CH407665A - Storage of centrifugal machine rotors - Google Patents
Storage of centrifugal machine rotorsInfo
- Publication number
- CH407665A CH407665A CH434064A CH434064A CH407665A CH 407665 A CH407665 A CH 407665A CH 434064 A CH434064 A CH 434064A CH 434064 A CH434064 A CH 434064A CH 407665 A CH407665 A CH 407665A
- Authority
- CH
- Switzerland
- Prior art keywords
- bearing
- axial
- bushes
- floating
- lubricant
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/166—Sliding contact bearing
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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
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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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
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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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
- F16C17/26—Systems consisting of a plurality of sliding-contact bearings
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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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Description
Lagerung von Kreiselmaschinenrotoren Die Erfindung bezieht sich auf die Lagerung eines Kreiselmaschi,nenrotors. Dabei sind schwimmende Büchsen als Lagerelemente vorgesehen. Schwim mende Büchsen sind als Radiallager bekannt. Erfin dungsgemäss sollen sie gleichzeitig als Axiallagerele- mente dienen. Dabei werden die Stirnflächen der Büchsen zur Aufnahme von Achsschüben benutzt. Die Stirnflächen können dabei zur Erhöhung der Tragfähigkeit nach bekannten Verfahren mit hydro dynamischen Tragprofilen versehen sein.
Erfin dungsgemäss erfolgt der Zutritt des Schmiermittels in der Weise, dass die Bewegung des Schmiermittels in den an den axial tragenden Stirnflächen der Büchsen, gebildeten Schmierspalten in Richtung des durch die Rotation der Büchse dort vorhandenen Fliehkraftfel des erfolgt. Vorteilhafterweise wird dadurch, eine in tensive Durchströmung der Schmierspalte auch bei hohen Drehzahlen erreicht, wodurch die Wärmeab fuhr aus den Lagern und die Tragfähigkeit verbessert werden.
In den beiliegenden Zeichnungen ist am Beispiel des Rotors eines Abgas-Turboaufladegerätes der Er findungsgegenstand veranschaulicht.
Die Gesamtanordnung der Lagerung zeigt Fig. <B>1,</B> und Fig. 2 den vergrössert dargestellten Ausschnitt des linksseitigen Lagers. Gleiche Teile sind in Fig. <B>1,</B> Fig. 2, Fig. <B>3</B> und Fig. 4 mit gleichen Zahlen bezeich net. Die Teile<B>1</B> sind die schwimmenden Büchsen, Teil 2 der Lagerträger des Gehäuses, Teil 4 die Welle des Rotors. Die Teile<B>3</B> dienen dem axialen Anlauf der schwimmenden Büchsen am Lagerträger. Sie können, wie im Beispiel dargestellt, in den Lage rungsträger eingeschoben oder aber auch mit dem Lagerungsträger einteilig sein.
In Fig. <B>3</B> ist zum axia len Anlauf der schwimmenden Büchsen eine einteilig ausgebildete feststehende Mittelbüchse 14 eingescho- ben. Diese ist gegen axiale Verschiebung und Ver- drehungdurch eine Fixierschraube<B>15</B> gesichert. Die in der Büchse radial angeordneten Löcher<B>16</B> dienen einerseits der #ölzufuhr und andererseits greift in eine von ihnen die Fixierschraube<B>15</B> ein, wobei die Löcher wie in der Abwicklung Fig. 4 dargestellt am Umfang axialen Versatz aufweisen können, um die Axialeinstellung des Rotors vornehmen zu können.
Die Teile<B>5</B> und<B>5'</B> dienen ün Beispiel dem axialen Anlauf des Rotors an die schwimmenden Büchsen; mindestens eine von ihnen kann mit dem Rotor ein4 teilig sein. Die Schmiermittelzuführung erfolgt durch den Kanal<B>6.</B> Das Schmiermittel verzweigt sich nach rechts und links und durchströmt in axialer Richtung den Spalt<B>7,</B> in, Fig. 2. Nach Durchströmen von Spalt <B>7</B> verzweigt es sich abermals. Ein Teilstrom durch strömt den Schmierspalt<B>8</B> in radialer Richtung nach aussen.
Diese Bewegung wird gefördert durch die ebenfalls radial nach aussen wirkenden Zentrifugal- kräfte, die bei Rotation der schwimmenden Büchse auf das an ihrer axialen Anlauffläche<B>8'</B> haftende Schmiermittel wirksam werden. Dieser Teilstrom des Schmiermittels durchströmt anschliessend den Schmierspalt<B>9</B> in axialer Richtung und tritt an dessen Ende in den Schmiermittelablaufraum aus.
Der andere Teilstrom durchtritt zunächst den Schmierspalt<B>10</B> in axialer Richtung und durchströmt den Schmierspalt<B>11</B> in radialer Richtung nach aus sen. Dabei wird auch hierdiese Bewegung durch die ebenfalls radial nach aussen wirkenden Zentrifugal- kräfte gefördert, die bei Rotation auf das an der axia len Anlauffläche<B>11'</B> der schwimmenden Büchse und der axialen Anlauffläche<B>11"</B> des Rotors haftende Schmiermittel wirksam werden. Aus dem Schmier spalt<B>11</B> tritt das Schmiermittel ebenfalls in den<B>Ab-</B> laufraum aus. Die am Rotor wirksame Axialkraft wird<B>je</B> nach ihrer Wirkungsrichtung auf dem linken oder rechten Lager abgestützt.
Im Beispiel der Fig. 2 wird die Axi- alkraft P von der Anlauffläche lY' des Rotors über den Schmierspalt<B>11</B> auf die, axiale Anlauffläche<B>11'</B> der schwimmenden Büchse übertragen. Letztere wie derum wird von ihrer axialen Anlauffläche<B>8'</B> -über den Schmierspelt <B>8</B> auf die axiale Anlauffläche<B>8"</B> des Lagerträgers abgestützt.
Zur Erhöhung der Tragfähigkeit können die An laufflächen lF', ll', <B>8'</B> und<B>V</B> sämtlich oder nur einige von ihnen in bekannter Weise mit die hydro dynamische Tragfähigkeit erhöhenden Profilen ver sehen sein.
Zur Dosierung der Schmiermittelströme können sowohl an den axialen wie auch den radialen Laufflä chen der Lagerung Schmiemuten 12 und 12' bzw. <B>13</B> und<B>13'</B> angebracht sein.
Storage of centrifugal machine rotors The invention relates to the storage of a centrifugal machine rotor. Floating bushes are provided as bearing elements. Floating bushes are known as radial bearings. According to the invention, they are intended to serve as axial bearing elements at the same time. The end faces of the bushes are used to accommodate axle thrusts. The end faces can be provided with hydrodynamic support profiles by known methods to increase the load-bearing capacity.
In accordance with the invention, the access of the lubricant takes place in such a way that the movement of the lubricant in the lubrication gaps formed on the axially bearing end faces of the bushes takes place in the direction of the centrifugal force field present there due to the rotation of the bush. Advantageously, an intensive flow through the lubrication gap is achieved even at high speeds, whereby the heat dissipated from the bearings and the load capacity are improved.
In the accompanying drawings, the subject of the invention is illustrated using the example of the rotor of an exhaust gas turbocharger.
The overall arrangement of the bearing is shown in FIGS. 1, and 2, the enlarged section of the bearing on the left. The same parts are denoted by the same numbers in FIG. 1, FIG. 2, FIG. 3 and FIG. 4. The parts <B> 1 </B> are the floating bushings, part 2 the bearing bracket of the housing, part 4 the shaft of the rotor. The parts <B> 3 </B> are used for the axial run-up of the floating bushes on the bearing bracket. As shown in the example, they can be inserted into the bearing support or they can also be integral with the bearing support.
In FIG. 3, a one-piece stationary central bushing 14 is inserted for axial contact of the floating bushes. This is secured against axial displacement and rotation by a fixing screw <B> 15 </B>. The holes <B> 16 </B> arranged radially in the liner are used on the one hand to supply oil and on the other hand the fixing screw 15 engages in one of them, the holes as shown in the development in FIG. 4 can have an axial offset on the circumference in order to be able to carry out the axial adjustment of the rotor.
The parts <B> 5 </B> and <B> 5 '</B> serve, for example, the axial run-up of the rotor on the floating bushes; at least one of them can be integral with the rotor. The lubricant is supplied through the channel <B> 6. </B> The lubricant branches to the right and left and flows through the gap <B> 7, </B> in FIG. 2 in the axial direction. After flowing through the gap < B> 7 </B> it branches again. A partial flow flows through the lubrication gap <B> 8 </B> in the radial direction outwards.
This movement is promoted by the centrifugal forces also acting radially outwards, which, when the floating sleeve rotates, act on the lubricant adhering to its axial contact surface 8 '. This partial flow of the lubricant then flows through the lubrication gap <B> 9 </B> in the axial direction and exits at its end into the lubricant drainage space.
The other partial flow first passes through the lubrication gap <B> 10 </B> in the axial direction and flows through the lubrication gap <B> 11 </B> in the radial direction outward. Here, too, this movement is promoted by the centrifugal forces, which also act radially outwards, which upon rotation act on the axial contact surface <B> 11 '</B> of the floating bush and the axial contact surface <B> 11 "</ B> of the rotor, the lubricant adhering to the rotor become effective. The lubricant also escapes from the lubricating gap <B> 11 </B> into the <B> waste </B> running space. The axial force acting on the rotor is <B> depending < / B> supported on the left or right bearing according to their direction of action.
In the example of FIG. 2, the axial force P is transmitted from the contact surface lY 'of the rotor via the lubrication gap 11 to the axial contact surface 11' of the floating bush. The latter, in turn, is supported by its axial contact surface <B> 8 '</B> - via the lubricant <B> 8 </B> on the axial contact surface <B> 8 "</B> of the bearing bracket.
To increase the load-bearing capacity, the contact surfaces IF ', ll', <B> 8 '</B> and <B> V </B> can all or only some of them in a known manner with profiles that increase the hydrodynamic load-bearing capacity be.
For metering the lubricant flows, lubricating grooves 12 and 12 'or <B> 13 </B> and <B> 13' can be attached to both the axial and the radial running surfaces of the bearing.
Claims (1)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH434064A CH407665A (en) | 1964-04-06 | 1964-04-06 | Storage of centrifugal machine rotors |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH434064A CH407665A (en) | 1964-04-06 | 1964-04-06 | Storage of centrifugal machine rotors |
Publications (1)
Publication Number | Publication Date |
---|---|
CH407665A true CH407665A (en) | 1966-02-15 |
Family
ID=4274260
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CH434064A CH407665A (en) | 1964-04-06 | 1964-04-06 | Storage of centrifugal machine rotors |
Country Status (1)
Country | Link |
---|---|
CH (1) | CH407665A (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3005873A1 (en) * | 1979-02-22 | 1980-09-04 | Wallace Murray Corp | BEARING STRUCTURE FOR FAST ROTATING SHAFTS |
EP0021738A1 (en) * | 1979-06-19 | 1981-01-07 | Household Manufacturing, Inc. | Floating ring bearing structure and turbocharger employing same |
EP0794319A1 (en) * | 1996-03-06 | 1997-09-10 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger bearing arrangement |
DE102008046582A1 (en) * | 2008-09-10 | 2010-03-11 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Exhaust gas turbocharger for internal combustion engine, particularly motor vehicle, has shaft, which is pivoted in housing of exhaust gas turbocharger |
EP1998010A3 (en) * | 2007-05-30 | 2010-07-21 | Bosch Mahle Turbo Systems GmbH & Co. KG | Bearing arrangement of a turbocharger |
DE102011077137A1 (en) * | 2011-06-07 | 2012-12-13 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Slide bearing assembly for turbocharger, has axial grooves which are evenly distributed with respect to bearing tunnel so as to inhibit or eliminate circulation of lubricant in the circumferential direction of the bearing tunnel |
DE102012207010A1 (en) * | 2012-04-27 | 2013-10-31 | Continental Automotive Gmbh | Exhaust gas turbocharger has lubricating oil collecting space that is provided between both floating bush bodies and stands in connection with lubricating oil supplying bore, from which radial bearing is guided from lubricating oil |
CN106662144A (en) * | 2014-08-28 | 2017-05-10 | 三菱重工业株式会社 | Bearing device and rotary machine |
-
1964
- 1964-04-06 CH CH434064A patent/CH407665A/en unknown
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3005873A1 (en) * | 1979-02-22 | 1980-09-04 | Wallace Murray Corp | BEARING STRUCTURE FOR FAST ROTATING SHAFTS |
EP0021738A1 (en) * | 1979-06-19 | 1981-01-07 | Household Manufacturing, Inc. | Floating ring bearing structure and turbocharger employing same |
EP0794319A1 (en) * | 1996-03-06 | 1997-09-10 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger bearing arrangement |
US5993173A (en) * | 1996-03-06 | 1999-11-30 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger |
EP1582755A2 (en) * | 1996-03-06 | 2005-10-05 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger bearing arrangement |
EP1582755A3 (en) * | 1996-03-06 | 2005-10-12 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger bearing arrangement |
EP1998010A3 (en) * | 2007-05-30 | 2010-07-21 | Bosch Mahle Turbo Systems GmbH & Co. KG | Bearing arrangement of a turbocharger |
DE102008046582A1 (en) * | 2008-09-10 | 2010-03-11 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Exhaust gas turbocharger for internal combustion engine, particularly motor vehicle, has shaft, which is pivoted in housing of exhaust gas turbocharger |
DE102011077137A1 (en) * | 2011-06-07 | 2012-12-13 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Slide bearing assembly for turbocharger, has axial grooves which are evenly distributed with respect to bearing tunnel so as to inhibit or eliminate circulation of lubricant in the circumferential direction of the bearing tunnel |
DE102012207010A1 (en) * | 2012-04-27 | 2013-10-31 | Continental Automotive Gmbh | Exhaust gas turbocharger has lubricating oil collecting space that is provided between both floating bush bodies and stands in connection with lubricating oil supplying bore, from which radial bearing is guided from lubricating oil |
CN106662144A (en) * | 2014-08-28 | 2017-05-10 | 三菱重工业株式会社 | Bearing device and rotary machine |
EP3163103A4 (en) * | 2014-08-28 | 2017-09-13 | Mitsubishi Heavy Industries, Ltd. | Bearing device and rotary machine |
US9897137B2 (en) | 2014-08-28 | 2018-02-20 | Mitsubishi Heavy Industries, Ltd. | Bearing device and rotary machine |
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