WO2015090786A1 - Wellen-lager-baugruppe für ein windkraft-getriebe - Google Patents
Wellen-lager-baugruppe für ein windkraft-getriebe Download PDFInfo
- Publication number
- WO2015090786A1 WO2015090786A1 PCT/EP2014/074824 EP2014074824W WO2015090786A1 WO 2015090786 A1 WO2015090786 A1 WO 2015090786A1 EP 2014074824 W EP2014074824 W EP 2014074824W WO 2015090786 A1 WO2015090786 A1 WO 2015090786A1
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- WIPO (PCT)
- Prior art keywords
- shaft
- bearing
- rolling bearing
- spacer
- lock
- Prior art date
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Classifications
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- 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
- F03D15/00—Transmission of mechanical power
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- 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
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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
- 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
- F16C19/36—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 a single row of rollers
- F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
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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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller 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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H57/022—Adjustment of gear shafts or 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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2230/00—Manufacture
- F05B2230/60—Assembly methods
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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
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
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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
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
- F05B2240/54—Radial bearings
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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
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/60—Shafts
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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
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/403—Transmission of power through the shape of the drive components
- F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
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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
- F16C2229/00—Setting preload
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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
- F16C2360/31—Wind motors
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H2057/0216—Intermediate shaft supports, e.g. by using a partition wall
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H57/022—Adjustment of gear shafts or bearings
- F16H2057/0221—Axial adjustment
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H57/022—Adjustment of gear shafts or bearings
- F16H2057/0227—Assembly method measuring first tolerances or position and selecting mating parts accordingly, e.g. special sized shims for transmission bearings
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- 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
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- 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
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/50—Manufacturing or production processes characterised by the final manufactured product
Definitions
- the present invention relates to a shaft bearing assembly for a wind power transmission and a method for mounting rolling bearings on a shaft of a wind power transmission.
- shafts are supported by bearings so that the shafts can rotate.
- a movement of the bearing must be prevented axially to the shaft. Another important requirement is that the bearing clearance can be set accurately.
- a pair of bearings e.g. 1 shows a first mechanism for adjusting a bearing arrangement with tapered roller bearings in a mirror-image back-to-back arrangement (O arrangement), in which case a first tapered roller bearing 1 is shown at one end of a shaft 2 and a second tapered roller bearing 3 at the other end of the shaft 2.
- the bearing clearance is adjusted by means of a locknut 4.
- the locknut 4 is positioned on the side of the second tapered roller bearing 3 farthest from the first tapered roller bearing 1
- the locknut 4 fixes the position and thus the bearing clearance of the tapered roller bearing 3, since the inner race 5 of the second tapered roller bearing 3 is not positioned against the shaft 2 or another part in a pressing manner Repeatability of the exact bearing clearance adjustment, as the Position of the bearing inner ring 5 is not fixed and depends on the mounting of the lock nut 4.
- FIG. 1 Another known method for adjusting the bearing clearance is illustrated in FIG.
- a lock nut 4 and a spacer 6 are used with the lock nut 4 positioned on the side of the second tapered roller bearing 3 farthest from the first tapered roller bearing 1.
- the Spacer 6 is located on the other side of the tapered roller bearing 3 and between a collar 7 of the shaft 2 and the inner ring 5 of the second tapered roller bearing 3.
- a regrinding of the spacer 6 to the correct width can lead to a precise and repeatable bearing clearance adjustment.
- the position of the inner ring 5 of the bearing 3 is defined by the collar 7 of the shaft 2 and the spacer 6.
- the bearing 3 To correct the width of the spacer by regrinding, the bearing 3 must be dismantled to get to the spacer 6. This makes the process time consuming and therefore more expensive.
- An object of the invention is to provide an alternative shaft bearing assembly and an alternative method of mounting multiple bearings on a shaft.
- it may be an object of the invention to provide a shaft bearing assembly or a method for mounting bearings on a shaft, which allows easier adjustment of the bearing clearance
- the object can be achieved by a shaft bearing assembly for a wind power transmission, wherein the shaft bearing assembly comprises at least one shaft, these at least one shaft by means of a first rolling bearing, preferably a tapered roller bearing, and a second rolling bearing, preferably a tapered roller bearing, is mounted, wherein the first rolling bearing is axially fixed and the second rolling bearing is secured with a lock, and wherein
- the lock is located on the side of the second rolling bearing, which faces away from the first rolling bearing, and
- the lock has a first contact surface on which the inner ring of the rolling bearing is supported, and a second contact surface which is connected to an abutment on the shaft.
- the locking of the second rolling bearing can be arranged on the side facing away from the first rolling bearing of the second rolling bearing.
- the shaft bearing assembly are not decomposed, in particular, the second roller bearing does not have to be removed from the shaft.
- the first contact surface and the second contact surface are on the same side of the detent, i. on the side of the lock facing the bearing.
- the first rolling bearing is preferably fixed axially by securing an inner ring of the first bearing on the shaft against displacement in an axial direction facing away from the second rolling bearing.
- an outer ring of the first rolling bearing is secured against displacement in a direction facing the second bearing in a component of the wind power transmission, for example in the gearbox housing.
- the rolling elements of the first rolling bearing then secure the inner ring of the first rolling bearing against displacement in the direction facing the second bearing and the outer ring of the first rolling bearing against displacement in the direction away from the second rolling bearing.
- the securing of the second roller bearing by the lock preferably causes an axial fixation of the second rolling bearing, wherein an inner ring of the second bearing is secured on the shaft against displacement in an axial direction facing away from the first rolling bearing.
- An outer ring of the second rolling bearing is secured against displacement in a direction facing the first bearing in the above-mentioned component of the wind power transmission.
- the rolling elements of the second rolling bearing then secure the inner ring of the second rolling bearing against displacement in the direction facing the first bearing and the outer ring of the second rolling bearing against displacement in the direction away from the first rolling bearing.
- the component of the wind power transmission secures the outer race of the first bearing against displacement in the axial direction facing the second rolling bearing and the outer race of the second rolling bearing against displacement in the direction facing the first rolling bearing.
- the abutment is part of the shaft and has the function of securing the locking in the axial direction, in particular in a direction facing the first bearing and the second bearing.
- a contact surface may be formed as an abutment on which the second contact surface, in particular in the axial direction, is supported.
- the first contact surface, the second contact surface and the contact surface formed as abutment are preferably aligned radially, i. are orthogonal to the rotational or symmetry axis of the shaft.
- the lock may comprise a spacer and a locking member, which are designed according to embodiments of the invention as a single component, i. the lock is made in one piece, or according to other embodiments of the invention are designed as two different parts.
- the spacer may be located between the rolling bearing and the locking member.
- An advantage of a shaft bearing assembly of the present invention is that the bearing clearance can be repeatedly accurately adjusted. Furthermore, whenever it is necessary during assembly, you can regrind the spacer without having to disassemble the shaft or the bearing; only the lock must be removed. In addition, you can adjust the bearing clearance from the side of the second rolling bearing, which is furthest away from the first rolling bearing.
- the fixing device e.g. an end plate or a circlip, which fixes the first rolling bearing, must not be accessible for mounting or dismounting the locking member.
- the locking member may be a nut or end plate or other suitable locking member known to a person skilled in the art.
- the first contact surface may be formed between the spacer and the inner ring of the rolling bearing.
- the second contact surface may be formed between the locking member and the shaft collar according to embodiments of the invention. According to other statements Formations of the invention may be the second contact surface between the spacer and the shaft collar.
- the shaft in the shaft bearing assembly may be a high speed shaft, a low speed shaft and / or an intermediate shaft.
- the first bearing is pushed onto the shaft and fixed axially.
- the inner ring of the first rolling bearing is fixed in relation to a displacement in the axial direction facing away from the second rolling bearing.
- the first rolling bearing is used in the component of the wind power transmission. This can be done after the first rolling bearing has been pushed onto the shaft and fixed in the axial direction.
- the component of the wind power transmission ensures the axial fixation of the shaft.
- the component of the wind power transmission fixes the outer ring of the first rolling bearing against a displacement in the direction facing the second rolling bearing.
- the second rolling bearing is pushed onto the shaft.
- the second rolling bearing is introduced into the component of the wind power transmission.
- the component of the wind power transmission is designed so that it axially fixes the second rolling bearing as well as the first rolling bearing.
- the component of the wind power transmission secures the outer ring of the second rolling bearing against displacement in the direction of the first rolling bearing.
- the lock is then applied to the shaft. This secures the inner ring of the second bearing against displacement in the direction away from the first bearing direction.
- the lock is applied as far as the shaft, as in the Arreit ist is screwed onto the shaft until the second contact surface comes into contact with the abutment.
- the lock is initially selected so that the shaft has a large axial play after the lock has been applied. According to the invention this axial clearance is measured. Then the lock is removed. In order to achieve a desired axial play of the shaft or a defined preload of the bearings, the lock is now modified or replaced.
- the measured axial play of the shaft is used. It is thus possible to determine, based on the measured axial play of the shaft, a geometry of the lock which leads to the desired preload or the desired axial clearance.
- the second rolling bearing is secured with the modified or replaced Arreit ist so that sets the desired preload or the desired axial play.
- the procedure described has the advantage that the desired preload or the desired axial play can be adjusted independently of dimensional deviations of the components used.
- the existing dimensional deviations instead flow into the measured axial play of the shaft. This in turn forms the basis for determining the desired geometry of the lock. A compensation of the deviations takes place automatically in this way. Specific measures to take account of the deviations are not required.
- Fig. 1 and Fig. 2 illustrate shaft-bearing assemblies according to the prior
- FIGS. 3 and 4 illustrate a shaft bearing assembly according to one embodiment of the present invention.
- FIGS. 5 through 7 schematically illustrate possible implementations of a shaft bearing assembly according to various embodiments of the present invention.
- the present invention provides a shaft bearing assembly for a wind turbine transmission, in particular a parallel transmission stage of a wind turbine gearbox.
- the shaft-bearing assembly comprises at least one shaft, which is supported by two roller bearings, in particular tapered roller bearings.
- the rolling bearings may be arranged in a back-to-back (O-arrangement) position and are axially mounted with clearance on the at least one shaft.
- the shaft may have a tooth engagement point, and the rolling bearings may in particular be arranged so that in each case at least one rolling bearing on one side of the tooth engagement point and at least one second rolling bearing on the second side of the Meshing point is located.
- the one rolling bearing is axially fixed by a fixing device such as an end plate, a lock ring or other suitable means, and the second rolling bearing is secured with a lock.
- the lock is located on the side of the rolling bearing farthest from the other rolling bearing and has a first contact surface which contacts an inner ring of the rolling bearing and a second contact surface which contacts an abutment on the shaft.
- FIG. 3 illustrates a shaft bearing assembly 10 according to an embodiment of the present invention.
- the shaft 1 1 includes a tooth engagement point 12.
- the tooth engagement point is meant a location on the shaft which is provided with teeth for engagement with other teeth of another part of the transmission.
- the shaft 1 1 is mounted in two tapered roller bearings 13, 14, of which one is located on each side of the tooth engagement point 12.
- the tooth engagement point 12 on the shaft 1 1 is located between the two tapered roller bearings 13, 14, in which the shaft 1 1 is rotatably mounted.
- the tapered roller bearings 13, 14 are mounted in a mirror-image back-back arrangement, or in other words, in O arrangement.
- the tapered roller bearing 13 on one side of the meshing position 12 on the shaft 1 1 is axially fixed by a fixing device 15, in the example given by an end plate 15.
- the tapered roller bearing 14 on the other side of the tooth engagement point 12 on the shaft 1 1 is with a Lock 1 6 positioned or adjusted.
- the lock 1 6 is located on the side of the tapered roller bearing 14, which is farthest from the tapered roller bearing 13.
- the detent 16 has a first contact surface 17 which contacts an inner race 18 of the tapered roller bearing 14 and a second contact surface 19 which contacts an abutment 20 on the shaft 11 (see also FIG. 4, in which a detail of FIG is).
- An outer ring 21 of the bearing 14 is mounted adjacent to a part of the transmission housing 22.
- FIGS. 5 to 7 schematically illustrate some embodiments of the present invention.
- Fig. 5 schematically illustrates a first embodiment of the present invention.
- the lock 1 6 a spacer 23 and a locking member 24 include.
- the locking member 24 may be any suitable retaining member known to those skilled in the art, such as a lock nut or end plate.
- the spacer 23 and the locking member 24 may be designed according to the present invention as two separate parts.
- the locking member 24 has double contact according to embodiments of the present invention, or in other words, has two contact surfaces.
- One contact is to the bearing 14, and more specifically, to the inner ring 18 of the bearing 14, and another contact is to the abutment 20, i. to the collar 20 on the shaft 1 1.
- the lock 1 6 has a first contact surface 17, which contacts the inner ring 18 of the bearing 14 and is formed from one side of the spacer 23.
- the lock 16 also has a second contact surface 19 which contacts an abutment 20, in the example given a collar 20 on the shaft 1 1 and is formed by a part of the locking member 24.
- the collar 20 defines the end position of the locking member 24 and thus the position of the inner ring 18 of the bearing 14th
- the spacer 23 is located between the bearing 14, more specifically, the bearing inner ring 18 of the bearing 14 and the locking member 24th
- An advantage of a detent 16 according to embodiments of the invention is that, when the bearings 13, 14 are mounted on the shaft 11, the bearing clearance can be easily and accurately adjusted by mounting the detent 16 according to embodiments of the present invention becomes.
- a first tapered roller bearing 13 is first mounted on the shaft 1 1 at one end of the tooth engagement position 12.
- This first tapered roller bearing 13 is axially fixed by a fixing device 15, in the example given by an end plate 15.
- a second tapered roller bearing 14 is mounted on the other side of the tooth engagement position 12.
- the first and second tapered roller bearings 13, 14 are arranged axially with clearance on the shaft 1 1.
- the second tapered roller bearing 14 is then secured with a lock 1 6.
- the lock 1 6 is mounted on the farthest from the first tapered roller bearing 13 side of the second tapered roller bearing 14, and that such that it has a first contact surface 17, which contacts an inner ring 18 of the second tapered roller bearing 14, and a second contact surface 19, which contacts an abutment 20 of the shaft 1 1.
- the first contact surface 17 and the second contact surface 19 are located on the same side of the detent 16, ie on the side of the detent 16 which faces the tapered-roller bearing 14.
- a spacer 23 is first mounted with a certain width, preferably slightly smaller than the presumed width. After mounting the locking member 24, the game is measured. If it turns out that the bearing clearance adjustment is deficient, you can lock 1 6, i. the spacer 23 and the locking member 24, dismantle and a new spacer 23, now with the correct width, and then mount the locking member 24. It is an advantage of a detent 16 used in accordance with embodiments of the present invention that only the spacer 23 and the locking member 24 must be disassembled and the other parts, including the shaft 1 1 and the tapered roller bearings 13, 14, must not be disassembled you can exchange the spacer 23.
- FIG. Another embodiment of the invention is shown schematically in FIG. This embodiment is similar to that illustrated in FIG. 5.
- the spacer 23 and the locking member 24 are designed as a single component, while in the embodiment in Fig. 5, the spacer 23 and the locking member 24 are designed as two separate parts.
- the detent 16 can be mounted in a manner similar to that described for the previous embodiment, except that in the present embodiment, the spacer 23 and the detent member 24 are mounted and dismounted together because they are made of a single component. If the bearing clearance setting is poor, the lock 1 6 is also degraded in a similar manner and replaced by another lock 1 6 with the correct width.
- FIG. 7 schematically illustrates another embodiment of the invention. Similar to the embodiments described above, the detent 16 according to this embodiment also includes a spacer 23 and a locking member 24.
- the spacer 23 and the locking member 24 are designed as two separate parts, and the spacer 23 is located between the bearing 14, more precisely the inner ring 18 of the bearing 14, and the locking member 24.
- the spacer 23 may have an inverted L-shape.
- the spacer 23 consists of a first part having a first width and a second part having a second width, wherein the second width is narrower than the first width.
- the locking member 24 may, for. Example, a lock nut or an end plate or another, a person skilled in the known suitable locking member.
- the spacer 23 has double contact, namely a contact with the inner ring 18 of the bearing 14 and the other contact with the collar 20 on the shaft 1 1.
- the lock 1 6 has a first contact surface 17 which is formed by a part of the spacer 23, that is, the widest part or the part with the highest width, and touches the inner ring 18 of the bearing 14.
- the lock 1 6 also has a second contact surface 19 which is formed by another part of the spacer 23, ie the smallest part or by the part with the smallest width, and an abutment 20, in the present embodiment, a collar 20, on the shaft 1 1 touched.
- the first contact surface 17 and the second contact surface 19 are both on the same side of the lock 1 6, ie on the side of the lock 1 6, which faces the tapered roller bearing 14.
- an advantage of a lock 1 6 according to embodiments of the invention is that the bearing clearance can be easily and accurately adjusted.
- a detent 16 is mounted as described with reference to FIG.
- that side of the spacer 23, which the second contact surface 19 of the lock 1 6 forms, are reground to optimize the bearing clearance adjustment.
- An advantage of a shaft bearing assembly 10 according to embodiments of the present invention is that the bearing clearance can be repeatedly accurately adjusted.
- the shaft 1 1 may be a high-speed shaft, a low-speed shaft and / or an intermediate shaft 1 1 of a parallel transmission stage of a wind turbine transmission.
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)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201480068525.7A CN105829768A (zh) | 2013-12-18 | 2014-11-18 | 风力传动装置的轴轴承组件 |
KR1020167019029A KR20160098437A (ko) | 2013-12-18 | 2014-11-18 | 풍력 터빈 변속기용 샤프트-베어링-서브어셈블리 |
JP2016536233A JP2017500504A (ja) | 2013-12-18 | 2014-11-18 | 風力設備用歯車装置の軸/軸受アセンブリ |
EP14799161.6A EP3094887A1 (de) | 2013-12-18 | 2014-11-18 | Wellen-lager-baugruppe für ein windkraft-getriebe |
US15/104,060 US20160290475A1 (en) | 2013-12-18 | 2014-11-18 | Shaft-bearing subassembly for a wind turbine transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013226519.0 | 2013-12-18 | ||
DE102013226519.0A DE102013226519A1 (de) | 2013-12-18 | 2013-12-18 | Wellen-Lager-Baugruppe für ein Windkraft-Getriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015090786A1 true WO2015090786A1 (de) | 2015-06-25 |
Family
ID=51900882
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/074824 WO2015090786A1 (de) | 2013-12-18 | 2014-11-18 | Wellen-lager-baugruppe für ein windkraft-getriebe |
Country Status (7)
Country | Link |
---|---|
US (1) | US20160290475A1 (de) |
EP (1) | EP3094887A1 (de) |
JP (1) | JP2017500504A (de) |
KR (1) | KR20160098437A (de) |
CN (1) | CN105829768A (de) |
DE (1) | DE102013226519A1 (de) |
WO (1) | WO2015090786A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112272647B (zh) * | 2018-06-20 | 2022-03-15 | 三菱电机株式会社 | 曳引机的支承结构 |
CN110953254A (zh) * | 2018-09-27 | 2020-04-03 | 北京自动化控制设备研究所 | 一种轴向预紧可调舵机输出轴机构 |
DE102019100999A1 (de) * | 2019-01-16 | 2020-07-16 | Schaeffler Technologies AG & Co. KG | Lageranordnung zur angestellten Stützlagerung einer Welle mit einer Distanzringscheibe zur Einstellung des axialen Wellenspiels |
EP3739207A1 (de) * | 2019-05-16 | 2020-11-18 | Siemens Gamesa Renewable Energy A/S | Lageranordnung für eine windturbine sowie windturbine |
CN112524152B (zh) * | 2019-09-17 | 2023-05-09 | 福建金风科技有限公司 | 轴承游隙调整装置、方法及风力发电机组 |
EP3919768A1 (de) * | 2020-06-03 | 2021-12-08 | Flender GmbH | Anordnung, verfahren zur montage und simulation eines wälzlagers |
US20230392680A1 (en) | 2020-10-20 | 2023-12-07 | Sew-Eurodrive Gmbh & Co. Kg | Gearing having a housing and a shaft unit |
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GB1023637A (en) * | 1963-08-16 | 1966-03-23 | Fischer Ag Georg | Improvements in or relating to a bearing assembly for a rotatable spindle or shaft |
US3552812A (en) * | 1969-06-11 | 1971-01-05 | Textron Inc | Angular-contact bearing construction |
US20020133951A1 (en) * | 2000-10-10 | 2002-09-26 | Beduhn Mark W. | Rotary die cutter apparatus and method |
US20030066398A1 (en) * | 2001-10-04 | 2003-04-10 | Tuthill James C. | Spindle nut retainer |
WO2005005866A1 (en) * | 2003-07-02 | 2005-01-20 | The Timken Company | Transmission containing helical gearing and bearing arrangement therefor |
GB2421987A (en) * | 2005-01-10 | 2006-07-12 | Hansen Transmissions Int | Bearing assembly |
US20060175893A1 (en) * | 2005-02-08 | 2006-08-10 | Continental Conveyor & Equipment Company | Spindle and hub assembly |
DE102009040349A1 (de) * | 2009-08-05 | 2011-02-10 | Robert Bosch Gmbh | Fixierung großer Stirnräder auf Getriebewellen |
DE102009031320A1 (de) * | 2009-06-30 | 2011-03-03 | Siemens Aktiengesellschaft | Planetengetriebe |
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US4012154A (en) * | 1973-09-28 | 1977-03-15 | United Technologies Corporation | Threadless locking device |
ATE24227T1 (de) * | 1981-12-19 | 1986-12-15 | Hammond Eng Ltd | Befestigungsmittel. |
US5058424A (en) * | 1990-10-25 | 1991-10-22 | Navistar International Transportation Corp. | Wheel end play setting device |
US5402560A (en) * | 1993-10-29 | 1995-04-04 | Temper Corporation | Bearing setting apparatus |
US7090609B2 (en) * | 2003-08-08 | 2006-08-15 | Dana Corporation | Pinion support for a differential assembly |
CN101526068B (zh) * | 2008-03-04 | 2012-08-22 | 南京宇能仪表有限公司 | 一种组合式螺旋叶轮风力发电系统 |
WO2013152850A1 (de) * | 2012-04-13 | 2013-10-17 | Eolotec Gmbh | Lageranordnung sowie verfahren zur einstellung der vorspannung einer lageranordnung |
-
2013
- 2013-12-18 DE DE102013226519.0A patent/DE102013226519A1/de not_active Withdrawn
-
2014
- 2014-11-18 CN CN201480068525.7A patent/CN105829768A/zh active Pending
- 2014-11-18 US US15/104,060 patent/US20160290475A1/en not_active Abandoned
- 2014-11-18 WO PCT/EP2014/074824 patent/WO2015090786A1/de active Application Filing
- 2014-11-18 KR KR1020167019029A patent/KR20160098437A/ko not_active Application Discontinuation
- 2014-11-18 JP JP2016536233A patent/JP2017500504A/ja active Pending
- 2014-11-18 EP EP14799161.6A patent/EP3094887A1/de not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1023637A (en) * | 1963-08-16 | 1966-03-23 | Fischer Ag Georg | Improvements in or relating to a bearing assembly for a rotatable spindle or shaft |
US3552812A (en) * | 1969-06-11 | 1971-01-05 | Textron Inc | Angular-contact bearing construction |
US20020133951A1 (en) * | 2000-10-10 | 2002-09-26 | Beduhn Mark W. | Rotary die cutter apparatus and method |
US20030066398A1 (en) * | 2001-10-04 | 2003-04-10 | Tuthill James C. | Spindle nut retainer |
WO2005005866A1 (en) * | 2003-07-02 | 2005-01-20 | The Timken Company | Transmission containing helical gearing and bearing arrangement therefor |
GB2421987A (en) * | 2005-01-10 | 2006-07-12 | Hansen Transmissions Int | Bearing assembly |
US20060175893A1 (en) * | 2005-02-08 | 2006-08-10 | Continental Conveyor & Equipment Company | Spindle and hub assembly |
DE102009031320A1 (de) * | 2009-06-30 | 2011-03-03 | Siemens Aktiengesellschaft | Planetengetriebe |
DE102009040349A1 (de) * | 2009-08-05 | 2011-02-10 | Robert Bosch Gmbh | Fixierung großer Stirnräder auf Getriebewellen |
Also Published As
Publication number | Publication date |
---|---|
US20160290475A1 (en) | 2016-10-06 |
CN105829768A (zh) | 2016-08-03 |
JP2017500504A (ja) | 2017-01-05 |
DE102013226519A1 (de) | 2015-06-18 |
EP3094887A1 (de) | 2016-11-23 |
KR20160098437A (ko) | 2016-08-18 |
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