CA2489699A1 - Bearing for the rotor of a rotating machine - Google Patents
Bearing for the rotor of a rotating machine Download PDFInfo
- Publication number
- CA2489699A1 CA2489699A1 CA002489699A CA2489699A CA2489699A1 CA 2489699 A1 CA2489699 A1 CA 2489699A1 CA 002489699 A CA002489699 A CA 002489699A CA 2489699 A CA2489699 A CA 2489699A CA 2489699 A1 CA2489699 A1 CA 2489699A1
- Authority
- CA
- Canada
- Prior art keywords
- bearing
- radial
- axial
- rotor
- sliding surface
- 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.)
- Abandoned
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
-
- 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
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/08—Structural association with bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
- Rotary Pumps (AREA)
- Supercharger (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention relates to a bearing for a rotor of a rotating machine (10), especially a hydrogenerator which rotates around a vertically rotating axis (11). Said bearing is embodied as a sliding bearing and comprises first mean s (21, 24) for axial bearing and second means (21, 25) for radial bearing. Due to said bearing, simplified and improved bearing properties are achieved suc h that the first and second means are united to form a combined radial and axi al bearing (21) which simultaneously comprises axially sliding surfaces (24) an d radially sliding surfaces (25).
Description
DESCRIPTION
BEARING FOR THE ROTOR OF A ROTATING MACHINE
TECHNICAL FIELD
The present invention pertains to the field of rotating machines. It relates to a bearing for the rotor of a rotating machine according to the preamble of claim 1.
Such a bearing is known, for example from CH-A5-651 362.
PRIOR ART
Rotors of large rotating machines, such as hydrogenerators, are normally carried by hydrodynamic sliding bearings. In these bearings, the axial and radial guidance is performed by separate bearings of different design. A partial combination of these intrinsically separate bearings is possible inasmuch as a running ring running in an axial bearing additionally absorbs radial forces by radial guide segments being arranged around said running ring. Such a configuration, as is known from CH-A5-651 362 mentioned at the beginning (see fig. 1 there), is reproduced in highly simplified form in figure 1. In the rotating machine 10' of figure l, the rotor is mounted with the rotor shaft 12 such that it can be rotated about a vertical axis of rotation 11. For this purpose, a running ring 14' is fixed to the rotor shaft 12 via a flange 13 and slides with the underside on the sliding surface 20 of an axial bearing or supporting bearing 17 comprising individual segments (vertical arrows in figure 1). The axial bearing 17 is in turn supported in the axial direction by a support 18. With the outer side, the running ring 14' slides along the sliding surface 19 of a radial bearing or guide bearing 15 (horizontal arrows in figure 1) . The radial bearing 15 is in turn supported in the radial direction by supports 16.
The axial bearing 17 and the radial bearing or guide bearing 15 function independently of one another in this known configuration. Both bearings run in an oil bath. The function of "carrying the rotor" is performed by the axial bearing 17, the function of "guiding the rotor" is performed by the guide or radial bearing 15.
Both bearings have their own segments matched to the respective function.
In the known mounting having the separate bearing functions, the disadvantage is that the thickness of the running ring in the axial direction has to be chosen to be large enough to permit the radial mounting arranged laterally on the running ring. As a result, the machine becomes longer overall in the axial direction.
However, the fact that the radial mounting is placed on the outer side of the running ring is also disadvantageous. At this point, the circumferential speeds are comparatively high, which leads to correspondingly high friction losses.
Finally, separate segments have to be produced and installed for the two bearings, which overall considerably increases the expenditure on producing and assembling the mounting.
SUMMARY OF THE INVENTION
It is therefore an object of the invention to provide a bearing for a rotating machine which avoids the disadvantages of known bearings and is distinguished in particular by a simplified, space-saving construction and, in operation, leads to considerably reduced friction losses.
The object is achieved by all of the features of claim 1. The core of the invention is to combine the previously separated radial bearing and axial bearing (or their bearing segments) to form a combined radial and axial bearing which has axial sliding surfaces and radial sliding surfaces at the same time. As distinct from the prior art according to figure 1, in which, although a common running ring for the two bearings is fixed to the rotor, separate bearing segments are used for the two bearings, here the two sliding surfaces are arranged on the same bearing (or bearing segment). In this way, a simplified, more compact construction of the bearing is made possible, in which, at the same time, the friction losses are reduced by means of a skilful arrangement of the sliding surfaces.
A first preferred refinement of the invention is characterized in that the combined radial and axial bearing comprises a plurality of individual bearing segments, which have the form of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation, in that an axial sliding surface and a radial sliding surface are formed on each of the bearing segments, and in that each bearing segment has its own radial support.
According to one alternative, the combined radial and axial bearing is arranged in an oil bath.
Another alternative is distinguished by the fact that means for supplying lubricating oil are provided in the bearing segments, which lubricating oil emerges onto the sliding surfaces through outlet openings in the axial and radial sliding surfaces, there preferably being provided in each bearing segment, in the axial sliding surface, a first outlet opening, which has the form of an elongated slot extending in the radial direction and, as viewed in the direction of rotation, is arranged at the start of the axial sliding surface, and there being arranged in each bearing segment, in the radial sliding surface, a second outlet opening, which has the form of an elongated slot extending in the axial direction and, as viewed in the direction of rotation, is arranged at the start of the radial sliding surface. The outlet openings of each bearing segment are preferably connected to a common oil feed bore via connecting ducts.
The mounting according to the invention is simplified further and is distinguished by reduced friction losses if, according to another advantageous refinement, the rotor has a rotor shaft, if a running ring surrounding the rotor shaft concentrically is fixed to the rotor shaft, with which ring the rotor slides on the axial sliding surfaces of the combined radial and axial bearing, and if the rotor with the rotor shaft itself slides on the radial sliding surfaces of the combined radial and axial bearing.
BRIEF EXPLANATION OF THE FIGURES
The invention is to be explained in more detail in the following text by using examplary embodiments in conjunction with the drawing, in which figure 1 shows a mounting of a rotor of a vertical hydrogenerator with separate radial and axial bearing according to the prior art in a simplified, partially longitudinally sectioned illustration;
figure 2 shows a mounting with combined radial and axial bearing according to a preferred exemplary embodiment of the invention in an illustration comparable with figure l; and figure 3 shows an individual bearing segment of the mounting shown in figure 2, in which lubricating oil is specifically supplied to the sliding surfaces within the bearing segment, in a perspective view in the radial direction.
PREFERRED EMBODIMENTS OF THE INVENTION
A mounting with combined radial and axial bearing according to a preferred exemplary embodiment of the invention is reproduced in figure 2 in an illustration comparable with figure 1. Identical parts are largely designated by the same designations here. The rotating machine 10 rotates with a rotor, of which part of the rotor shaft 12 is shown in figure 2, about the vertical axis of rotation 11. Fixed to the rotor shaft 12 via a flange 13 is a running ring 14, which is used exclusively for the axial mounting. In terms of its axial thickness, it can therefore be reduced considerably as compared with the running ring 14' from figure 1.
The rotor slides with the running ring 14 on the upper, axial (horizontal) sliding surface 24 of a combined radial and axial bearing 21 (assembled from bearing segments), which is in turn supported in the axial direction by an axial support 23. The combined radial and axial bearing 21 is extended toward the rotor shaft 12 in the radial direction to such an extent that a radial (vertical) sliding surface 25 can be formed, on which the rotor shaft 12 is guided. The combined radial and axial bearing 21 is supported in the radial direction by a radial support 22 for this purpose.
Since the radial sliding surface 25 is located very much further in than the radial sliding surface I9 in the known bearing from figure 1, at the same rotational speed the result is a very much lower circumferential speed, which leads to lower friction losses and therefore lower heating.
The combined radial and axial bearing 21 preferably comprises individual bearing segments 26 according to figure 3, which have the form of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation 11 or rotor shaft 12.
An axial sliding surface 24 and a radial sliding surface 25 are formed on each of the bearing segments 26. Each of the bearing segments 26 has its own radial I5 support 22, whose force introduction surface is indicated in figure 3 by a circle.
The combined radial and axial bearing 21 can in principle be arranged in an oil bath. However, means 29,..,32 for supplying lubricating oil are preferably provided in the bearing segments 26 according to figure 3, the lubricating oil emerging onto the sliding surfaces 24, 25 through outlet openings 27, 28 in the axial and radial sliding surfaces 24 and 25. In the axial sliding surfaces 24, the means comprise a first outlet opening 27, which has the form of an elongated slot extending in the radial direction and, as viewed in the direction of rotation, is arranged at the start of the axial sliding surface 24. The lubricating oil emerging through the slot is in this way distributed in the form of a lubricating film on the sliding surface 24 by the bearing ring 14 sliding over the sliding surface 24. In an analogous way, in the radial sliding surface 25 there is provided a second outlet opening 28, which has the form of an elongated slot extending in the axial direction and, as viewed in the direction of rotation, is arranged at the start of the radial sliding surface 25.
The lubricating oil emerging from the outlet openings 27, 28 is led out from a rear connection 32 via a radial oil feed bore 31 arranged in the interior of the bearing segment 26 and is distributed to the outlet openings 27, 28 via connecting ducts 29, 30. In the comparatively long outlet opening 27, a plurality of connecting ducts 29 distributed over the length are provided.
The invention has been explained by using the example.
of a vertical hydrogenerator. It goes without saying that the use of the combined radial and axial bearing according to the invention is not restricted to hydrogenerators of this type.
Overall, the invention results in a combined radial and axial bearing which is specifically distinguished by the following advantages:
- The bearing needs less space in the axial direction. The entire machine can therefore be of lower construction.
- The radial bearing has a smaller radius toward the shaft. This means a lower circumferential speed and, as a result, lower friction losses.
- Overall, fewer bearing parts are needed.
LIST OF DESIGNATIONS
10, 10' Rotating machine (e. g. hydrogenerator) 11 Axis of rotation 12 Rotor shaft 13 Flange 14, 19' Running ring 15 Radial bearing (guide bearing) 16 Support (radial bearing) 17 Axial bearing (supporting bearing) 18 Support (axial bearing) 19 Sliding surface (radial bearing) 20 Sliding surface (axial bearing) 21 Combined radial and axial bearing 22 Radial support 23 Axial support 24 Axial sliding surface 25 Radial sliding surface 26 Bearing segment 27 Outlet opening (axial sliding surface) 28 Outlet opening (radial siding surface) 29, 30 Connecting duct 31 Oil feed bore 32 Connection
BEARING FOR THE ROTOR OF A ROTATING MACHINE
TECHNICAL FIELD
The present invention pertains to the field of rotating machines. It relates to a bearing for the rotor of a rotating machine according to the preamble of claim 1.
Such a bearing is known, for example from CH-A5-651 362.
PRIOR ART
Rotors of large rotating machines, such as hydrogenerators, are normally carried by hydrodynamic sliding bearings. In these bearings, the axial and radial guidance is performed by separate bearings of different design. A partial combination of these intrinsically separate bearings is possible inasmuch as a running ring running in an axial bearing additionally absorbs radial forces by radial guide segments being arranged around said running ring. Such a configuration, as is known from CH-A5-651 362 mentioned at the beginning (see fig. 1 there), is reproduced in highly simplified form in figure 1. In the rotating machine 10' of figure l, the rotor is mounted with the rotor shaft 12 such that it can be rotated about a vertical axis of rotation 11. For this purpose, a running ring 14' is fixed to the rotor shaft 12 via a flange 13 and slides with the underside on the sliding surface 20 of an axial bearing or supporting bearing 17 comprising individual segments (vertical arrows in figure 1). The axial bearing 17 is in turn supported in the axial direction by a support 18. With the outer side, the running ring 14' slides along the sliding surface 19 of a radial bearing or guide bearing 15 (horizontal arrows in figure 1) . The radial bearing 15 is in turn supported in the radial direction by supports 16.
The axial bearing 17 and the radial bearing or guide bearing 15 function independently of one another in this known configuration. Both bearings run in an oil bath. The function of "carrying the rotor" is performed by the axial bearing 17, the function of "guiding the rotor" is performed by the guide or radial bearing 15.
Both bearings have their own segments matched to the respective function.
In the known mounting having the separate bearing functions, the disadvantage is that the thickness of the running ring in the axial direction has to be chosen to be large enough to permit the radial mounting arranged laterally on the running ring. As a result, the machine becomes longer overall in the axial direction.
However, the fact that the radial mounting is placed on the outer side of the running ring is also disadvantageous. At this point, the circumferential speeds are comparatively high, which leads to correspondingly high friction losses.
Finally, separate segments have to be produced and installed for the two bearings, which overall considerably increases the expenditure on producing and assembling the mounting.
SUMMARY OF THE INVENTION
It is therefore an object of the invention to provide a bearing for a rotating machine which avoids the disadvantages of known bearings and is distinguished in particular by a simplified, space-saving construction and, in operation, leads to considerably reduced friction losses.
The object is achieved by all of the features of claim 1. The core of the invention is to combine the previously separated radial bearing and axial bearing (or their bearing segments) to form a combined radial and axial bearing which has axial sliding surfaces and radial sliding surfaces at the same time. As distinct from the prior art according to figure 1, in which, although a common running ring for the two bearings is fixed to the rotor, separate bearing segments are used for the two bearings, here the two sliding surfaces are arranged on the same bearing (or bearing segment). In this way, a simplified, more compact construction of the bearing is made possible, in which, at the same time, the friction losses are reduced by means of a skilful arrangement of the sliding surfaces.
A first preferred refinement of the invention is characterized in that the combined radial and axial bearing comprises a plurality of individual bearing segments, which have the form of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation, in that an axial sliding surface and a radial sliding surface are formed on each of the bearing segments, and in that each bearing segment has its own radial support.
According to one alternative, the combined radial and axial bearing is arranged in an oil bath.
Another alternative is distinguished by the fact that means for supplying lubricating oil are provided in the bearing segments, which lubricating oil emerges onto the sliding surfaces through outlet openings in the axial and radial sliding surfaces, there preferably being provided in each bearing segment, in the axial sliding surface, a first outlet opening, which has the form of an elongated slot extending in the radial direction and, as viewed in the direction of rotation, is arranged at the start of the axial sliding surface, and there being arranged in each bearing segment, in the radial sliding surface, a second outlet opening, which has the form of an elongated slot extending in the axial direction and, as viewed in the direction of rotation, is arranged at the start of the radial sliding surface. The outlet openings of each bearing segment are preferably connected to a common oil feed bore via connecting ducts.
The mounting according to the invention is simplified further and is distinguished by reduced friction losses if, according to another advantageous refinement, the rotor has a rotor shaft, if a running ring surrounding the rotor shaft concentrically is fixed to the rotor shaft, with which ring the rotor slides on the axial sliding surfaces of the combined radial and axial bearing, and if the rotor with the rotor shaft itself slides on the radial sliding surfaces of the combined radial and axial bearing.
BRIEF EXPLANATION OF THE FIGURES
The invention is to be explained in more detail in the following text by using examplary embodiments in conjunction with the drawing, in which figure 1 shows a mounting of a rotor of a vertical hydrogenerator with separate radial and axial bearing according to the prior art in a simplified, partially longitudinally sectioned illustration;
figure 2 shows a mounting with combined radial and axial bearing according to a preferred exemplary embodiment of the invention in an illustration comparable with figure l; and figure 3 shows an individual bearing segment of the mounting shown in figure 2, in which lubricating oil is specifically supplied to the sliding surfaces within the bearing segment, in a perspective view in the radial direction.
PREFERRED EMBODIMENTS OF THE INVENTION
A mounting with combined radial and axial bearing according to a preferred exemplary embodiment of the invention is reproduced in figure 2 in an illustration comparable with figure 1. Identical parts are largely designated by the same designations here. The rotating machine 10 rotates with a rotor, of which part of the rotor shaft 12 is shown in figure 2, about the vertical axis of rotation 11. Fixed to the rotor shaft 12 via a flange 13 is a running ring 14, which is used exclusively for the axial mounting. In terms of its axial thickness, it can therefore be reduced considerably as compared with the running ring 14' from figure 1.
The rotor slides with the running ring 14 on the upper, axial (horizontal) sliding surface 24 of a combined radial and axial bearing 21 (assembled from bearing segments), which is in turn supported in the axial direction by an axial support 23. The combined radial and axial bearing 21 is extended toward the rotor shaft 12 in the radial direction to such an extent that a radial (vertical) sliding surface 25 can be formed, on which the rotor shaft 12 is guided. The combined radial and axial bearing 21 is supported in the radial direction by a radial support 22 for this purpose.
Since the radial sliding surface 25 is located very much further in than the radial sliding surface I9 in the known bearing from figure 1, at the same rotational speed the result is a very much lower circumferential speed, which leads to lower friction losses and therefore lower heating.
The combined radial and axial bearing 21 preferably comprises individual bearing segments 26 according to figure 3, which have the form of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation 11 or rotor shaft 12.
An axial sliding surface 24 and a radial sliding surface 25 are formed on each of the bearing segments 26. Each of the bearing segments 26 has its own radial I5 support 22, whose force introduction surface is indicated in figure 3 by a circle.
The combined radial and axial bearing 21 can in principle be arranged in an oil bath. However, means 29,..,32 for supplying lubricating oil are preferably provided in the bearing segments 26 according to figure 3, the lubricating oil emerging onto the sliding surfaces 24, 25 through outlet openings 27, 28 in the axial and radial sliding surfaces 24 and 25. In the axial sliding surfaces 24, the means comprise a first outlet opening 27, which has the form of an elongated slot extending in the radial direction and, as viewed in the direction of rotation, is arranged at the start of the axial sliding surface 24. The lubricating oil emerging through the slot is in this way distributed in the form of a lubricating film on the sliding surface 24 by the bearing ring 14 sliding over the sliding surface 24. In an analogous way, in the radial sliding surface 25 there is provided a second outlet opening 28, which has the form of an elongated slot extending in the axial direction and, as viewed in the direction of rotation, is arranged at the start of the radial sliding surface 25.
The lubricating oil emerging from the outlet openings 27, 28 is led out from a rear connection 32 via a radial oil feed bore 31 arranged in the interior of the bearing segment 26 and is distributed to the outlet openings 27, 28 via connecting ducts 29, 30. In the comparatively long outlet opening 27, a plurality of connecting ducts 29 distributed over the length are provided.
The invention has been explained by using the example.
of a vertical hydrogenerator. It goes without saying that the use of the combined radial and axial bearing according to the invention is not restricted to hydrogenerators of this type.
Overall, the invention results in a combined radial and axial bearing which is specifically distinguished by the following advantages:
- The bearing needs less space in the axial direction. The entire machine can therefore be of lower construction.
- The radial bearing has a smaller radius toward the shaft. This means a lower circumferential speed and, as a result, lower friction losses.
- Overall, fewer bearing parts are needed.
LIST OF DESIGNATIONS
10, 10' Rotating machine (e. g. hydrogenerator) 11 Axis of rotation 12 Rotor shaft 13 Flange 14, 19' Running ring 15 Radial bearing (guide bearing) 16 Support (radial bearing) 17 Axial bearing (supporting bearing) 18 Support (axial bearing) 19 Sliding surface (radial bearing) 20 Sliding surface (axial bearing) 21 Combined radial and axial bearing 22 Radial support 23 Axial support 24 Axial sliding surface 25 Radial sliding surface 26 Bearing segment 27 Outlet opening (axial sliding surface) 28 Outlet opening (radial siding surface) 29, 30 Connecting duct 31 Oil feed bore 32 Connection
Claims (8)
1. A bearing for the rotor of a rotating machine (10), in particular a hydrogenerator rotating about a vertical axis of rotation (11), which bearing is formed as a sliding bearing and comprises a first means (21, 24) for axial mounting and a second means (21, 25) for radial mounting, characterized in that the first and second means are combined to form a combined radial and axial bearing (21), which has axial sliding surfaces (24) and radial sliding surfaces (25) at the same time.
2. The bearing as claimed in claim 1, characterized in that the combined radial and axial bearing (21) comprises a plurality of individual bearing segments (26), which have the form of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation (11), and in that an axial sliding surface (24) and a radial sliding surface (25) are formed on each of the bearing segments (26).
3. The bearing as claimed in claim 2, characterized in that each bearing segment (26) has its own radial support (22).
4. The bearing as claimed in one of claims 1 to 3, characterized in that the combined radial and axial bearing (21) is arranged in an oil bath.
5. The bearing as claimed in either of claims 2 and 3, characterized in that means (29,..,32) for supplying lubricating oil are provided in the bearing segments (26), which lubricating oil emerges onto the sliding surfaces (24, 25) through outlet openings (27, 28) in the axial and radial sliding surfaces (24, 25).
6. The bearing as claimed in claim 5, characterized in that, in each bearing segment (26), in the axial sliding surface (24), there is provided a first outlet opening (27), which has the form of an elongated slot extending in the radial direction and, as viewed in the direction of rotation, is arranged at the start of the axial sliding surface (24) , and in that in each bearing segment (26), in the radial sliding surface (25), there is provided a second outlet opening (28), which has the form of an elongated slot extending in the axial direction and, as viewed in the direction of rotation, is arranged at the start of the radial sliding surface (25).
7. The bearing as claimed in claim 6, characterized in that the outlet openings (27, 28) of each bearing segment (26) are connected to a common oil feed bore (31) via connecting ducts (29, 30).
8. The bearing as claimed in one of claims 1 to 7, characterized in that the rotor has a rotor shaft (12), in that a running ring (14) surrounding the rotor shaft (12) concentrically is fixed to the rotor shaft (12), with which ring the rotor slides on the axial sliding surfaces (24) of the combined radial and axial bearing (21), and in that the rotor with the rotor shaft (12) itself slides on the radial sliding surfaces (25) of the combined radial and axial bearing (21).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH10432002 | 2002-06-19 | ||
| CH20021043/02 | 2002-06-19 | ||
| PCT/IB2003/002364 WO2004001241A1 (en) | 2002-06-19 | 2003-06-06 | Bearing for the rotor of a rotating machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2489699A1 true CA2489699A1 (en) | 2003-12-31 |
Family
ID=29783960
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002489699A Abandoned CA2489699A1 (en) | 2002-06-19 | 2003-06-06 | Bearing for the rotor of a rotating machine |
Country Status (10)
| Country | Link |
|---|---|
| EP (1) | EP1514033B1 (en) |
| CN (1) | CN100460696C (en) |
| AT (1) | ATE389120T1 (en) |
| AU (1) | AU2003233114A1 (en) |
| BR (1) | BR0312431A (en) |
| CA (1) | CA2489699A1 (en) |
| DE (1) | DE50309372D1 (en) |
| ES (1) | ES2301796T3 (en) |
| RU (1) | RU2319045C2 (en) |
| WO (1) | WO2004001241A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE202009014649U1 (en) | 2009-10-29 | 2010-02-25 | Alstom Technology Ltd. | Plain bearing for the rotor of a rotating machine, in particular a hydrogenerator, and suitable for such a bearing bearing segment |
| DE102011013692B4 (en) * | 2011-03-11 | 2015-06-18 | Voith Patent Gmbh | Bearing arrangement for receiving the axial thrust of a shaft |
| EP3276191B1 (en) | 2016-07-28 | 2020-11-11 | GE Renewable Technologies | Hydrodynamic bearing pad construction |
| WO2019106404A1 (en) | 2017-12-01 | 2019-06-06 | Ge Renewable Technologies | Bearing pad for a hydro-generating unit and hydro-generating unit with such a bearing pad |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2901297A (en) * | 1956-07-16 | 1959-08-25 | Gen Electric | Bearings |
| US3583778A (en) * | 1968-10-03 | 1971-06-08 | Hideo Mori | Combination thrust-radial bearing |
| CH651362A5 (en) * | 1983-08-31 | 1985-09-13 | Bbc Brown Boveri & Cie | SELF-PUMPING HYDRODYNAMIC SLIDING BEARING. |
| FR2608700B1 (en) * | 1986-12-23 | 1989-04-28 | Graffenstaden Engrenages | COMBINED RADIAL AND AXIAL PAD BEARING |
| DK169927B1 (en) * | 1992-02-19 | 1995-04-03 | Man B & W Diesel Gmbh | Piston engine with a Michell-type thrust bearing |
| US5626470A (en) * | 1996-04-10 | 1997-05-06 | Ingersoll-Rand Company | Method for providing lubricant to thrust bearing |
| DE19641673B4 (en) * | 1996-10-11 | 2005-09-01 | Abb Turbo Systems Ag | axial plain |
| US6017184A (en) * | 1997-08-06 | 2000-01-25 | Allied Signal Inc. | Turbocharger integrated bearing system |
-
2003
- 2003-06-06 BR BR0312431-2A patent/BR0312431A/en not_active IP Right Cessation
- 2003-06-06 EP EP03727866A patent/EP1514033B1/en not_active Expired - Lifetime
- 2003-06-06 CA CA002489699A patent/CA2489699A1/en not_active Abandoned
- 2003-06-06 AT AT03727866T patent/ATE389120T1/en not_active IP Right Cessation
- 2003-06-06 DE DE50309372T patent/DE50309372D1/en not_active Expired - Lifetime
- 2003-06-06 WO PCT/IB2003/002364 patent/WO2004001241A1/en active IP Right Grant
- 2003-06-06 AU AU2003233114A patent/AU2003233114A1/en not_active Abandoned
- 2003-06-06 RU RU2005101078/11A patent/RU2319045C2/en not_active IP Right Cessation
- 2003-06-06 CN CNB038197936A patent/CN100460696C/en not_active Expired - Fee Related
- 2003-06-06 ES ES03727866T patent/ES2301796T3/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP1514033A1 (en) | 2005-03-16 |
| RU2319045C2 (en) | 2008-03-10 |
| WO2004001241A1 (en) | 2003-12-31 |
| ES2301796T3 (en) | 2008-07-01 |
| BR0312431A (en) | 2005-04-19 |
| RU2005101078A (en) | 2006-01-20 |
| DE50309372D1 (en) | 2008-04-24 |
| ATE389120T1 (en) | 2008-03-15 |
| CN100460696C (en) | 2009-02-11 |
| AU2003233114A1 (en) | 2004-01-06 |
| EP1514033B1 (en) | 2008-03-12 |
| CN1675476A (en) | 2005-09-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |