EP2414692A1 - Bearing assembly for rotatably supporting a machine element and method for fixing a tapered roller bearing to a machine element - Google Patents
Bearing assembly for rotatably supporting a machine element and method for fixing a tapered roller bearing to a machine elementInfo
- Publication number
- EP2414692A1 EP2414692A1 EP10713569A EP10713569A EP2414692A1 EP 2414692 A1 EP2414692 A1 EP 2414692A1 EP 10713569 A EP10713569 A EP 10713569A EP 10713569 A EP10713569 A EP 10713569A EP 2414692 A1 EP2414692 A1 EP 2414692A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- clamping device
- tapered roller
- roller bearing
- component
- elastically deformable
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
-
- 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
-
- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/063—Fixing them on the shaft
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/10—Application independent of particular apparatuses related to size
- F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
-
- 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
- F16C2360/31—Wind motors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the invention relates to a bearing assembly with a designed as a double-row tapered roller bearings large warehouse for rotatably supporting a machine part and with a clamping device for fixing the tapered roller bearing on the machine part. Furthermore, the invention relates to a wind turbine with such a bearing assembly and a method for fixing a tapered roller bearing on a machine part.
- bearing having an outer ring with a diameter of at least one meter.
- Other criteria and, in particular, other diameter values may also be used for the definition of large bearings.
- the invention has for its object to enable a mounting of a bearing assembly having a designed as a tapered roller bearing large stock, with a defined bias with little effort.
- the bearing assembly comprises a double-row tapered roller bearing for rotatably supporting a machine part and a clamping device for fixing the KegehOllenlagers on the machine part.
- the tapered roller bearing has an outer ring whose outer diameter is at least 1 meter, a first inner ring, a second inner ring disposed axially adjacent to the first inner ring, a set of conically shaped first rolling elements rolling between the outer ring and the first inner ring and a set of conically shaped second rolling elements, which are arranged axially adjacent to the first Wälzkörpem and roll between the outer ring and the second inner ring, on.
- the tensioning device has a rigid component and an elastically deformable component.
- the rigid component of the clamping device strikes axially on Machine part on.
- the elastically deformable component of the tensioning device is axially clamped and thereby axially deformed relative to a relaxed state.
- the elastically deformable component of the tensioning device is connected to the first inner ring of the tapered roller bearing with the second inner ring of the tapered roller bearing, with the rigid component of the clamping device or with the machine part.
- the invention has the advantage that it is ensured with relatively little effort that the axial preload of the tapered roller bearing is within a predetermined range.
- the elastically deformable component dimensional tolerances can be compensated for the components used. If the permitted dimensional tolerances are complied with for the components used, it is ensured that the axial preload of the tapered roller bearing is within the specified range. Individual adjustment or adjustment measures are not required.
- By connecting the elastically deformable component with an already existing component is also achieved that the number of components to be handled during assembly of the bearing assembly does not increase and accordingly the assembly can be performed quickly and efficiently.
- the bearing assembly according to the invention may in particular be designed so that the first inner ring abuts axially on the machine part or in cooperation with the machine part axially clamps the elastically deformable component of the clamping device and the second inner ring abuts axially against the rigid component of the clamping device or in cooperation with the rigid component the clamping device axially clamps the elastically deformable component of the clamping device
- the elastically deformable component of the clamping device can cohesively, in particular by vulcanization, with the first inner ring of the tapered roller bearing, with the second inner ring of the tapered roller bearing with the rigid component of Clamping device or is connected to the machine part.
- Such a compound can be produced with little effort and has sufficient strength.
- the elastically deformable component of the tensioning device is formed integrally with the first inner ring of the tapered roller bearing, with the second inner ring of the tapered roller bearing, with the rigid component of the tensioning device or with the machine part and is in particular made of the same material as the The first inner ring of the tapered roller bearing, the second inner ring of the tapered roller bearing, the rigid component of the clamping device or the machine part.
- This embodiment represents a particularly cost-effective implementation form with a long service life.
- the elastically deformable component of the tensioning device may have a reduced material thickness compared to the rigid component.
- the elastically deformable component of the tensioning device may be formed as a flange-like extension of the rigid component.
- Clamping device is designed as a circumferentially closed ring. As a result, the number of individual components can be kept low. Likewise, however, it is also possible for the rigid component and / or the elastically deformable component of the tensioning device to be segmented in the circumferential direction. As a result, the handling can be facilitated, especially in the case of very large bearing arrangements, and the installation effort can be reduced if accessibility is poor.
- the elastically deformable component of the clamping device for example, made of spring steel or plastic, in particular made of elastomeric material be. These materials are available inexpensively and elastically deformable over a sufficient deformation path.
- the machine part can be designed, for example, as a shaft connection part or a shaft
- the bearing assembly is formed as a component of a wind turbine.
- bearing arrangements are used with very large dimensions and it is a short assembly time desired.
- the assembly time can even be of paramount importance, since an assembly is possible only in favorable weather conditions.
- the invention further relates to a wind energy plant with a rotor which is fastened to a rotor shaft which is rotatably mounted in a bearing arrangement according to the invention.
- the invention relates to a method for fixing a tapered roller bearing, which has an outer diameter of at least 1 meter, by means of a clamping device comprising a rigid component and an elastically deformable
- Component has, on a machine part.
- the rigid component of the clamping device is axially approximated to the machine part until it abuts the machine part.
- the elastically deformable component of the tensioning device which is connected to the tapered roller bearing, the rigid component of the tensioning device or the machine part, axially deformed about a deformation path which is so large that the tapered roller bearing with an axial force which is a value between a predetermined Minimum value and a predetermined maximum value, is clamped axially between the rigid component of the clamping device and the machine part or a machine connected to the machine part fastening element. Since the rigid component of the tensioning device is approached axially to the machine part until it stops against the machine part and thus the correct axial preload of the tapered roller bearing is already set without further adjustment, the method according to the invention can be carried out very simply and quickly.
- the elastically deformable component of the tensioning device with respect to their elastic constant and their tolerances tolerances and the rigid component of the tensioning device, the machine part and the tapered roller bearing with respect to their permitted dimensional tolerances can be coordinated so that the product from within the approved Dimensional tolerances resulting mimmal axial deformation path and the elastic constant of the elastically deformable component of the clamping device at least the predetermined minimum value of the axial force corresponds.
- the elastically deformable component of the tensioning device with respect to their elastic constant and their permitted dimensional tolerances and the rigid component of the tensioning device, the machine part and the tapered roller bearing with respect to their allowable dimensional tolerances can be coordinated so that the product from within the approved Dimensional tolerances resulting maximum axial deformation path and the elastic constant of the elastically deformable component of the clamping device corresponds to a maximum of the predetermined maximum value of the axial force.
- Figure 2 shows another exemplary embodiment of the bearing assembly according to the invention in a schematic sectional view
- Figure 3 shows the exemplary embodiment shown in Figure 1 of the bearing assembly according to the invention during assembly in a sectional view.
- FIG. 1 shows an exemplary embodiment of an inventively designed bearing assembly in a schematic sectional view.
- the bearing assembly includes a double row Kegeh * olle bearing 1 and a tension apparatus 2 with which the Kegel ⁇ is> llenlager 1 fixed to a shaft connecting part.
- the shaft connection part 3 can be fastened, for example, to a rotor shaft (not shown in FIG. 1) that is driven by a rotor of a wind energy plant.
- the tapered roller bearing 1 has a rotation axis 4. Unless stated otherwise below, directions are in each case based on this axis of rotation 4 of the tapered roller bearing 1. An axial direction is thus a direction parallel to the axis of rotation 4 of the tapered roller bearing 1. A radial direction is a direction perpendicular to the axis of rotation 4 of the Kegerrollenlagers first
- the tapered roller bearing 1 has an outer ring 5 with two axially adjacent conical raceways, which together form a V-shaped profile.
- the outer ring 5 has an outer diameter of at least 1 meter and has axial holes 6, with the aid of the outer ring 5 can be attached to a non-figured housing.
- the tapered roller bearing 1 has two axially juxtaposed inner rings 7 and 8, each with a conical raceway.
- the inner ring 7 has an outer axial end surface 8 and the inner ring 9 has an outer axial end surface 10.
- the outer ring 5 and the two inner rings 7, 9 are formed in the illustrated embodiment as closed in the circumferential direction rings. In principle, it is also possible to use segmented rings.
- the rolling elements 11 are arranged in a cage 13, the rolling elements 12 in a cage 14.
- the cages 13, 14 may be segmented or formed closed in the circumferential direction.
- the individual cage segments can be lined up in the circumferential direction, as disclosed in DE 102 46 825 A1 and be made of plastic.
- the two inner rings 7, 9 are arranged on the shaft connection part 3 and rotatably connected to the shaft connection part 3.
- the shaft connecting part 3 has a shoulder 15 with an axial stop surface 16 against which the inner ring 7 axially abuts with its outer axial end surface 8.
- the shaft connection part 3 has an axial abutment surface 17 at its axial end opposite to the shoulder 15.
- the tensioning device 2 has a clamping ring 18 and an elastic ring 19.
- the clamping ring 18 is made, for example, of metal, in particular of steel, and has axial bores 20 and in the region of the axial bores 20 an axial stop surface 21 which abuts against the axial stop surface 17 of the shaft connection part 3.
- the elastic ring 19 is fixed to the axial side of the clamping ring 18, which faces the outer axial end surface 10 of the inner ring 9 of the tapered roller bearing 1 and has an axial end surface 22 which rests against the outer axial end surface 10 of the inner ring 9.
- the elastic ring 19 is made of an elastomer material and connected by vulcanization with the clamping ring 18.
- the clamping ring 18 and the elastic ring 19 are each closed in the circumferential direction.
- the clamping ring 18 and / or the elastic ring 19 may also be formed segmented.
- the elastic ring 19 is clamped axially between the inner ring 9 of the tapered roller bearing 1 and the clamping ring 18, since the inner ring 7 is prevented by the shoulder 15 of the shaft connection part 3 at a deflection in the axial direction and the clamping ring 18 is screwed by means of clamping screws 24 with the shaft connection part 3 , Compared to an undeformed state, the elastic ring is compressed in the axial direction by an axial deformation path x. On the inner ring 7, 9 of the tapered roller bearing 1 accordingly acts an axial force F, which is the greater, the stronger the elastic ring 19 is compressed axially, d. H. the larger the axial deformation path x is. Thus, the tapered roller bearing 1 is under an axial bias whose size corresponds to the axial force F.
- the elastic ring 19 has an elastic constant k
- the axial force F results:
- the axial deformation path x of the elastic ring 19 is limited by the fact that the clamping ring 18 abuts axially with its axial stop surface 21 against the axial stop surface 17 of the shaft connection part 3.
- An axial displacement of the clamping ring 18 up to this stop state can take place with the aid of the clamping screws 24, which are threaded axially through the axial bores 20 and screwed into the shaft connection part 3.
- the clamping screws 24 are fully tightened, so that the clamping ring 18 abuts axially against the shaft connection part 3.
- the axial deformation path x of the elastic ring 19 and thus the axial force F on the inner rings 7, 9 defined in principle exactly and accordingly the axial preload of the tapered roller bearing 1 exactly specified.
- the deformation path x of the elastic ring 19 in the assembled state is not always exactly the same value, but may within a range vary between a minimum value x min and a maximum value x max. Accordingly, the axial force F exerted on the inner rings 7, 9 can also vary between a minimum value F min and a maximum value F max.
- the minimum value x min for the axial deformation path x and thus the minimum value F_min for the axial force result for a first combination of maximum exhausted tolerances in the axial dimensions.
- the maximum value x max of the axial deformation path x and thus also the maximum value F max of the axial force F results.
- the axial deformation amount x increases with increasing axial distance a1 between the axial end surface 22 of the elastic ring 19 and the axial abutment surface 21 of the clamping ring 18 in the undeformed state of the elastic ring 19, with increasing axial distance a2 between the two axial abutments 16, 17 of the shaft connection part 3 from and with increasing axial distance a3 between the outer axial end surfaces 8, 10 of the inner rings 7, 9 to.
- the minimum value F min of the axial force results for a combination of the smallest permissible values for a 1 and a 3 and the largest permissible value for a 2.
- the maximum value F max of the axial force results for a combination of the largest permissible values for a 1 and a3 and the smallest permissible value for a2.
- the tolerances for the axial distances al, a2 and a3 and the elastic constant k of the elastic ring 19 are matched to one another such that the minimum value F min and the maximum value F max of the axial force F are just within the permissible range.
- the exemplary embodiment of the bearing arrangement according to the invention shown in FIG. 1 can be modified in many different ways, in particular with regard to the design of the tensioning device 2.
- the elastic ring 19 may be attached to the outer axial end surface 10 of the inner ring 9 of the tapered roller bearing 1.
- Figure 2 shows another embodiment of the inventive bearing arrangement in a schematic sectional view.
- the configuration of the tapered roller bearing 1 and the shaft connection part 3 completely coincide with the embodiment shown in Figure 1.
- the elastic ring 19 shown in FIG. 1 is omitted.
- the clamping ring 18 has a flange-like extension 23 which extends obliquely radially outwardly.
- the orientation of the flange-like extension 23 is selected such that it extends toward the inner ring 9 and bears against the outer axial end face 10 of the inner ring 9 under tension.
- the flange-like extension 23 is made of an elastic material, in particular of a spring steel.
- the flange-like extension 23 is formed integrally with the clamping ring 18 and has a smaller material thickness than the other areas of the clamping ring 18.
- the entire clamping ring 18 including the flange-like extension 23 can be made of the same material. However, it is possible, for example, by means of a suitable heat treatment to vary the hardness location-dependent. In particular, the clamping ring 18 in the region of the flange-like extension 23 may have increased hardness and elasticity. Furthermore, it is possible to form segmented the entire clamping ring 18 including the flange-like extension 23.
- the axial clamping of the tapered roller bearing 1 and the generation of a bias in the tapered roller bearing 1 takes place in an analogous manner, as described with reference to FIG.
- the statements there on the component tolerances and the axial deformation path x apply analogously, wherein the flange-like extension 23 analogous to the elastic ring 19 also has an elastic constant k and enters into the determination of the axial distance al an axial position, the maximum axial projection of the flange Extension 23 of the clamping ring 18 corresponds in the relaxed state.
- the tapered roller bearing 1 is axially pushed onto the shaft connection part 3 from the side axially opposite to the shoulder 15 until the outer axial end surface 8 of the inner ring 7 of the tapered roller bearing 1 abuts against the axial stop surface 16 of the shoulder 15 of the shaft connection part 3 strikes.
- the ball bearing roller 1 it may be necessary for the ball bearing roller 1 to be pressed onto the shaft connecting part 3 and / or for the inner rings 7, 9 to be heated be widened or the shaft connection part 3 is cooled.
- FIG. 3 shows the exemplary embodiment of the bearing assembly according to the invention shown in FIG. 1 during assembly in a sectional view.
- the clamping screws 24 are inserted into the axial bores 20 of the clamping ring 18 and tightened.
- the tensioning device 2 is brought closer to the tapered roller bearing 1 until the axial abutment surface 21 of the clamping ring 18 of the tensioning device 2 abuts axially against the axial abutment surface 17 of the shaft connection part 3.
- the elastic ring 19 of the clamping device 2 between the inner ring 9 of the tapered roller bearing 1 and the clamping ring 18 of the clamping device 2 is axially clamped and compressed to the axial deformation path x.
- the tapered roller bearing 1 is rotatably connected to the shaft connection part 3 and has an axial bias within a desired range.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009015827.8A DE102009015827B4 (en) | 2009-04-01 | 2009-04-01 | Bearing arrangement for rotatably supporting a machine part |
PCT/EP2010/002102 WO2010112229A1 (en) | 2009-04-01 | 2010-04-01 | Bearing assembly for rotatably supporting a machine element and method for fixing a tapered roller bearing to a machine element |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2414692A1 true EP2414692A1 (en) | 2012-02-08 |
Family
ID=42556999
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10713569A Withdrawn EP2414692A1 (en) | 2009-04-01 | 2010-04-01 | Bearing assembly for rotatably supporting a machine element and method for fixing a tapered roller bearing to a machine element |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2414692A1 (en) |
CN (1) | CN102449331B (en) |
DE (1) | DE102009015827B4 (en) |
WO (1) | WO2010112229A1 (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
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US20120070110A1 (en) * | 2010-09-21 | 2012-03-22 | Owens Steven J | Gearbox assembly component and method |
CN102182644B (en) * | 2011-01-24 | 2012-12-19 | 江苏兴盛风能科技有限公司 | Front stander rough casting of wind power generator set |
CN102518787A (en) * | 2011-12-13 | 2012-06-27 | 哈尔滨东安发动机(集团)有限公司 | Planetary transmission structure of wind power gear box |
CN104632883B (en) * | 2015-03-10 | 2017-02-01 | 洛阳新强联回转支承股份有限公司 | Three-row-roller type turntable bearing with axial pre-compression structure |
CN105508155B (en) * | 2015-12-31 | 2021-06-01 | 北京金风科创风电设备有限公司 | Wind generating set |
WO2018153418A1 (en) * | 2017-02-21 | 2018-08-30 | Vestas Wind Systems A/S | Wind turbine main rotor arrangement having means to prevent angular creep of outer bearing ring |
CN108223566B (en) * | 2018-02-05 | 2024-02-20 | 洛阳新强联回转支承股份有限公司 | Soft-belt-free large-cone-angle double-row tapered roller slewing bearing |
CN108194511A (en) * | 2018-03-06 | 2018-06-22 | 洛阳新强联回转支承股份有限公司 | A kind of retainer of double-row conical bearing |
DE102019100999A1 (en) * | 2019-01-16 | 2020-07-16 | Schaeffler Technologies AG & Co. KG | Bearing arrangement for the employed support bearing of a shaft with a spacer washer for adjusting the axial shaft play |
DE102020208956A1 (en) * | 2020-07-17 | 2022-01-20 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electromechanical brake pressure generator with spindle drive unit, braking system |
CN113251131B (en) * | 2021-05-19 | 2022-05-20 | 山东华成中德传动设备有限公司 | Preload adjusting method for tapered roller bearing of industrial gearbox |
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US4363527A (en) | 1980-12-29 | 1982-12-14 | Howard Thrasher | Split race bearing |
US4784438A (en) * | 1986-02-20 | 1988-11-15 | Fikse Tyman H | Tunneling machine rotatable member |
JPH0331442Y2 (en) * | 1987-10-28 | 1991-07-04 | ||
JPH0238713A (en) | 1988-07-28 | 1990-02-08 | Nippon Seiko Kk | Rolling bearing with clearance compensator |
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DE10256855A1 (en) | 2002-12-05 | 2004-06-17 | Ab Skf | Procedure for assembling a double row tapered roller bearing |
FR2868820B1 (en) * | 2004-04-09 | 2006-07-14 | Snr Roulements Sa | ROLLING BEARING MOUNTING INCORPORATING A MEANS OF REDUCING CONTACT CORROSION |
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JP2008202782A (en) | 2007-01-26 | 2008-09-04 | Jtekt Corp | Rolling bearing device |
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2009
- 2009-04-01 DE DE102009015827.8A patent/DE102009015827B4/en active Active
-
2010
- 2010-04-01 EP EP10713569A patent/EP2414692A1/en not_active Withdrawn
- 2010-04-01 CN CN201080023768.0A patent/CN102449331B/en active Active
- 2010-04-01 WO PCT/EP2010/002102 patent/WO2010112229A1/en active Application Filing
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CH265281A (en) * | 1947-02-08 | 1949-11-30 | Liechti Walter | Device for connecting an axle or shaft with a ball bearing. |
US2736617A (en) * | 1953-11-23 | 1956-02-28 | Lippmann Engineering Works | Roller bearing |
CH407666A (en) * | 1963-08-16 | 1966-02-15 | Fischer Ag Georg | Spindle bearings in roller bearings |
JP2003184873A (en) * | 2001-12-21 | 2003-07-03 | Koyo Seiko Co Ltd | Bearing equipment for automatic transmission |
JP2006002815A (en) * | 2004-06-16 | 2006-01-05 | Koyo Seiko Co Ltd | Bearing unit for rolling stock |
DE102007014010A1 (en) * | 2007-03-23 | 2008-09-25 | Schaeffler Kg | roller bearing |
Also Published As
Publication number | Publication date |
---|---|
CN102449331B (en) | 2014-11-26 |
DE102009015827A1 (en) | 2010-10-07 |
DE102009015827B4 (en) | 2023-11-02 |
CN102449331A (en) | 2012-05-09 |
WO2010112229A1 (en) | 2010-10-07 |
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