EP2153066A2 - Ensemble palier pour éolienne - Google Patents

Ensemble palier pour éolienne

Info

Publication number
EP2153066A2
EP2153066A2 EP08758987A EP08758987A EP2153066A2 EP 2153066 A2 EP2153066 A2 EP 2153066A2 EP 08758987 A EP08758987 A EP 08758987A EP 08758987 A EP08758987 A EP 08758987A EP 2153066 A2 EP2153066 A2 EP 2153066A2
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing block
block
arrangement according
lining
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08758987A
Other languages
German (de)
English (en)
Inventor
Georgios Pechlivanoglou
Jürgen Wagner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Suzlon Energy GmbH
Original Assignee
Suzion Energy GmbH
Suzlon Energy GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102007056763A external-priority patent/DE102007056763A1/de
Application filed by Suzion Energy GmbH, Suzlon Energy GmbH filed Critical Suzion Energy GmbH
Priority to EP08758987A priority Critical patent/EP2153066A2/fr
Publication of EP2153066A2 publication Critical patent/EP2153066A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts
    • 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
    • F05B2260/90—Braking
    • 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
    • F05B2260/90—Braking
    • F05B2260/902—Braking using frictional mechanical forces
    • 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
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/50—Intrinsic material properties or characteristics
    • F05B2280/501—Self lubricating materials; Solid lubricants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/14—Self lubricating materials; Solid lubricants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a bearing arrangement, in particular for a wind turbine, for the transmission of radial and axial forces, wherein two bearing partners are provided against each other about an axis rotatable.
  • the bearing partners each have a support surface, wherein a bearing block between the support surfaces is arranged inserted in order to produce a force acting on the support surfaces normal force.
  • the bearing block is non-rotatably connected to one of the bearing partners.
  • such bearing arrangements are arranged between the tower of the plant and the nacelle and serve, inter alia, for receiving and discharging thrust, gyro and yaw forces from the machine carrier 7 of the nacelle in the tower.
  • the wind tracking of the nacelle is made possible by means of the bearing assembly, the so-called azimuth bearing, and the azimuth drive.
  • the nacelle is rotated in the horizontal plane about a substantially vertical axis of rotation, so that the wind flows perpendicular to a rotational plane of the rotor, and thus the energy yield is maximized.
  • the azimuth bearing comprises a bearing ring, which is bolted firmly to the tower and is axially gripped by a bearing ring.
  • the bearing ring is firmly connected to the nacelle and rests on the bearing ring.
  • Between the bearing ring and the bearing ring sliding linings are provided, by means of which the bearing clearance and a bias between the two bearing partners are adjustable.
  • a spindle is provided, via which a radial position of the sliding lining can be defined.
  • the present bearing arrangement serves as a passive brake between the
  • the azimuth drives produce a torque which limits the torque between the nacelles. Overcomes warehouse partners, and thus can move the gondola. This is to be considered disadvantageous, since the azimuth drives are dimensioned so potent must that they are able to overcome the adhesive torque of the bearing assembly. Furthermore, the azimuth drives must have an independent braking system, which serves to influence the rotational speed of the bearing assembly.
  • the azimuth drives can also serve to prevent unwanted rotation of the nacelle, if environmental high torques - for example, caused by a gust - threaten to overcome the adhesive torque of the passive braking system. This tangential forces are derived via the transmission of the azimuth drives, whereby this is heavily loaded.
  • a bearing assembly for an azimuth bearing of a wind turbine is to be specified, which has a claim-friendly and maintenance-friendly construction.
  • an optional object of the invention is that the bearing assembly can simultaneously serve as an active brake.
  • a friction lining is disposed between the bearing block and the bearing block rotatable bearing partner.
  • This concept makes it possible for the first time to represent a support of a bearing ring and a bearing ring, the adjustment of the bearing clearance is carried out in a simple manner.
  • the bearing assembly with a functioning as a brake or sliding bearings bearing block can be displayed, both the exclusive use as a bearing without active brake, as well as the combined, simultaneous use as a bearing and as an active brake in the invention should be.
  • the braking means and the bearing means can engage the same support surface of a bearing partner, which further reduces the complexity, and possibly also the number of components of the construction.
  • the friction lining rotatably connected to a bearing partner, and is executable as a brake pad or sliding coating, the manufacturing costs can be significantly reduced, since substantially similar or identical components are used, and a differentiation of the devices as an active brake or plain bearings primarily on the basis of training of the friction lining is made.
  • the friction lining in Pairing with the non-rotatably connected bearing partner has a high coefficient of friction, especially greater than 0.3, so this is to be referred to as a brake pad, and is also used accordingly. This means that in unrestrained operation a high normal force between the bearing partners and the brake pad is to be avoided.
  • the friction lining is designed as a sliding coating with a low coefficient of friction, preferably less than 0.09.
  • normal force or biasing force is set constant by means of the bearing block for operation, so that the bearing assembly works without play. Since the friction lining is shown as a sliding coating with a low coefficient of friction, the biasing force causes only a small braking torque.
  • An advantageous embodiment of the invention teaches to form the bearing block wedge-shaped in a radial sectional plane, wherein the bearing block has a first bearing surface facing a bearing partner and a second bearing surface facing the other bearing partner.
  • the bearing surfaces are anti-parallel to each other. This anti-parallelism of the bearing surfaces, in cooperation with the bearing surfaces of the bearing partners, causes the actuation force exerted on the bearing block to be reinforced by wedging action of the antiparallel surfaces.
  • the wedging action of the bearing surfaces advantageously affects the functionality of the bearing assembly when the wedge angle ⁇ enclosed by the bearing surfaces is in a range of 3 ° to 10 ° degrees, and preferably 4 ° degrees.
  • the friction lining is designed as a sliding layer, which is arranged on the bearing surface of the bearing block, which faces the rotatable bearing partner, so in one embodiment of the invention, the support surfaces of the bearing partners each parallel to the associated bearing surfaces on the bearing block.
  • the surface pressure is kept low due to distribution.
  • the support surface of the bearing block for non-rotatably arranged bearing partner extends antiparallel to the axis and with the axis of the bearing assembly an angle ⁇ of 3 ° to 10 ° degree, in particular 4 ° degree includes.
  • the friction lining is designed as a brake pad.
  • the brake lining and the bearing block are designed as separate components, wherein a Belagabstütz Stamate Stamate Stamate Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Staize Sta bearing block facing side of the brake pad. This can be acted upon by the bearing block and runs parallel to the second bearing surface.
  • the bearing block and the brake lining are thus not completely interlocked with each other geometrically, which is why primarily only compressive forces between the brake pad and the bearing block are positively transferable.
  • Circumferential forces are derived in the sense of a division of the power flow directly from the friction lining in the rotatably connected bearing partner, without significant proportions of the circumferential force act on the bearing block.
  • the support surface of the bearing block rotatably arranged bearing partner extends parallel to the axis, so no axial force flow can be made in a positive manner on the support surfaces between the bearing partners.
  • This advantageously has the effect that the radial pretension and the radial play can be adjusted independently of the axial play.
  • this arrangement causes the active braking of the bearing assembly no unwanted axial loads between the bearing partners are present.
  • the support surface of the bearing block for non-rotatably arranged bearing partner can run anti-parallel to the axis, and thereby with the axis an angle ⁇ of 3 ° to 10 ° degree, in particular 4 ° degree include.
  • the wedge effect can alternatively be achieved by the lining supporting surface extending anti-parallel to the axis and enclosing with the axis an angle ⁇ of 3 ° to 10 ° degrees, in particular 4 ° degrees.
  • the static friction between the sliding lining and the supporting surface can be reduced by means of a favorable material or by a coating, for example with Teflon or with plastic.
  • a favorable material for example with Teflon or with plastic.
  • a further embodiment of the invention further improves the functional behavior of the bearing block between the bearing partners, by means for rolling off a translatory relative movement of at least between the bearing block and the pad support surface or between the bearing block and the support surface
  • Bearing block and the bearing partner or the brake pad are provided. These means for unwinding span a plane which replaces the bearing surfaces while having the same spatial orientation as the bearing surfaces. Thus, the tendency of the bearing block to jamming is reduced again, since when releasing the brake only the rolling resistance of the means must be overcome.
  • an adjusting device is provided to adjust a defined position of the bearing block between the bearing partners and to allow readjustment.
  • the game between the bearing partners depending on the geometric conditions and manufacturing tolerances is adjustable so that an optimal operation of the azimuth bearing of the wind turbine is ensured.
  • adjustment screws are conceivable.
  • a further development of the invention includes providing an actuator to vary the axial position of the bearing block during operation. This ensures that the effective between the bearing partners normal or biasing force or play can be increased or decreased as needed, by moving the storage block.
  • the wedge-shaped form of the bearing block in cooperation with the corresponding support surface, converts an axial displacement under force amplification into a radial displacement. Ultimately, therefore, an active braking system is displayed.
  • the automatic actuating device comprises a pneumatic muscle.
  • the actuator is so pronounced that a spring assembly presses the bearing block under pretension between the support surfaces, whereby the active brake is closed, and the bearing assembly can perform no rotation.
  • the pneumatic muscle can be effectively arranged against the spring force of the spring assembly, wherein the pneumatic muscle overcomes the spring force upon actuation, pulls out the bearing block between the bearing partners, and thus opens the brake.
  • the bearing arrangement comprises at least two friction linings, wherein a friction lining is designed as a brake lining and a friction lining as a sliding lining.
  • a friction lining is designed as a brake lining and a friction lining as a sliding lining.
  • the above-described embodiments of bearing arrangements can be used in wind turbines, which have a about the axis on a tower rotatably mounted nacelle. Between the tower and the nacelle, this bearing arrangement is partially or completely arranged according to the various embodiments described above. Because this reveals the enormous advantages of the bearing arrangement particularly clearly, as act in such wind turbines extremely high forces and moments. There is the open conflict of objectives, on the one hand to represent a leichcitede possible vibration-free storage, which must be controllable on the other by braking devices and adjustable bearing blocks.
  • a method for operating a wind turbine is also to be disclosed.
  • a control device of the wind turbine detects an actual value of the horizontal orientation of the nacelle, and compares this with a nominal value. If the actual value deviates from the target value by more than a certain amount, the following steps are carried out:
  • FIG. 1 is a perspective view of an underside of a first embodiment of a bearing assembly
  • FIG. 2 is a detail view of an upper side of the bearing assembly of FIG. 1,
  • FIG. 3 is an axial view of the underside of the bearing assembly of FIG. 1,
  • FIG. 4 shows a section through the bearing arrangement along the line A-A according to FIG. 3, FIG.
  • FIG. 6 is an exploded view of the brake pad of FIG. 5,
  • FIG. 8 is a perspective view of the closure plate and the spacer ring of the bearing assembly of FIG. 1, and
  • Fig. 1 leads to an embodiment of the bearing assembly 1 according to the invention.
  • Such bearing arrangements 1 are installed in wind turbines as so-called azimuth bearings between the nacelle and the tower, the nacelle comprising a nacelle and a rotor.
  • a drive train mounted on a machine carrier.
  • the drive train has - depending on the design - essentially a rotor shaft, a rotor bearing and a generator connected thereto.
  • the generator has a gearbox with the Rotor shaft connected, which is acted upon by a brake.
  • the azimuth bearing allows the horizontal orientation of the nacelle according to the wind direction, the so-called wind direction tracking of the wind turbine.
  • one or more azimuth drives are provided on the azimuth, which are rotatably connected to the machine carrier of the nacelle.
  • the azimuth bearing must initiate the occurring bearing forces, such as thrust, gyro and yaw forces, from the machine carrier of the nacelle into the tower.
  • wind direction tracking also referred to as "yawing"
  • the nacelle is rotated about a vertical axis of rotation 2 in the horizontal plane to rotate the rotor vertically into the wind and thus maximize energy yield.
  • a bearing assembly 1 is shown in a perspective view obliquely from below.
  • a bearing partner 5 which is designed as a turntable 5, fixedly connected via holes 7 with a tower, not shown.
  • the other bearing partner 8 of the bearing assembly 1 is pronounced as a rotatable about the axis 2 bearing ring 8, which surrounds the turntable 5 axially and thus in an axial direction 3 and in a radial direction 4 with the turntable 5 is geometrically entangled.
  • On the turntable 5 an outer toothing 6 is provided, which can engage in azimuth drives, not shown.
  • the invention also includes bearing assemblies having a turntable with an internal toothing, or wherein the bearing partners are pronounced in an alternative or reversed, ie have a rotatable turntable and a rotationally fixed bearing ring.
  • bearing partners 5 instead of the bearing partners 5, 8 only talk of the turntable 5 and the bearing ring 8.
  • the bearing ring 8 consists inter alia of an annular flange 9, which may be designed as a separate component or integrally with the machine carrier of the nacelle.
  • annular flange 9 In the annular flange 9 are prestressed, upper sliding devices 12th arranged in a form-fitting manner, via which the annular flange 9, and thus the entire nacelle of the wind turbine rests in the assembled state on the turntable 5 in the axial direction 3.
  • the axial entanglement of the bearing ring 8 takes place with a plurality of closure plates 11, which are connected in a ring shape to the annular flange 9 via a spacer ring 10 (FIG. 7).
  • Ring flange 9, spacer ring 10 and closure plates 11 are screwed together by screws 13, resulting in a turntable 5 encompassing, U-shaped contour of the bearing ring 8 results.
  • the play-free, complete fixation of the bearing ring 8 in the axial direction 3 on the turntable 5 is ensured by the use of further, lower sliding devices 24 which are fixedly connected to the closure plates 11.
  • the construction of the sliding devices 12, 24 will be described below with reference to the section along the line A-A from FIG. 3 shown in FIG.
  • the upper, prestressable sliding device 12 comprises a cylindrical housing 15, which is closed on one side with a plug 16 in a form-fitting manner.
  • an adjusting screw 17 is screwed axially with lock nut, wherein the shank of the adjusting screw 17 via a spring receiving 18 disc springs 19 acted upon.
  • the plate springs 19 generate a biasing force acting on a support plate 20 of a sliding lining 21.
  • Through the sliding device 12 performs a lubrication hole 22 which is connectable via a grease nipple 23 with a lubricant supply, not shown.
  • the lower sliding device 24 has a similar construction to the upper sliding device 12, but this is hardly biased because of the missing springs.
  • An adjusting screw 25 is guided in a thread in a plug 26 which is provided directly in the closure plate 11, and directly a support plate 27 of a sliding lining 28 loaded.
  • the axial play and the axial preload of the bearing assembly 1 can be adjusted as required over the circumference, so that a defined bearing seat with sufficient ease is feasible.
  • the arrangement of the upper prestressable sliding devices 12 is shown in a view from above of the annular flange 9, Fig. 1 and Fig. 3 illustrates the arrangement of the lower sliding devices 24th
  • the support of the bearing ring 8 on the turntable 5 in the radial direction 4 will be made below with the aid of Fig. 4.
  • the radial guidance is essentially of an axially extending support surface 29 on the radially inner side of the turntable 5 and formed by a support surface 30 on the radial outer side of the spacer ring 10. Between the support surfaces 29, 30, a bearing block 31 is provided, which in the axial direction 3 between the turntable 5 and the bearing ring 8 can be inserted.
  • the bearing block 31 is rotatably connected to the spacer 10, to which the spacer 10 is provided on the circumference with radially projecting lugs 36 which receive the force acting on the bearing block 31 peripheral forces (Fig. 7).
  • the bearing block 31 has two bearing surfaces 32,33, which each face a support surface 29, 30 and extend parallel to the same.
  • the support surface 29 of the turntable 5 and the corresponding bearing surface 32 on the bearing block 31 are formed parallel to the axis 2, which can be transmitted via this form-fitting exclusively radial forces.
  • the support surface 30 on the spacer ring 10 is slightly inclined relative to the axis 2 pronounced, and closes with this in a plane which is spanned by the axis 2 and the radial direction 4, a small angle ⁇ .
  • the bearing surface 33 on the bearing block 31 extends parallel to the inclined support surface 30.
  • the bearing block 31 has a wedge-shaped contour which, in interaction with the support surfaces 29, 30 of the bearing partners 5, 8 forms a wedge-based transmission gear, wherein on the axial position the bearing block 31 under force amplification, the radial clearance and the bias between the turntable 5 and the spacer ring 8 is adjustable.
  • an adjusting device 37 is provided in the closure plate 11, wherein an adjusting screw 38 acts on the bearing block 31 and thereby determines the axial position of the bearing block 31.
  • the bearing surfaces 32, 33 of the bearing block 31 are each provided with a sliding coating 34, 35, which in friction pairing with the support surfaces 29, 30 preferably has a low coefficient of friction of about 0.09.
  • the radial play and preload are adjusted, and independently with the slips 12, 24 the axial play and axial preload are adjusted.
  • the nacelle during operation can perform any unwanted movements and causes no excessive friction, so that yawing of the nacelle with small-sized and cheap azimuth drives can be implemented.
  • the sliding linings 34, 35 are applied for example from a plastic by injection molding on the bearing block 31 and form thereon the bearing surfaces 32, 33 from. It is also conceivable to use self-lubricating materials, which may optionally be positively connected to the bearing block 31.
  • FIG. 5 shows a section along the line B-B from FIG. 2.
  • a wedge-shaped bearing block 41 is provided displaceably in the axial direction 3 between the spacer ring 10 and the turntable 5.
  • This bearing block 41 exerts via two bearing surfaces 42, 43 a radial force on the support surface 29 of the turntable 5 and on the support surface 44 of the spacer ring 10, when the bearing block 41 is pressed between them.
  • the wedge angle ß is equal to the angle Y, which includes the support surface 44 of the spacer ring 10 with the axis 2.
  • a brake pad 45 is arranged, which has a pad support surface 40 and can be acted upon by the bearing block 41.
  • This brake pad 45 is shown individually in Fig. 6 with the bearing block 41, wherein the functionally relevant elements can be seen.
  • Brake pad 45 and bearing block 41 are secured to the lugs 36 of the spacer 10 against rotation.
  • Both bearing surfaces 42, 43 of the bearing block 41 are provided with sliding linings or coatings 46, 47.
  • the brake pad 45 includes a friction plate 48 supporting back plate 49. It is also possible that a sliding pad 46 is received by the rear plate 49 of the brake pad 45.
  • the closure plate 10 receives the actuator 50, by means of which the axial position of the bearing block 41 is automatically varied.
  • the actuator 50 comprises a support tube 52, at the end 53 of a pneumatic muscle 54 is fixedly arranged. Furthermore, the pneumatic muscle 54 is connected via a connecting piece 55 to the bearing block 41.
  • disc springs 56 are arranged, which press the bearing block 41 via the connecting piece 55 between the bearing ring 8 and the turntable 5 and the brake pad 45.
  • the bearing block 41 permanently causes a normal force between the slewing ring 5 and the bearing ring 8 or the brake pad 45, whereby the brake is closed the tube body 57, thus shortens the muscle 54 and pulls contrary to the spring force of the plate springs 56, the bearing block 41 out. This opens the brake.
  • FIG. 8 is a perspective section on a closure plate 11 and the spacer ring 10 of the bearing assembly 1 without a turntable 5 is given.
  • This is the arrangement of serving as a radial bearing blocks 31 with sliding linings 34, 35 and acting as an active brake bearing blocks 41 illustrated with brake pad 45.
  • the bearing blocks 31, 41 are supported by the lugs 36 of the spacer ring 10 in the circumferential direction.
  • FIG. 9 An alternative embodiment of the invention is illustrated in Fig. 9, wherein serving as a brake bearing block 61 is provided with means for unrolling 57, on the pad support surface 58 of the brake pad 59 and the support surface 60 of the spacer ring 10 are acted upon.
  • rollers 63 can be used, which span a plane. These planes act as bearing surfaces and have the same spatial orientation as the bearing surfaces 42, 43 of FIG. 5. It is advantageous in this case that jamming of the bearing block 61 between the brake pad 59 and the spacer ring 64 is substantially ruled out since there is no static friction and the bearing block 61 tends to move out between the turntable 5 and the spacer ring 64 due to the wedging action.
  • the support surface 60 of the spacer ring 64 is parallel to the axis 2, and the Belagabstützamide 58 on the back plate 62 of the brake pad 59 is inclined relative to the axis 2 at the angle ⁇ .
  • an axial force component of the actuating force is transmitted to the brake pad 59, which is received by the annular flange 9.
  • bearing partners are not necessarily perform as rotationally symmetric rings, in particular, the U-shaped expression of the bearing partners can only partially extend over certain angular sections or circle segments of the bearing assembly. LIST OF REFERENCE NUMBERS

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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)
  • Wind Motors (AREA)

Abstract

L'invention concerne un ensemble palier, destiné en particulier à une éolienne, pour la transmission de forces radiales et axiales, cet ensemble comprenant deux éléments de palier pouvant tourner l'un par rapport à l'autre autour d'un axe. Ces éléments de palier présentent chacun une surface d'appui, un bloc de palier étant disposé de façon à pouvoir être inséré entre les surfaces d'appui dans une direction d'actionnement pour générer une force normale agissant sur les surfaces d'appui. Ce bloc de palier est relié à l'un des éléments de palier de façon solidaire en rotation. Un objectif de l'invention est de concevoir un ensemble palier amélioré, ne présentant pas notamment les inconvénients de l'art antérieur. En particulier, l'objectif est de concevoir un ensemble palier présentant une structure adaptée aux contraintes et d'entretien facile pour un palier azimutal d'une éolienne. Un autre objectif de l'invention est de concevoir un ensemble palier pouvant servir simultanément de frein actif. L'objectif est atteint grâce aux caractéristiques de la revendication principale 1, selon laquelle une garniture de friction est disposée entre le bloc de palier et l'élément de palier pouvant tourner par rapport au bloc de palier. Cette configuration permet pour la première fois de représenter un support d'une bague et d'une couronne, le jeu de palier pouvant être réglé facilement.
EP08758987A 2007-06-04 2008-06-03 Ensemble palier pour éolienne Withdrawn EP2153066A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08758987A EP2153066A2 (fr) 2007-06-04 2008-06-03 Ensemble palier pour éolienne

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP07090108 2007-06-04
DE102007056763A DE102007056763A1 (de) 2007-06-04 2007-11-23 Lageranordnung für eine Windturbine
PCT/EP2008/004426 WO2008148526A2 (fr) 2007-06-04 2008-06-03 Ensemble palier pour éolienne
EP08758987A EP2153066A2 (fr) 2007-06-04 2008-06-03 Ensemble palier pour éolienne

Publications (1)

Publication Number Publication Date
EP2153066A2 true EP2153066A2 (fr) 2010-02-17

Family

ID=39968053

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08758987A Withdrawn EP2153066A2 (fr) 2007-06-04 2008-06-03 Ensemble palier pour éolienne

Country Status (5)

Country Link
US (1) US20100176601A1 (fr)
EP (1) EP2153066A2 (fr)
CN (1) CN101711312A (fr)
AU (1) AU2008258839A1 (fr)
WO (1) WO2008148526A2 (fr)

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CN101711312A (zh) 2010-05-19
AU2008258839A1 (en) 2008-12-11
WO2008148526A3 (fr) 2009-02-05
AU2008258839A2 (en) 2010-02-18
US20100176601A1 (en) 2010-07-15

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