WO2000040870A1 - Axiallagerung für schnellaufende rotoren - Google Patents
Axiallagerung für schnellaufende rotoren Download PDFInfo
- Publication number
- WO2000040870A1 WO2000040870A1 PCT/CH1999/000616 CH9900616W WO0040870A1 WO 2000040870 A1 WO2000040870 A1 WO 2000040870A1 CH 9900616 W CH9900616 W CH 9900616W WO 0040870 A1 WO0040870 A1 WO 0040870A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- membrane
- axial
- cavity
- axial bearing
- Prior art date
Links
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP99973582A EP1141564A1 (de) | 1998-12-30 | 1999-12-21 | Axiallagerung für schnellaufende rotoren |
JP2000592547A JP2002534647A (ja) | 1998-12-30 | 1999-12-21 | 高速回転ロータ用のスラスト軸受装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19860783A DE19860783A1 (de) | 1998-12-30 | 1998-12-30 | Axiallagerung für schnellaufende Rotoren |
DE19860783.0 | 1998-12-30 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000040870A1 true WO2000040870A1 (de) | 2000-07-13 |
Family
ID=7893157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CH1999/000616 WO2000040870A1 (de) | 1998-12-30 | 1999-12-21 | Axiallagerung für schnellaufende rotoren |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1141564A1 (de) |
JP (1) | JP2002534647A (de) |
DE (1) | DE19860783A1 (de) |
TW (1) | TW418291B (de) |
WO (1) | WO2000040870A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016119682A1 (de) * | 2016-10-14 | 2018-04-19 | Abb Turbo Systems Ag | Schublageranordnung für Turbolader |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1577608A (de) * | 1967-08-10 | 1969-08-08 | ||
FR2109527A5 (de) * | 1970-10-23 | 1972-05-26 | Motoren Turbinen Union | |
GB1485773A (en) * | 1973-11-16 | 1977-09-14 | Mannesmann Ag | Hydraulically loaded axial thrust bearing for a shaft provided with a thrust collar more particularly for ship transmission apparatus |
US4239300A (en) * | 1978-02-10 | 1980-12-16 | Polysius Ag | Hydrostatic bearing |
US4288128A (en) * | 1979-10-01 | 1981-09-08 | Caterpillar Tractor Co. | Self-aligning thrust bearing |
FR2547878A1 (fr) * | 1983-06-27 | 1984-12-28 | Alsthom Atlantique | Dispositif d'appui axial d'un arbre avec anneaux glissants rigides |
EP0362327B1 (de) | 1988-03-25 | 1994-01-19 | Asea Brown Boveri Ag | Axiallagerung mit einer schiefstellungskompensation |
US5531522A (en) * | 1987-05-29 | 1996-07-02 | Kmc, Inc. | Fluid dampened support having variable stiffness and damping |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH422437A (de) * | 1964-08-19 | 1966-10-15 | Escher Wyss Ag | Wellenlager für einen auf sich einstellenden Lagersegmenten gleitenden Rotor |
DE2604889A1 (de) * | 1976-02-07 | 1977-08-11 | Polysius Ag | Hydrostatische lagerstelle sowie hydrostatisches lager mit mehreren solcher lagerstellen |
CH631523A5 (de) * | 1978-09-14 | 1982-08-13 | Bbc Brown Boveri & Cie | Kammlager. |
FR2576647B1 (fr) * | 1985-01-28 | 1990-08-10 | Europ Propulsion | Palier, notamment pour arbre tournant |
US5620260A (en) * | 1987-05-29 | 1997-04-15 | Ide; Russell D. | Variable characteristic thrust bearing |
JPH0216820U (de) * | 1988-07-19 | 1990-02-02 | ||
EP0757186B1 (de) * | 1995-08-02 | 2003-09-03 | Renk Aktiengesellschaft | Gleitlager-Gleitschuh mit einer Druckfeder |
-
1998
- 1998-12-30 DE DE19860783A patent/DE19860783A1/de not_active Withdrawn
-
1999
- 1999-12-21 JP JP2000592547A patent/JP2002534647A/ja active Pending
- 1999-12-21 EP EP99973582A patent/EP1141564A1/de not_active Withdrawn
- 1999-12-21 WO PCT/CH1999/000616 patent/WO2000040870A1/de not_active Application Discontinuation
- 1999-12-23 TW TW088122765A patent/TW418291B/zh not_active IP Right Cessation
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1577608A (de) * | 1967-08-10 | 1969-08-08 | ||
FR2109527A5 (de) * | 1970-10-23 | 1972-05-26 | Motoren Turbinen Union | |
GB1485773A (en) * | 1973-11-16 | 1977-09-14 | Mannesmann Ag | Hydraulically loaded axial thrust bearing for a shaft provided with a thrust collar more particularly for ship transmission apparatus |
US4239300A (en) * | 1978-02-10 | 1980-12-16 | Polysius Ag | Hydrostatic bearing |
US4288128A (en) * | 1979-10-01 | 1981-09-08 | Caterpillar Tractor Co. | Self-aligning thrust bearing |
FR2547878A1 (fr) * | 1983-06-27 | 1984-12-28 | Alsthom Atlantique | Dispositif d'appui axial d'un arbre avec anneaux glissants rigides |
US5531522A (en) * | 1987-05-29 | 1996-07-02 | Kmc, Inc. | Fluid dampened support having variable stiffness and damping |
EP0362327B1 (de) | 1988-03-25 | 1994-01-19 | Asea Brown Boveri Ag | Axiallagerung mit einer schiefstellungskompensation |
Also Published As
Publication number | Publication date |
---|---|
JP2002534647A (ja) | 2002-10-15 |
EP1141564A1 (de) | 2001-10-10 |
DE19860783A1 (de) | 2000-07-20 |
TW418291B (en) | 2001-01-11 |
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