CN118056078A - Rotor support unit for a wind energy plant and method for adjusting a preload in a rotor support unit - Google Patents
Rotor support unit for a wind energy plant and method for adjusting a preload in a rotor support unit Download PDFInfo
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- CN118056078A CN118056078A CN202280063433.4A CN202280063433A CN118056078A CN 118056078 A CN118056078 A CN 118056078A CN 202280063433 A CN202280063433 A CN 202280063433A CN 118056078 A CN118056078 A CN 118056078A
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- rotor support
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- bearing ring
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- 230000036316 preload Effects 0.000 title claims description 16
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- 229910000831 Steel Inorganic materials 0.000 description 4
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Classifications
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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
- F16C19/38—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
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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
-
- 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
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
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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
- 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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- 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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- 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)
- Mounting Of Bearings Or Others (AREA)
Abstract
The invention relates to a rotor support unit for a wind energy plant (100), comprising: a sleeve-like inner connection (2) extending along a central axis (a); a sleeve-shaped external connection structure (3) coaxially arranged with the internal connection structure (2); and two tapered roller bearings (4, 5) which are arranged axially at a distance from one another and each have at least one inner bearing ring (6, 7 ') which is fastened to the inner connecting structure (2) and at least one outer bearing ring (8 ', 9 ') which is fastened to the outer connecting structure (3), wherein at least one radially extending fastening flange (10, 11, 12, 13) having an axial fastening surface (14) is formed on the inner connecting structure (2) and/or the outer connecting structure (3), and wherein the fastening flange (10, 11, 12, 13) corresponds to one of the bearing rings (6, 7', 8', 9 '), which bearing ring has a first perforated circle (16), and the bearing ring (6, 7', 8', 9 ') which corresponds to the fastening flange (10, 11, 12, 13) is screwed onto the axial fastening surface (14) of the fastening flange (10, 11, 12, 13) by means of the first perforated circle when introducing an axial pretension into the rotor support unit (1), and a method for adjusting an axial pretension in such a rotor support unit.
Description
Technical Field
The invention relates to a rotor support unit for a wind energy plant according to the preamble of claim 1 and to a method for adjusting an axial preload in a rotor support unit according to the preamble of claim 13.
Background
The rotor support of a wind power plant serves on the one hand to transmit power torques from a rotating hub to a generator arranged in the nacelle. In this case, the torque is transmitted either directly from the hub to the generator (in the case of a so-called direct drive) or from the hub to the transmission, which is connected in-between as a torque-to-rotational speed converter. On the other hand, the rotor bearing must be designed such that the reaction forces and reaction moments occurring can be conducted out into the foundation of the wind energy installation via the rotor support and the stationary components of the wind energy installation.
Depending on the design of the wind power plant, the rotor support is designed with a rotating outer ring or with a rotating inner ring, to which the hub is connected. The nacelle of the wind energy plant is connected to a respective further stationary ring of the rotor support. Grease-lubricated and oil-lubricated bearing devices with and without water cooling are known.
In order to meet the requirements for a rotor support device, two forms of rotor support device are basically known. In the so-called torque support known from WO 2012/136632 A1, for example, the rotor is supported by a single large rolling bearing. In this embodiment, the large rolling bearings are usually designed either as a multi-row roller rotary connection or as double-cone roller bearings, which are suitable for withstanding both the forces and moments that occur, because of their design. However, in order to ensure a sufficient bending stiffness for absorbing the torques that occur via the single bearing point, a particularly large-sized bearing ring, in particular a bearing ring having a high radial ring thickness, is required. The transport and the assembly of the rotor support in the field is correspondingly difficult. The bearing ring is usually case hardened only in the region of the raceways of the rolling bodies. The required high radial ring thickness can be used to introduce a hole circle on which the bearing ring is directly screwed to the coupling structure of the hub or nacelle, respectively.
An alternative embodiment of the rotor bearing device comprises at least two large rolling bearings which are axially spaced apart from one another, the outer bearing ring and the inner bearing ring of which are each connected to one another by a connecting structure. As rolling bearings, for example, existing tapered roller bearings or fixed-floating bearings can be used. The bending moment introduced into the rotor support is transmitted via the load-side rolling bearing as a fulcrum and the coupled connection to the rolling bearing facing away from the load. The connection acts like a lever, converting the applied torque into a force that acts radially and/or axially on the bearing facing away from the load. The advantage of this support solution known as a so-called double-point support or multi-point support is that a sufficiently high bending strength is achieved with the relatively small radial dimensions of the rolling bearing used. In such bearing arrangements, surface-hardened rolling-element bearing steel is generally used for the bearing ring and an iron casting is used for the connection structure, onto or into which the bearing ring is mounted with a press fit. The bearing ring is installed in this case in a costly manner by heat shrinking onto or into the corresponding connection structure. Disassembly of the bearing ring can only be achieved with great effort and requires the use of, for example, pressurized oil. However, the disassembly of the bearing ring carries the risk of damaging the bearing housing and thus the entire rotor support unit. In general, in the event of shrinkage of the rolling bearing ring into the connecting structure, which is usually constructed as a cast part, the force transmission is subject to wear, drop and cracking.
In order to avoid complex installation of the bearing ring in the field by shrinkage, it is known, for example, from EP 2,710,271b 1 to implement a two-point bearing arrangement in the installed rotor bearing unit, which is referred to here as a stator unit or a rolling bearing connection of the rotor unit, which has a flange for connection to the machine carrier or the hub of the wind energy installation, respectively. Disadvantageously, in this type of construction, problems often occur due to so-called ring migration and due to axial pretension variations of the rotor support unit.
Ring migration is a phenomenon that occurs in rings installed in press-fit under high running forces and moments, and more strongly with large bearing diameters. The bending up (Aufwel lung) of the bearing ring causes a local weakening of the press fit and a local displacement of the bearing ring relative to the corresponding connection. By ring migration, wear and corrosion in the mating joint is promoted, thereby exacerbating the problem itself over time. This can eventually lead to bearing damage or failure of the entire rotor support unit. One known measure for reducing ring migration is to enlarge the cross section of the bearing ring in order to be able to generate a greater pressing force in the mating joint. However, due to the maximum available radial installation space, which is mostly predefined by the wind power plant manufacturer, the radial ring cross section can only be increased at the expense of the diameter and/or length of the rollers used as rolling bodies, which leads to a reduction in the service life of the rotor bearing unit, in particular due to an increase in the number of rolling steps.
In the known rotor support units, the axial pretension is a value which is important and should be adjusted sufficiently precisely. If the axial preload is too small or if axial play occurs, the rotor support unit loses bending stiffness, which can lead to impacts, axial pushing and tilting under different wind loads, as a result of which subsequent components, such as the transmission or the generator, are subjected to higher loads and have an adverse effect on their service life and efficiency. Excessive pretensioning adversely affects the loading of the bearing components and the connection and furthermore leads to increased bearing friction.
In the solution disclosed by EP 2 710 271 B1, the axial pretension is introduced by a bearing clamping ring screwed to the stator unit onto a bearing ring mounted on the stator unit. This adjustment of the preload is, on the one hand, imprecise and prone to errors, since the locally generated axial preload is dependent on the corresponding radial pressing forces present in the press fit of the bearing ring with the stator unit. Furthermore, it is prone to change during operation due to the drop phenomenon (Setzerscheinung). The phenomenon of descent in the compression of the bearing clamping ring may result in a reduction of the axial pretension. Furthermore, the known method of introducing an axial pretension by means of a pretensioning ring has the disadvantage that the pretension achieved can generally only be determined computationally by the geometry of the individual components. The resulting pretension can only be determined inaccurately by the accumulation of component tolerances. A sufficiently accurate control measurement in the installed state is likewise not possible.
Disclosure of Invention
The object of the present invention is therefore to provide a rotor support unit for a wind power plant and a method for adjusting an axial pretension in such a rotor support unit, by means of which the accuracy of the axial pretension adjustment is improved, the drop phenomenon is reduced and the maintenance requirements are reduced, and the service life of the rotor support unit is increased.
This object is solved by a rotor support unit having the features of claim 1.
Hereby, a rotor support unit for a wind power plant is provided, comprising a sleeve-like inner connection structure extending along a central axis. The rotor bearing unit further comprises a sleeve-shaped outer connection which is arranged coaxially to the inner connection and two tapered roller bearings which are arranged axially at a distance from one another and each have at least one inner bearing ring which is fastened to the inner connection and at least one outer bearing ring which is fastened to the outer connection. At least one radially extending fastening flange having an axial fastening surface is formed on the inner and/or outer connecting structure. According to the invention, the fastening flange corresponds to one of the bearing rings, which has a first bore circle. In this case, the bearing ring corresponding to the fastening flange is screwed onto the axial fastening surface of the fastening flange by means of a hole circle, with the axial pretension being introduced into the rotor support unit.
In the rotor support unit according to the invention, the inner and outer connection forms a pretension circle with the two tapered roller bearings, which pretension circle is closed by fitting a bearing ring corresponding to the fastening flange. The axial threaded connection of the bearing ring simultaneously achieves a fixation of the bearing ring on the connection structure and introduces an axial pretension predetermined by an undersize between the inner and outer connection structure. By means of the same axial direction of action of the fixing force and the pretensioning force of the bearing ring, the predetermined axial pretensioning can be adjusted precisely without being influenced by radially acting fixing forces, which occur, for example, when the bearing ring is fixed using a press fit. A ready-to-install (einbaufertig) rotor support unit with preloaded tapered roller bearings is thereby produced, which is designed for the highest cyclic stresses.
Furthermore, the screw-threaded assembly of the bearing ring is advantageous, since the mechanical fixing of the bearing ring prevents the ring from migrating, so that ring migration is reliably avoided even under the highest loads. As a result, by the assembly of the rotor support unit according to the invention, corrosion at the fixing surface of the bearing ring and the resulting adjustment of the axial pretension is reduced, whereby the maintenance requirements of the rotor support unit are reduced and the service life is prolonged.
Preferably, the threaded connection is designed to completely transmit forces and moments acting on the threaded connection of the tapered roller bearing of the threaded connection of the bearing ring during operation of the wind energy installation. The screw connection is thus located in the force flow of the rotor support unit for guiding out the operating forces of the wind energy installation into the tower or foundation of the wind energy installation. Preferably, the threaded connection forms a single fastening of the bearing ring to the corresponding connection structure, as a result of which a particularly simple assembly or disassembly of the bearing ring is possible.
In a preferred embodiment, the fastening flange is arranged on an axial end of the corresponding connection structure and the connection structure ends with an axial fastening surface in the axial direction. In this case, the connection corresponding to the threaded bearing ring ends on the radial flange, so that the connection in particular does not have a section that surrounds or supports the bearing ring in the radial direction. The connecting structure is mostly formed as a cast part, and therefore has a particularly simple geometry, which only has to be finished to a certain size in the region of the flat fastening surface. Furthermore, the structural height of the rotor bearing unit in the region of the tapered roller bearing is reduced in the radial direction to the radial dimension of the bearing ring. The structural height disadvantage that arises from the thickening of the ring for providing the first bore circle can thus be compensated for by the elimination of the section of the connecting structure surrounding the threaded bearing ring. Furthermore, with the same structural height, larger rollers can be used as rolling bodies in order to optimize the service life of the rotor support unit. The rotor support unit is characterized by a particularly high static and dynamic load-bearing capacity, which is advantageous in particular for large hubs.
Preferably, the bearing ring of the tapered roller bearing has an inner diameter of more than 3 meters and particularly preferably an inner diameter of more than 5 meters.
Furthermore, the fastening flange is preferably arranged on the side of the connection structure that faces radially away from the respective other connection structure. By this arrangement of the fixing flange, the assembly of the threaded bearing ring is facilitated. Furthermore, these embodiments of the rotor support unit can have a particularly small radial structural height, wherein the sleeve-shaped inner or outer connection has a larger inner diameter or a smaller outer diameter than the inner ring or the outer ring of the tapered roller bearing. The sleeve-shaped base body of the connecting structure preferably extends as an axial support between the bearing rings within the height of their radial structure.
For adjusting the predetermined axial pretension, the fastening surface of the fastening flange can be dimensioned and the bearing ring can be screwed directly against it. Alternatively, a matching ring may be inserted in the threaded connection between the fixing flange and the bearing ring for adjusting the axial pretension of the rotor support unit. This has the advantage that during installation and/or in the event of a drop phenomenon, the matching of the axial pretension can be achieved by exchanging or reworking the matching ring during operation without having to completely disassemble the rotor support unit.
In some embodiments, the tapered roller bearings are arranged in an O-shaped arrangement, the inner connecting structure is designed with at least one fastening flange which is screwed to an inner bearing ring of one of the two tapered roller bearings, and the remaining bearing rings are fastened to the respective connecting structure by means of a press fit. In this bearing arrangement, the bearing ring is arranged on an inner bearing ring in a screw connection in a pretensioning circuit formed by the bearing and the connection, the pretensioning circuit being closed by the inner bearing ring after the installation of the remaining components. This design combines the advantage of a small radial design of the shrink bearing ring with a simple and precise adjustment of the axial pretension by the threaded connection of the last to be assembled, screwed bearing ring. Alternatively, an X-shaped arrangement of the tapered roller bearing is also conceivable, wherein then at least one of the outer rings is screwed to the external connection in the manner according to the invention.
In a further embodiment, the tapered roller bearings are arranged in an O-shaped arrangement, the inner connecting structure is designed with two fastening flanges which are screwed to the inner bearing rings of the two tapered roller bearings, and the outer bearing rings are fastened in the outer connecting structure by means of a press fit. Alternatively, an X-shaped arrangement of the tapered roller bearing is conceivable, wherein the two outer rings are screwed with the outer connection in the manner according to the invention.
In a further embodiment, the inner connection and the outer connection are each designed with two fastening flanges, to which the inner bearing ring and the outer bearing ring of the two tapered roller bearings are screwed. The two bearing rings of the two tapered roller bearings are thus screwed to the connecting structure, and the complex, narrow-tolerance machining of the mating surfaces for the press fit and the assembly of the bearing rings by press fit, for example by heat shrinkage, can be dispensed with entirely. This enables a simple mounting and dismounting of the bearing ring, if necessary also in the field.
Another advantage when using at least one, preferably two, fully threaded tapered roller bearings is the modular design. The connection structure and the tapered roller bearing are connected to each other by means of a bore circle as a standardized interface and can be selected separately from each other in a manner adapted to the respective application. In the further development of the rotor support unit, it is furthermore not necessary to create a new casting model for the connection structure, even if a change occurs in the bearing ring used, as long as the hole circle remains unchanged. Thus, bearings with different bearing angles, longer rollers, larger diameters, etc. can be used in a simple manner without changing the connection structure. In contrast, by using a longer or shorter connecting structure, the bearing distance can be matched in the case of identical tapered roller bearings. Thus, a precondition for a simple construction of a modular building block system for different turbine types is given.
Preferably, the bearing ring screwed to the inner or outer connection has an additional hole circle for fastening the rotor support unit in the wind power plant. In order to introduce additional hole circles, the threaded bearing ring has an increased radial structural height which stiffens the bearing ring and increases the bending stiffness of the rotor support unit.
The object is furthermore achieved by a wind power plant having a tower, a nacelle fixed to the tower and a rotor fixed to the nacelle, wherein the rotor is rotatably supported on the nacelle via a rotor support unit according to the invention. The rotor support unit according to the invention can in particular be provided as a ready-to-install unit and be installed in a wind power plant by screwing with the nacelle and the rotor.
In a preferred embodiment, the nacelle and the rotor each have a coupling structure for mounting the rotor support unit, and the rotor support unit is fixed to the nacelle and/or to the rotor by means of a threaded connection of the fixing flange with the corresponding bearing ring. The bolts of the threaded connection extend here through the fastening flange, the bearing ring and the fastening holes in the respective coupling structure. The threaded connection of the bearing ring on the connection structure thus serves in this case at the same time for fixing the rotor support unit on the corresponding coupling structure. The threaded connection thus transmits not only the operating forces in the rotor support unit, but also simultaneously provides a force transmission into the adjacent components of the wind energy installation.
In some embodiments, the nacelle and the rotor have coupling structures for mounting the rotor support unit, and the rotor support unit is fixed to the nacelle and/or to the rotor by means of a second threaded connection of the respective coupling structures on a second bore circle of a bearing ring that is screwed to the connection structure.
In terms of method, this object is achieved by a method for adjusting an axial preload in a rotor support unit according to the invention, wherein the axial preload of the rotor support unit is determined and, if there is a deviation from the setpoint range, is adjusted to the setpoint range by installing at least one matching ring in the threaded connection between the fastening flange and the bearing ring or by reworking the fastening surface. Since the axial fastening surface of the fastening flange not only forms an anchor point for the bearing ring, but also affects the axial pretension of the rotor support unit by its axial positioning, the axial pretension of the bearing unit can be adjusted by simple reworking of the fastening surface and/or insertion of a matching ring. The matching ring can be selected, for example, from a group of prefabricated matching rings having different thicknesses or can be combined as a ring assembly from a group of prefabricated matching rings. This saves reworking and results in time savings in the scope of assembly.
In the partially assembled state of the rotor support unit, it is preferably provided that the preload is determined by measuring the axial distance of the two reference surfaces before the final screwed bearing ring to be assembled is assembled. The reference surface is arranged on the fastening flange and on the already mounted further bearing ring of the tapered roller bearing, which is formed by the bearing ring being screwed in. By measuring the partially installed rotor support unit, the axial pretension can be determined particularly accurately, since tolerances do not have to be taken into account computationally, but rather the actual value of the partially installed rotor support unit can be used. In particular, the fact that the connection structure, which is usually produced as a cast part, is produced with significantly greater tolerances than the bearing ring to be screwed in last, takes into account the great majority of the factors that influence the axial pretension when measured in the partially assembled state.
Alternatively or additionally, the axial pretension in the assembled state of the rotor support unit can be registered by a measuring roller which is inserted as a rolling element into one of the tapered roller bearings in dependence on the circumferential angle of the tapered roller bearing. The measuring rollers used as rolling bodies are designed to detect the load of the measuring rollers in the bearing in a position-dependent manner. When the rotor support unit is measured in the unloaded state, an uneven axial preload can be deduced from the change in the measured value during one revolution. During application to a wind energy installation, a time-dependent change in the measured value, in particular at the same location, can indicate a change in the axial preload that occurs during operation, which may require a readjustment of the axial preload.
Alternatively or additionally, the axial pretension can be determined over time by means of differential measurement with the aid of strain gauges and/or measuring shims on the threaded connection in the assembled state of the rotor support unit.
Further advantageous embodiments can be seen from the following description and the dependent claims.
The invention is explained in detail below with the aid of an embodiment shown in the drawings.
Drawings
Fig. 1 schematically shows a wind power plant according to the invention, the rotor of which is rotatably supported on a nacelle via a rotor support unit according to the invention,
Fig. 2 shows schematically a first embodiment of a rotor support unit according to the invention with two tapered roller bearings, wherein one of the inner bearing rings is screwed with the inner connecting structure with the insertion of the matching ring,
Fig. 3 schematically shows a second embodiment of the rotor support unit according to the invention, wherein the inner and outer bearing rings of the tapered roller bearing are screwed with corresponding inner or outer connection structures respectively,
Fig. 4 schematically shows a third embodiment of the rotor support unit according to the invention, wherein the bearing rings of the interiors of two tapered roller bearings are screwed with an internal connection,
Fig. 5 shows schematically a variant of the embodiment according to fig. 3, in which the bearing ring screwed to the external connection has an additional hole circle for fastening to the coupling structure of the wind energy installation.
Detailed Description
In the different figures, identical components are provided with identical reference numerals throughout the various views and are therefore also generally named or referred to only once, respectively.
Fig. 1 shows a wind power installation 100 having a tower 110, a nacelle 120 fastened to the tower 110, and a rotor 130 fastened to the nacelle 120. The rotor 130 is rotatably supported on the nacelle 120 via the rotor support unit 1 according to the invention, as it is described in detail below in relation to the embodiment shown in fig. 2 to 5.
Fig. 2 shows a first exemplary embodiment of a rotor support unit 1 according to the invention for a wind power plant 100 (see fig. 1). The rotor bearing unit 1 comprises a sleeve-shaped inner connection 2 extending along a central axis a, a sleeve-shaped outer connection 3 arranged coaxially to the inner connection 2, and two tapered roller bearings 4, 5 arranged axially at a distance from one another, each having at least one inner bearing ring 6, 7' fastened to the inner connection 2 and at least one outer bearing ring 8', 9' fastened to the outer connection 3. A radially extending fastening flange 10 with an axial fastening surface 14 is formed on the inner connecting structure 2. The fastening flange 10 corresponds to one bearing ring 6 of the bearing rings 6, 7', 8', 9', which has a first bore circle 16. Through this hole circle 16, the bearing ring 6 corresponding to the fastening flange 10 is screwed onto the axial fastening surface 14 of the fastening flange 10 with the introduction of an axial preload into the rotor support unit 1.
The tapered roller bearings 4, 5 are provided in an O-shaped arrangement in fig. 2. The inner connecting structure 2 is formed with a fastening flange 10 which is screwed to the inner bearing ring 6 of one 4 of the two tapered roller bearings, and the remaining bearing rings 7', 8', 9' are fastened to the respective connecting structure 2, 3 by means of a press fit. If only one bearing ring is screwed to the corresponding connection in the rotor support unit 1, the windward bearing ring on the fixed connection is preferably selected for the screwed connection, since it is particularly susceptible to ring migration by experience. In a preferred O-shaped arrangement of the tapered roller bearing, this is the inner ring 6 on the windward side.
The bearing ring 6, like all the bearing rings 6, 7, 8, 9 of the screw connection described in the context of the present disclosure, is preferably made of induction-hardenable rolling bearing steel, for example 42CrMo4, and has an induction-hardened bearing raceway for the rolling elements 22. On the contracted bearing rings 7', 8', 9', the bearing raceways together with the entire surface are usually case hardened. The induction hardening of the raceways in this case leads to hardening deformations which can no longer be tolerated due to the small ring cross section. The use of induction-hardenable rolling bearing steel for the threaded bearing rings 6, 7, 8, 9 has the advantage of better workability, whereby, for example, the hole circles 16 can be introduced more simply. The induction-hardenable rolling bearing steel, in particular 42CrMo4, has both high static and dynamic strength and high notched impact strength, so that high cycle strength can be achieved in the bearing region of the rotor bearing unit 1.
The threaded connection of the bearing ring 6 is designed to completely transmit forces and torques acting on the threaded bearing ring 6 during operation of the wind power plant 100 (see fig. 1) via the tapered roller bearing 4 of the threaded bearing ring 6.
As shown in fig. 2, the fastening flange 10 is preferably arranged on one axial end of the corresponding connection structure 2 and the connection structure 2 ends in the axial direction with an axial fastening surface 14.
The fastening flange 10 is preferably arranged on the side of the connection 2 facing radially away from the respective other connection 3. The fastening flange on the inner connecting structure 2 therefore preferably extends radially inwards, and the fastening flange on the outer connecting structure 3 preferably extends radially outwards.
As also shown in fig. 2, a matching ring 15 can be inserted in the threaded connection between the fastening flange 10 and the bearing ring 6 for adjusting the axial pretension of the rotor support unit 1.
The internal and/or external connection structures 2, 3 may additionally have functional attachments 27. In this case, for example, a flange for connection to the rotor of the generator or to the transmission input on the rotary connection of the rotor support unit can be provided. The other functional attachment can be, for example, a fastening device, by means of which the external and internal connection structures can be mechanically prevented from moving relative to one another.
Fig. 3 shows a second exemplary embodiment of a rotor support unit 1 according to the invention. In this exemplary embodiment, the inner connection 2 and the outer connection 3 are each formed with two fastening flanges 10, 11; 12. 13. The inner bearing rings 6, 7 and the outer bearing rings 8, 9 of the two tapered roller bearings 4, 5 are screwed to the fastening flanges 10, 11; 12. 13.
In a wind energy installation 100 (see fig. 1) whose nacelle 120 and rotor 130 each have a coupling 160, 170 for mounting a rotor support unit 1, the rotor support unit 1 can be fastened to the nacelle 120 and/or the rotor 130 by means of a threaded connection of the fastening flange 11, 12 to the corresponding bearing ring 7, 8, wherein the bolts 18 of the threaded connection extend through the fastening flange 11, 12, the bearing ring 7, 8 and the fastening holes 19 in the respective coupling 160, 170. By fixing the bearing ring to the connection and coupling structure using the same threaded connection 21, radial space and manufacturing costs are saved.
By using only threaded bearing rings 6, 7, 8, 9, the geometry of the connection structure 2,3 is simplified in this embodiment. By means of an axial screw connection, the inner and outer ring stacks are formed by two bearing rings and an inner or outer connecting structure 2,3 arranged therebetween. The simple casting model for the connection 2,3 can thus be combined with standard bearings or also with sealed bearings ready for installation, whereby the development of new-generation turbines can be effected more quickly. Furthermore, the axial dimensions of the connecting structures 2,3 are reduced to the region between the tapered roller bearings 4, 5, which brings advantages in terms of manufacturing, logistics, assembly and quality of the cast component. All bearing rings 6, 7, 8, 9 can be assembled and disassembled simply without jeopardizing the rotor support unit 1. Again, rings or coupling structures made of any material may be used on both sides of the bearing ring. In order to prevent radial misalignment of the bearing ring in the threaded connection, the axial ring contact surface can be sprayed and/or coated in order to increase the coefficient of friction.
Furthermore, these embodiments apply correspondingly to the first example.
Fig. 4 shows a third embodiment of the rotor support unit according to the invention, in which the tapered roller bearings 4, 5 are provided in an O-shaped arrangement, the inner connecting structure 2 is designed with two fastening flanges 10, 11 which are screwed to the inner bearing rings 6, 7 of the two tapered roller bearings 4, 5, and the outer bearing rings 8', 9' are fastened in the outer connecting structure 3 by means of a press fit.
Furthermore, these embodiments apply correspondingly to the first and second examples.
Fig. 5 shows a variant of the second embodiment, in which the bearing ring 8, which is screwed to the outer connection 3, has a second hole circle 17 for fastening the rotor support unit 1 in the wind power plant 100 (see fig. 1). In the case shown, the second hole circle 17 serves to fix the rotor support unit 1 to the coupling structure 160 of the hub 150. However, depending on the position of the threaded bearing rings 6, 7, 8, 9 in the rotor support unit and the type of wind energy installation, the second hole circle 17 can also be provided on the threaded bearing rings 6, 7 inside the threaded connection and/or for fastening to a further connecting structure 170.
By way of a variant shown in fig. 5, a wind energy installation 100 with a rotor support unit 1 is achieved in which the nacelle 120 and the rotor 130 each have a coupling 160, 170 for mounting the rotor support unit 1, and the rotor support unit 1 is fastened to the nacelle 120 and/or the rotor 130 by means of a second threaded connection 20 of the respective coupling 160, 170 on a second eyelet 17 of the bearing ring 8 which is screwed to the connection 3.
The separate second hole circle 17 for connection with the coupling structures 160, 170 provides advantages in particular with regard to flexibility in designing the coupling structures 160, 170, since the rotor support unit 1 can be more simply adapted to a given hole circle of the coupling structures 160, 170. Furthermore, the assembly of the rotor support unit 1 can be simplified by the individual hole circles 17 and the guidance of the force flow under operating load can be optimized.
In the O-shaped arrangement of the tapered roller bearings 4, 5 shown in fig. 2 to 5, the assembly of the rotor supporting unit is performed in the following steps:
First, the bearing rings 7 or 7', 8 or 8' and 9 or 9' are fastened to the respective connection structures 2, 3. For this purpose, the bearing rings 7', 8', 9', if present, which are to be fixed by press fit, are first fitted to the associated connection structure 2, 3 by heat shrink. For the correct axial positioning of the bearing rings, shoulders are provided on the connecting structures 2, 3, which shoulders form mechanical stops for the bearing rings 7', 8', 9 '. The mechanical stops are positioned on the sides of the bearing rings 7', 8', 9', respectively, so that they can absorb the forces acting on the bearing rings 7', 8', 9' under axial pretension. The shrink-on or shrink-back bearing rings 7', 8', 9', respectively, are additionally secured by a securing ring 26.
The remaining bearing rings 7, 8, 9 are screwed to the corresponding flanges 11, 12, 13 of the associated connecting structure 2, 3. For this purpose, the bolts pass through the hole circles 16 of the bearing rings 7, 8, 9 and the holes in the fastening flanges 11, 12, 13. If the threaded connection should be used simultaneously for fixing the rotor support unit 1 to the coupling structures 160, 170 of the hub 150 or the nacelle 120, a smaller number of mounting bolts can be used first from the factory, which are then replaced in the field by the bolts 18 when the rotor support unit 1 is assembled in a wind energy installation. Separate holes (not shown) may also be provided in the bearing ring and the connection structure for the mounting bolts.
Subsequently, the connection structures 2, 3 and the mounted bearing rings 7, 8, 9 are introduced into each other and into the rolling bodies 22 of the rolling bearing 5.
The axial pretension in the rotor support unit 1 is now set by determining the axial pretension of the rotor support unit 1 and, in the event of a deviation from the setpoint range, setting the matching ring 15 in the final threaded connection 21 between the fastening flange 10 and the bearing ring 6 or by reworking the fastening surface 14 into the setpoint range.
In the partially installed state of the rotor support unit 1, an axial preload is determined by measuring the axial distance D between the two reference surfaces F1, F2, which are provided on the fastening flange 10 and the already installed further bearing ring 8 of the tapered roller bearing 4, which is formed by the installation of the threaded bearing ring 6, before the installation of the last threaded bearing ring 6 to be installed. In this case, the pretension-in the case of an O-arrangement of the tapered roller bearing-results from an insufficient axial dimension of the inner part 2, 6, 7 of the rotor support unit 1 relative to the outer part 3, 8, 9, which remains taking into account the geometry of the bearing ring 6 to be assembled last.
Preferably, the reference surface F1 is formed by a fixing surface 14 on the fixing flange 10 corresponding to the bearing ring 6 to be finally mounted, and the reference surface F2 is one of the end surfaces of the other bearing ring 8. Furthermore, the distance D of the reference surfaces F1, F2 is preferably measured at a plurality of points distributed over the circumference of the rotor support unit 1 or also continuously over the circumference. The fastening surface 14 can be reworked or the matching ring 15 can be produced accordingly, depending on the location.
After the reworking of the fastening surface 14 and/or the insertion of the matching ring 15, the rotor support unit 1 can be finally assembled by installing the final bearing ring 6.
After final assembly and/or during operation, the axial pretension in the rotor support unit 1 can also be monitored and readjusted if necessary. For this purpose, preferably, in the assembled state of the rotor support unit 1, the axial pretension can be registered by the measuring rollers 23 which are inserted as rolling elements 22 into one of the tapered roller bearings 4, 5 in association with the circumferential angle of the tapered roller bearings 4, 5.
Alternatively or additionally, in the assembled state of the rotor support unit 1, the axial pretension is determined by means of a differential measurement over time by means of strain gauges 24 and/or measuring shims 25 on the threaded connection. For this purpose, at least one reference measurement under load is recorded after the rotor support unit has been installed in the wind power plant 100. Later measurements under similar load conditions may then be compared to the reference measurements. If the deviation exceeds the maximum allowable value, a readjustment/readjustment of the axial pretension is performed.
All the embodiments shown in the figures can also be implemented with an X-shaped arrangement of tapered roller bearings within the knowledge of a person skilled in the art. In the X-arrangement, the bearing ring to be assembled last, which is screwed, is fixed to the external connection.
Furthermore, the person skilled in the art knows that the solution presented in the figures can be used not only for internally rotating rotor support units with grease lubrication or oil lubrication, but also for externally rotating rotor support units. For this purpose, a suitable sealing system is provided on the tapered roller bearing of the rotor support unit.
Description of the reference numerals
1. Rotor support unit
2. Internal connection structure
3. External connection structure
4. 5 Conical roller bearing
6.7, 7' Inner bearing ring
8. 8', 9' Outer bearing ring
10. 11, 12, 13 Fixing flange
14. Fixing surface
15. Matching ring
16. First hole circle
17. Second hole circle
18. Bolt
19. Fixing hole
20. 21 Screw connection
22. Rolling element
23. Measuring roller
24. Strain gauge
25. Measuring pad
26. Fixing ring
27. Functional accessory
100. Wind energy plant
110. Tower column
120. Nacelle
130. Rotor
140. Rotor blade
150. Hub
160. Hub connection structure
170. Nacelle connection structure
Axis of rotor support unit
D spacing
F1, F2 reference plane.
Claims (16)
1. Rotor support unit for a wind energy plant (100), comprising
A sleeve-shaped inner connecting structure (2) extending along a central axis (A),
A sleeve-shaped outer connection (3) arranged coaxially to the inner connection (2), and
Two tapered roller bearings (4, 5) arranged axially at a distance from each other, each having at least one inner bearing ring (6, 7 ') fastened to the inner connecting structure (2) and at least one outer bearing ring (8, 8', 9 ') fastened to the outer connecting structure (3),
Wherein at least one radially extending fastening flange (10, 11, 12, 13) having an axial fastening surface (14) is formed on the inner connection structure (2) and/or the outer connection structure (3),
It is characterized in that the method comprises the steps of,
The fastening flange (10, 11, 12, 13) corresponds to one of the bearing rings (6, 7, 8, 9) and has a first bore circle (16), by means of which the bearing ring (6, 7, 8, 9) corresponding to the fastening flange (10, 11, 12, 13) is screwed onto an axial fastening surface (14) of the fastening flange (10, 11, 12, 13) when an axial preload is introduced into the rotor support unit (1).
2. Rotor support unit according to claim 1, characterized in that the threaded connection is designed for completely transmitting forces and moments acting on the threaded connection of the bearing rings (6, 7, 8, 9) by means of tapered roller bearings (4, 5) of the threaded connection of the bearing rings (6, 7, 8, 9) during operation of the wind power plant (100).
3. Rotor support unit according to claim 1 or 2, characterized in that the fixing flange (10, 11;12, 13) is arranged on the axial end of the corresponding connection structure (2; 3) and the connection structure (2; 3) ends in the axial direction with the axial fixing surface (14).
4.A rotor support unit according to any one of claims 1 to 3, characterized in that the fixing flange (10, 11, 12, 13) is arranged on the connection structure (2; 3) on a side radially facing away from the respective other connection structure (3; 2).
5. Rotor support unit according to any one of claims 1 to 4, characterized in that a matching ring (15) is inserted in the threaded connection between the fixing flange (10, 11, 12, 13) and the bearing ring (6; 7;8; 9) for adjusting the axial pretension of the rotor support unit (1).
6. Rotor support unit according to one of claims 1 to 5, characterized in that the tapered roller bearings (4, 5) are arranged in an O-shaped arrangement, the inner connecting structure (2) is configured with at least one fixing flange (10, 11) which is screwed with an inner bearing ring (6; 7) of one (4; 5) of the two tapered roller bearings, and the remaining bearing rings (7; 6, 8, 9) are fixed on the respective corresponding connecting structure (2, 3) by means of a press fit.
7. Rotor support unit according to one of claims 1 to 6, characterized in that the tapered roller bearings (4, 5) are arranged in an O-shaped arrangement, the inner connecting structure (2) is configured with two fixing flanges (10, 11) which are screwed with the inner bearing rings (6, 7) of the two tapered roller bearings (4, 5), and the outer bearing rings (8, 9) are fixed in the outer connecting structure (3) by means of a press fit.
8. Rotor support unit according to one of claims 1 to 6, characterized in that the inner connection structure (2) and the outer connection structure (3) are each configured with two fastening flanges (10, 11;12, 13) on which the inner bearing rings (6, 7) and the outer bearing rings (8, 9) of the two tapered roller bearings (4, 5) are screwed.
9. The rotor support unit according to any of claims 1 to 8, characterized in that a bearing ring (6, 7;8, 9) which is screwed with the inner connection structure (2) or the outer connection structure (3) has a second hole circle (17) for fixing the rotor support unit (1) in a wind energy plant (100).
10. Wind power plant with a tower (110), a nacelle (120) fixed to the tower and a rotor (130) fixed to the nacelle (120), characterized in that the rotor (130) is rotatably supported on the nacelle (120) via a rotor support unit (1) according to any of claims 1 to 9.
11. Wind power plant according to claim 10, characterized in that the nacelle (120) and the rotor (130) have coupling structures (160, 170) for mounting the rotor support unit (1), and that the rotor support unit (1) is fixed on the nacelle (120) and/or the rotor (130) by means of a threaded connection of a fixing flange (10, 11, 12, 13) with a corresponding bearing ring (6, 7, 8, 9), wherein the threaded connection bolts (18) extend through the fixing flange (10, 11, 12, 13), the bearing ring (6, 7, 8, 9) and the fixing holes (19) in the respective coupling structures (160, 170).
12. Wind power plant according to claim 10, having a rotor support unit (1) according to claim 9, characterized in that the nacelle (120) and the rotor (130) have coupling structures (150, 160) for mounting the rotor support unit (1), and that the rotor support unit (1) is fixed on the nacelle (120) and/or the rotor (130) by means of the respective coupling structures (160, 170) on a second threaded connection (20) on a second eyelet (17) of a bearing ring (6, 7, 8, 9) which is screwed with the connection structure (2, 3).
13. Method for adjusting an axial pretension in a rotor support unit (1) according to any one of claims 1 to 9, characterized in that an axial pretension of the rotor support unit (1) is determined and is adjusted into the nominal range by installing at least one matching ring (15) in a threaded connection (21) between a fixing flange (10, 11, 12, 13) and a bearing ring (6, 7, 8, 9) or by reworking a fixing surface (14) when deviating from the nominal range.
14. Method according to claim 13, characterized in that, in the partially assembled state of the rotor support unit (1), the pretension is determined by measuring the axial distance (D) of two reference surfaces (F1, F2) which are arranged on the fastening flange (10, 11, 12, 13) and the already assembled further bearing ring (7, 6, 9, 8) of the tapered roller bearing (4, 5) formed by the mounting of the threaded bearing ring (6, 7, 8, 9) before the mounting of the last to be assembled, threaded bearing ring (6, 7, 8, 9).
15. Method according to claim 13 or 14, characterized in that in the assembled state of the rotor support unit (1), an axial preload is recorded in association with the circumferential angle of the tapered roller bearing (4, 5) by a measuring roller (23) introduced as a rolling element (22) into one of the tapered roller bearings (4, 5).
16. Method according to any of claims 13 to 15, characterized in that in the assembled state of the rotor support unit (1) the axial pretension is determined over time by means of differential measurement by means of strain gauges (24) and/or measuring shims (25) on the threaded connection.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102021210436.3A DE102021210436A1 (en) | 2021-09-20 | 2021-09-20 | Rotor bearing unit for a wind turbine and method for adjusting the preload in a rotor bearing unit |
| BEBE2021/5740 | 2021-09-20 | ||
| DE102021210436.3 | 2021-09-20 | ||
| PCT/EP2022/075934 WO2023041772A1 (en) | 2021-09-20 | 2022-09-19 | Rotor bearing unit for a wind turbine and method for setting the preload in a rotor bearing unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN118056078A true CN118056078A (en) | 2024-05-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202280063433.4A Pending CN118056078A (en) | 2021-09-20 | 2022-09-19 | Rotor support unit for a wind energy plant and method for adjusting a preload in a rotor support unit |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN118056078A (en) |
| DE (1) | DE102021210436A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116542072B (en) * | 2023-06-05 | 2023-10-03 | 北京航空航天大学 | Rotor connection structure deformation analysis method based on bolt assembly moment change |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2694832B1 (en) | 2011-04-05 | 2017-05-31 | ThyssenKrupp Rothe Erde GmbH | Oil-lubricated anti-friction bearing |
| WO2013113487A1 (en) | 2012-02-02 | 2013-08-08 | Eolotec Gmbh | Bearing unit, in particular for a wind turbine |
-
2021
- 2021-09-20 DE DE102021210436.3A patent/DE102021210436A1/en active Pending
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2022
- 2022-09-19 CN CN202280063433.4A patent/CN118056078A/en active Pending
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| DE102021210436A1 (en) | 2023-03-23 |
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