6, characterized in that the other end region (5B) is fixable by means of a second locking ring (6) in a bore of the bearing housing (7) or in an attached part (8) of the bearing housing (7), as the case may be.
  8. Turbocharger according to one of Claims 1 to 7, characterized in that the feed devices (2, 3) are formed as slots (19) in or on the end faces (17, 17') of the sealing ring (1).
  9. Turbocharger according to Claim 8, characterized in that the slots (19, 19') are defined by air guiding ribs (18, 18') which are arranged on the end faces (17, 17') of the sealing ring (1).
  10. Sealing device (20) for a turbocharger (15) which has a bearing housing (7), a rotor shaft (12) which is supported in the bearing housing (7), and a bearing housing oil chamber (13) which is located in the bearing housing (7), and also has a compressor casing with a compressor chamber (14), wherein the sealing device (20) has a sealing ring (1) with two end faces (17, 17'),
    characterized in that
    - the sealing ring (1) has oppositely orientated air feed devices (2, 3) in or on the end faces (17, 17'); and
    - the sealing ring (1) is positionable with an axial clearance on the rotor shaft (12) of the turbocharger (15) between a disc (9) and a packing sleeve (16) of the turbocharger (15).
  11. Sealing device according to Claim 10, characterized by at least one of the features of Claims 2 to 9.
EP05023173A 2005-10-24 2005-10-24 Turbocharger Active EP1777417B1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP05023173A EP1777417B1 (en) 2005-10-24 2005-10-24 Turbocharger
DE502005004418T DE502005004418D1 (en) 2005-10-24 2005-10-24 turbocharger
JP2008536947A JP5106406B2 (en) 2005-10-24 2006-05-23 Turbocharger
PCT/EP2006/004908 WO2007048451A1 (en) 2005-10-24 2006-05-23 Turbocharger
US12/091,123 US8096774B2 (en) 2005-10-24 2006-05-23 Turbocharger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05023173A EP1777417B1 (en) 2005-10-24 2005-10-24 Turbocharger

Publications (2)

Publication Number Publication Date
EP1777417A1 EP1777417A1 (en) 2007-04-25
EP1777417B1 true EP1777417B1 (en) 2008-06-11

Family

ID=35610220

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05023173A Active EP1777417B1 (en) 2005-10-24 2005-10-24 Turbocharger

Country Status (5)

Country Link
US (1) US8096774B2 (en)
EP (1) EP1777417B1 (en)
JP (1) JP5106406B2 (en)
DE (1) DE502005004418D1 (en)
WO (1) WO2007048451A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249887B2 (en) * 2010-08-03 2016-02-02 Dresser-Rand Company Low deflection bi-metal rotor seals
US20150125263A1 (en) * 2012-05-16 2015-05-07 Borgwarner Inc. Flinger oil seal and turbocharger incorporating the same
CN103758589A (en) * 2013-12-30 2014-04-30 常州环能涡轮动力股份有限公司 Graphite seal device for turbocharger for gasoline engine
FR3024492B1 (en) * 2014-07-29 2019-08-23 Safran Aircraft Engines ELEMENT COMPRISING A STATOR AND A TURBOMACHINE ROTOR WITH A SEAL AND TESTING THIS SEAL
US10274087B2 (en) * 2015-09-25 2019-04-30 Flowserve Management Company Reverse pressure capable mechanical seal
CN105240308A (en) * 2015-11-10 2016-01-13 湖南天雁机械有限责任公司 Compressor end sealing sleeve of turbocharger

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Publication number Priority date Publication date Assignee Title
US3407994A (en) * 1966-11-15 1968-10-29 Hoover Co Shaft seal
US4196910A (en) * 1977-05-19 1980-04-08 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Shaft sealing device for turbocharger
US4268229A (en) * 1979-04-19 1981-05-19 The Garrett Corporation Turbocharger shaft seal arrangement
JPS5613513U (en) * 1979-07-10 1981-02-05
US4420160A (en) 1980-03-10 1983-12-13 The Garrett Corporation Face seal system
FR2503478A2 (en) * 1981-04-03 1982-10-08 Etri Sa Flat wall-mounted electric fan for electronic equipment - has resilient disc sealing end of channel formed through centre of rotor
US4502693A (en) * 1984-07-19 1985-03-05 Allis-Chalmers Corporation Bushing seal with dual restricted fluid passages
JPS63297734A (en) * 1987-05-29 1988-12-05 Canon Inc Turbocharger
DE3830470A1 (en) * 1988-09-08 1990-03-15 Mtu Friedrichshafen Gmbh SEALING DEVICE BETWEEN SHAFT AND HOUSING OF A FLUID MACHINE WITH AT LEAST ONE IMPELLER
US4986733A (en) * 1989-10-30 1991-01-22 Allied-Signal, Inc. Turbocharger compressor wheel assembly with boreless hub compressor wheel
JPH0874590A (en) * 1994-09-01 1996-03-19 Toyota Motor Corp Shaft sealing structure of supercharger
US5890881A (en) * 1996-11-27 1999-04-06 Alliedsignal Inc. Pressure balanced turbocharger rotating seal
GB2359863B (en) * 2000-03-04 2003-03-26 Alstom Turbocharger
GB0108119D0 (en) * 2001-03-30 2001-05-23 Holset Engineering Co Oil control device
GB0218092D0 (en) * 2002-08-03 2002-09-11 Holset Engineering Co Turbocharger

Also Published As

Publication number Publication date
US8096774B2 (en) 2012-01-17
DE502005004418D1 (en) 2008-07-24
WO2007048451A1 (en) 2007-05-03
EP1777417A1 (en) 2007-04-25
US20080317596A1 (en) 2008-12-25
JP2009512815A (en) 2009-03-26
JP5106406B2 (en) 2012-12-26

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