EP4226057A1 - Palier lisse, nacelle d'éolienne équipée de ce palier lisse et une éolienne - Google Patents

Palier lisse, nacelle d'éolienne équipée de ce palier lisse et une éolienne

Info

Publication number
EP4226057A1
EP4226057A1 EP21805344.5A EP21805344A EP4226057A1 EP 4226057 A1 EP4226057 A1 EP 4226057A1 EP 21805344 A EP21805344 A EP 21805344A EP 4226057 A1 EP4226057 A1 EP 4226057A1
Authority
EP
European Patent Office
Prior art keywords
bearing
plain bearing
ring element
plain
outer ring
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.)
Pending
Application number
EP21805344.5A
Other languages
German (de)
English (en)
Inventor
Johannes Sebastian HÖLZL
Albert WALDL
Patrick Laubichler
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.)
Miba Gleitlager Austria GmbH
Original Assignee
Miba Gleitlager Austria 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
Application filed by Miba Gleitlager Austria GmbH filed Critical Miba Gleitlager Austria GmbH
Publication of EP4226057A1 publication Critical patent/EP4226057A1/fr
Pending legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor 
    • F03D1/06—Rotors
    • F03D1/065—Rotors characterised by their construction elements
    • F03D1/0691—Rotors characterised by their construction elements of the hub
    • 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/105—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one bearing surface providing angular contact, e.g. conical or spherical bearing surfaces
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/046—Brasses; Bushes; Linings divided or split, e.g. half-bearings or rolled sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/26—Brasses; Bushes; Linings made from wire coils; made from a number of discs, rings, rods, or other members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
    • 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
    • F05B2240/53—Hydrodynamic or hydrostatic bearings
    • 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
    • F05B2240/57—Seals
    • 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
    • F05B2260/98—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a plain bearing and a pod equipped with the plain bearing for a wind turbine and a wind turbine.
  • a bearing element for mounting the rotor hub of a wind turbine is known from WO 2011/127510 A1.
  • the object of the present invention was to provide an improved plain bearing.
  • a slide bearing is designed.
  • the slide bearing includes:
  • At least one plain bearing element which is arranged between the inner ring element and the outer ring element, the plain bearing element comprising at least two plain bearing pads, the individual plain bearing pads each having a bearing surface which has the basic shape of a spherical cap.
  • the slide bearing according to the invention has the advantage that the bearing surface, which can have the basic shape of a spherical cap, is designed to absorb radial forces and at the same time to absorb axial forces.
  • the outer ring element is designed as a bearing block, which has a bearing block base and a bearing block cover.
  • This has the advantage that the bearing block cover can be easily removed, which makes it easier to remove the plain bearing pads for maintenance.
  • the slide bearing pads can be removed radially from the inner ring element.
  • this measure allows the individual plain bearing pads to be arranged more easily on the inner ring element when assembling the plain bearing by lifting them radially through the opening in the bearing block cover into the space between the inner ring element and the outer ring element.
  • the outer ring element stands still during operation of the plain bearing and that the plain bearing pads are attached to the inner ring element and are rotated together with the inner ring element.
  • the bearing surface interacts with the outer ring element, with a counter-surface to the bearing surface being formed in the outer ring element.
  • the inner ring element has a shaped element, in particular in the form of an elevation or a depression, the plain bearing pads having a counter-shaped element corresponding to the shaped element, so that the shaped element serves as axial security for the plain bearing pads.
  • the shaped element arranged on the inner ring element is designed in the form of a circumferential bead with a rectangular cross section, the plain bearing pads having a corresponding groove extending in the circumferential direction. High axial forces can be transmitted in particular through the formation of such a circumferential bead.
  • a groove with a rectangular cross section is formed on the inner ring element, with the slide bearing pads having a corresponding elevation or bead on the inside thereof.
  • At least one of the plain bearing pads is provided with an anti-twist device, by means of which this plain bearing pad is secured against twisting relative to the inner ring.
  • an anti-twist device can be, for example, an elevation, a depression or another element that acts in a form-fitting manner between the slide bearing pad and the inner ring element, such as a driving pin.
  • the plain bearing pads it is possible for at least some of the plain bearing pads to be coupled to one another by means of a connecting element. This has the advantage that the individual plain bearing pads can be fixed relative to one another. Thus, the position of the individual plain bearing pads can be fixed.
  • the connecting element is arranged on a peripheral side of the slide bearing pads.
  • the individual plain bearing pads can be well fixed to one another, particularly with a connecting element designed in this way.
  • the connecting element has at least one fastening wedge, with a fastening groove corresponding to the fastening wedge being formed in the plain bearing pad.
  • a connecting element that is equipped with a fastening wedge can be used not only to absorb shearing forces but also to absorb tensile forces.
  • the connecting element has an adjustment means, so that the distance from one another of two plain bearing pads coupled to one another by means of the connecting element can be adjusted. This has the advantage that the individual sliding bearing pads can be clamped to one another and can thus be clamped on the inner ring element.
  • the plain bearing pads it is possible for at least some of the plain bearing pads to be coupled to the inner ring element by means of a fastening means.
  • This has the advantage that the sliding bearing pads can be firmly connected to the inner ring element, and this connection can be detachable.
  • fastening screws are used as fastening means.
  • the fastening means can be inserted in the radial direction in the sliding bearing pads or in the inner ring element.
  • through-holes are formed in the sliding bearing pads, through which the fastening screws can engage in threaded bores, which can be arranged in the inner ring element.
  • the bearing surface has a spherical cap designed in such a way that the bearing surface has a first diameter in the area of a first end face of the plain bearing pad and that the bearing surface has a second diameter in the area of a second end face of the plain bearing pad, the first diameter is smaller than the second diameter and wherein the second diameter forms the largest diameter at the bearing surface.
  • the bearing surface tapers starting from the second diameter, with this tapering being able to be in the form of a spherical cap. This brings with it the advantage that the slide bearing pads are designed particularly well for absorbing forces in a first axial direction, in particular in a main loading direction.
  • an axial bearing ring is formed, which is coupled to the outer ring element, with an axial sliding surface being formed on the plain bearing pads, with an axial counter-sliding surface being formed on the axial bearing ring, which corresponds to the axial sliding surface. It can be provided here that the axial bearing ring is arranged on that side of the plain bearing in which the lower axial forces occur in comparison to the second side.
  • the outer ring element has a recess and/or a reinforcement which is used to change the position of a thrust center of the outer ring element.
  • the mating surface of the outer ring element and/or the bearing surfaces of the plain bearing pads have a shape that deviates from an ideal spherical cap by between 0.001 mm and 10 mm, in particular between 0.05 mm and 5 mm, preferably between 0.5 mm and 1 mm is designed in such a way that load-related deformations of the inner ring element and/or the outer ring element and/or the plain bearing pad are compensated and in the loaded state the bearing surfaces of the plain bearing pads lie flat against the mating surface of the outer ring element.
  • This has the advantage that this measure can be used to anticipate a load-related deformation of individual components of the plain bearing, so that during operation the bearing surface and the mating surface lie against one another as flatly as possible in order to prevent surface pressure.
  • the plain bearing is designed as a hydrodynamic plain bearing.
  • a hydrodynamic plain bearing in particular has low frictional resistance and therefore high efficiency.
  • At least one entrainment depression for conveying lubricating oil is formed on the bearing surface of at least one of the plain bearing pads. This brings with it the advantage that lubricating oil can be conveyed upwards from the lubricating oil sump by means of the driving depression and can thus be used to lubricate the slide bearing.
  • the entrainment recess is designed in the form of a groove or a bead.
  • a porous material is arranged in the entrainment depression, which serves to temporarily hold lubricating oil.
  • This can be a sponge, for example.
  • the driving depression has an opening which is inclined in the direction of rotation and has a cavity for receiving the lubricating oil.
  • the entrainment recess can be designed according to the scoop wheel principle. This has the advantage that lubricating oil can be conveyed upwards particularly well from the lubricating oil sump.
  • the mating surface of the outer ring element has an inlet groove that extends over a certain circumferential angle, so that lubricating oil can easily get into the driving recess.
  • the entrainment recess does not extend over the complete axial extension of the sliding surface of the plain bearing pad, so that the lubricating oil that has been taken up cannot run out of the entrainment recess on the face side.
  • a first labyrinth seal is formed in the axial bearing ring and/or that a second labyrinth seal is formed in a sealing ring.
  • the axial bearing ring is arranged on the second end face of the plain bearing pad and that the sealing ring is arranged on the first end face of the plain bearing pad.
  • the bearing block base and the bearing block cover are divided in such a way that a separating gap between the bearing block base and the bearing block cover is arranged at a distance from a load transmission zone.
  • a nacelle for a wind turbine is designed.
  • the gondola includes:
  • a rotor hub which is arranged on the rotor shaft
  • a rotor bearing for mounting the rotor shaft on the nacelle housing.
  • the rotor bearing comprises a plain bearing according to one of the preceding forms.
  • a nacelle designed in this way has high efficiency and a simple structure.
  • the rotor shaft forms the inner ring element.
  • a nacelle constructed in this way can be manufactured simply and thus inexpensively.
  • the bearing surface is designed in the form of a spherical cap such that the bearing surface has a first diameter in the area of a first end face of the plain bearing pad and that the bearing surface has a second diameter in the area of a second end face of the plain bearing pad, the first diameter is smaller than the second diameter and wherein the second diameter forms the largest diameter at the bearing surface with the second face facing a rotomabe.
  • the bearing surface tapers starting from the second diameter, with this tapering being able to be in the form of a spherical cap. This brings with it the advantage that the slide bearing pads are designed particularly well for absorbing forces in a first axial direction, in particular in a main loading direction.
  • a wind turbine is designed with a nacelle, the nacelle comprising the following component:
  • a rotor bearing for mounting the rotor hub on the nacelle housing.
  • the rotor bearing comprises a plain bearing according to one of the preceding forms.
  • a wind power plant designed in this way has high efficiency and a simple structure.
  • the outer ring element has a shear center and that the plain bearing pad acts on the outer ring element in a main direction of force, the main direction of force acting closer to the second end face of the plain bearing pad than the shear center is formed.
  • FIG. 1 shows a schematic representation of a wind turbine
  • FIG. 2 shows a perspective view of a first exemplary embodiment of a plain bearing
  • Fig. 4 is a perspective view of two plain bearing pads, which in the form of
  • FIG. 5 shows a perspective representation of a further exemplary embodiment of the plain bearing with a plurality of plain bearing pads
  • FIG. 6 shows a cross section of a further exemplary embodiment of the plain bearing with a plurality of plain bearing pads
  • FIG. 7 shows a detailed view of a further exemplary embodiment of a connecting element
  • FIG. 8 shows a cross section of a further exemplary embodiment of the plain bearing with two plain bearing pads
  • Fig. 10 is a longitudinal section of another embodiment of the plain bearing with a
  • FIG. 11 shows a longitudinal section of a further exemplary embodiment of the sliding bearing with a reinforcement on the outer ring element
  • FIG. 1 shows a first exemplary embodiment of a wind power plant 1 for generating electrical energy from wind energy in a schematic representation.
  • the nacelle 1 comprises a gondola 2 which is rotatably mounted on a tower 3.
  • the nacelle 2 comprises a nacelle housing 4 which forms the main structure of the nacelle 2 .
  • the electrotechnical components such as a generator of the wind turbine 1 are arranged in the nacelle housing 4 of the nacelle 2 .
  • a rotor 5 is formed, which has a rotor hub 6 with rotor blades 7 arranged thereon.
  • the Rotomabe 6 is seen as part of the Nacelle 2.
  • the rotor hub 6 is rotatably mounted on the nacelle housing 4 by means of a rotor bearing 8 .
  • a plain bearing 9 according to the invention and described in more detail below is used as the rotor bearing 8 .
  • the 2 serves is designed to absorb a radial force 10 and an axial force 11 .
  • the axial force 11 is due to the force of the wind.
  • the radial force 10 is due to the weight of the rotor 5 and acts on the center of gravity of the rotor 5 . Since the center of gravity of the rotor 5 is outside the rotor bearing 8, a tilting moment 12 is caused in the rotor bearing 8 by the radial force 10.
  • the tilting moment 12 can also be caused by an uneven load on the rotor blades 7 .
  • This tilting moment 12 can be absorbed by means of a second plain bearing, which is arranged at a distance from the plain bearing 9 according to the invention.
  • the rotor bearing 8 according to the invention can have a diameter of between 0.5 m and 5 m, for example. Of course it is also conceivable that the rotor bearing 8 is smaller or larger.
  • FIG. 2 shows a first exemplary embodiment of the plain bearing 9 installed in the nacelle 2. Of course, the plain bearing 9 shown in FIG. 2 can also be used in all other industrial applications outside of wind turbines.
  • the slide bearing 9 is shown in Fig. 2 in a perspective exploded view.
  • Fig. 3 the first embodiment of the slide bearing 9 is shown in a cross-sectional view.
  • the slide bearing 9 is described below with reference to FIGS. 2 and 3 being viewed together.
  • the plain bearing 9 has an inner ring element 13 and an outer ring element 14 .
  • a sliding bearing element 15 is arranged between the inner ring element 13 and the outer ring element 14 and is used for the rotary sliding bearing of the inner ring element 13 relative to the outer ring element 14 .
  • the inner ring element 13 is designed as a rotor shaft 16 .
  • the inner ring element 13 can also be another type of shaft.
  • the outer ring element 14 is designed as a bearing block 17 which has a bearing block base 18 and a bearing block cover 19 .
  • the bearing block base 18 is coupled to the nacelle housing 4 .
  • the outer ring element 14 is rigidly coupled to the nacelle housing 4 and the inner ring element 13 can be rotated relative to the outer ring element 14 with respect to a rotor axis 21 by means of the plain bearing element 15 .
  • the plain bearing element 15 comprises a plurality of individual plain bearing pads 20 which are distributed over the circumference between the inner ring element 13 and the outer ring element 14 .
  • first labyrinth seal 49 to be formed in the axial bearing ring 32 .
  • Provision can furthermore be made for a second labyrinth seal 50 to be formed in a sealing ring 48 which is arranged on the first end face 26 .
  • a hollow space for accommodating lubricating oil 51 is formed between the axial bearing ring 32 and the plain bearing pad 20 or between the sealing ring 48 and the plain bearing pad 20 .
  • This cavity can also be referred to as a lubricating oil sump.
  • the slide bearing pad 20 has an axially extending opening in the area of the lubricating oil sump, which is used to admit lubricating oil into driving depressions 47 .
  • Fig. 4 an embodiment of the slide bearing element 15 is shown in a perspective view. From this illustration it can be seen particularly well that it can be provided that the plain bearing element 15 comprises two individual plain bearing pads 20 . As can also be seen from FIG. 4 , provision can be made for the individual plain bearing pads 20 to be coupled to one another by means of a connecting element 22 .
  • At least one carrier depression 47 for conveying the lubricating oil 51 is formed on the bearing surface 23 of at least one of the plain bearing pads 20 .
  • the connecting elements 22 are designed in the form of screws.
  • the two plain bearing pads 20 are screwed together in the circumferential direction or tangentially. Such a screw connection can result in the inner ring element 13 being clamped by the plain bearing pads 20 .
  • the individual plain bearing pads 20 are thus firmly connected to the inner ring element 13 by the described structure in the operating state of the plain bearing 9 and thus rotate with it relative to the outer ring element 14.
  • a bearing surface 23 is formed on the individual slide bearing pads 20, which rests against a counter-surface 24 of the outer ring element 14 when the slide bearing 9 is in the ready-to-use state.
  • the counter surface 24 is arranged on an inner side 25 of the outer ring element 14 .
  • the bearing surface 23 of the sliding bearing pad 20 and the counter-surface 24 of the outer ring element 14 are designed as sliding surfaces which slide against one another when the sliding bearing 9 is in operation.
  • the mating surface 24 of the outer ring element 14 is designed as a hard, wear-resistant surface, which can be formed by hardened steel, for example.
  • the bearing surface 23 of the plain bearing pad 20 can be formed from a plain bearing material that is soft compared to the mating surface 24 .
  • the bearing surface 23 has a sliding coating.
  • the bearing surface 23 can be in the form of a spherical cap.
  • the formation of the bearing surface 23 or the counter-surface 24 in the form of a spherical cap has the advantage that the plain bearing pads 20 can be easily rotated about the rotor axis 21 .
  • the plain bearing pads 20 can be tilted at an angle with respect to the longitudinal extent of the rotor axis 21 . Deflections of the rotor shaft 16 in the plain bearing 9 can thus be compensated for by the described embodiment of a spherical cap without an increased surface load on the bearing surface 23 occurring in the process.
  • axial bearing forces can also be transmitted in addition to the transmission of radial bearing forces due to the design of the bearing surface 23 or the mating surface 24 in the form of a spherical cap.
  • the bearing surface 23 has a first diameter 27 on a first end face 26 . Starting from this first end face 26 , the bearing surface 23 can increase in diameter towards a second end face 28 . In the area of the second end face 28, in particular towards the Rotomabe, the Bearing surface 23 may be open and have a second diameter 29 there. This design of the bearing surface 23 allows the axial force 11 and also the radial force 10 to be absorbed particularly well.
  • a shaped element 30 in the form of a circumferential bead is formed on the inner ring element 13 .
  • a counter-shaped element 31 in the form of a recess can be formed in the plain bearing pad 20 on the side facing the inner ring element 13 .
  • an axial bearing ring 32 to be formed in the region of the second end face 28, which ring element can be coupled, in particular screwed, to the outer ring element 14.
  • an axial sliding surface 33 to be formed on the plain bearing pads 20 , with an axial counter-sliding surface 34 being formed on the axial bearing ring 32 , which corresponds to the axial sliding surface 33 .
  • the axial bearing ring 32 can thus stand still together with the outer ring element 14 and the plain bearing pad 20 can rotate relative to the axial bearing ring 32 .
  • FIG. 5 shows a further embodiment of the plain bearing 9, which may be independent in itself, with the same reference numerals or component designations as in the preceding FIGS. 1 to 4 being used again for the same parts.
  • reference numerals or component designations as in the preceding FIGS. 1 to 4 being used again for the same parts.
  • the plain bearing pads 20 are distributed over the circumference.
  • the individual plain bearing pads 20 can be coupled to the inner ring element 13 by means of fastening means 35 .
  • the fastening means 35 are designed in the form of screws.
  • FIG. 6 shows a further embodiment of the plain bearing 9, which may be independent of itself, with the same reference numerals or component designations as in the preceding FIGS. 1 to 5 being used again for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIGS.
  • the individual slide bearing pads 20 are held in position relative to one another by means of the connecting element 22 .
  • the connecting element 22 can be arranged on the peripheral side 36 of the slide bearing pads 20 .
  • the connecting element 22 is designed in the form of a rectangular rod, which is introduced into a fastening groove 38 arranged in the peripheral sides 36 .
  • the bearing block cover 19 in order to change the individual slide bearing pads 20, provision can be made for the bearing block cover 19 to be lifted off the bearing block base 18 in a first method step.
  • the connecting elements 22 of the plain bearing pad 20 to be replaced can then be removed.
  • the plain bearing pad 20 to be replaced can be taken out of its position and removed in the radial direction.
  • FIG. 7 shows a further embodiment of the plain bearing 9, which may be independent of itself, with the same reference numerals or component designations as in the previous FIGS. 1 to 6 being used again for the same parts.
  • reference numerals or component designations as in the previous FIGS. 1 to 6 being used again for the same parts.
  • FIG. 7 shows a detailed view of the connecting element 22 for connecting plain bearing pads 20 adjacent to one another.
  • the fastening groove 38 in the sliding bearing pads 20 can be wedge-shaped and that, corresponding thereto, the connecting element 22 has a fastening wedge 39 which is accommodated in the fastening groove 38 .
  • Another fastening wedge 39 of the connecting element 22 can be accommodated in the fastening groove 38 of the further plain bearing pad 20 .
  • connection element 22 provision can be made for the connecting element 22 to have an adjusting means 40, by means of which the distance between the two fastening wedges 39 can be adjusted.
  • the distance between adjacent slide bearing pads 20 can be adjusted by means of the adjustment means 40 .
  • this measure makes it possible for the sliding bearing pads 20 to be pressed against the inner ring element 13 .
  • FIG. 8 shows a further embodiment of the plain bearing 9, which may be independent of itself, with the same reference numerals or component designations as in the preceding FIGS. 1 to 7 being used again for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIGS.
  • Fig. 8 shows the other embodiment of the plain bearing 9 in a sectional view.
  • two plain bearing pads 20 are formed, which are coupled to one another by means of the connecting elements 22 .
  • 8 shows an East transmission zone 42 schematically, in which the bearing surface 23 of the slide bearing pad 20 contacts the mating surface 24 of the outer ring element 14, in particular the bearing block base 18, and bears against it. Due to the force of gravity, the load transfer zone 42 is formed around the lowest point of the mating surface 24 of the outer ring element 14 in the present exemplary embodiment.
  • the mating surface 24 of the outer ring element 14 is not divided in the region of the load transmission zone 42 and therefore has no gap.
  • FIGS. 9 to 11 each show a further and possibly independent embodiment of the plain bearing 9, with the same reference numerals or component designations as in the preceding FIGS. 1 to 8 being used for the same parts.
  • the outer ring element 14 has a thrust center 43 .
  • the vector sum of the radial force 10 and the axial force 11 results in a main force direction 44 in which the slide bearing pads 20 act on the outer ring element 14 .
  • the main force direction 44 can be arranged closer to the first end face 26 than the shear center 43. This means that when the outer ring element 14 is loaded by a force acting in the main force direction 44 Force the outer ring member 14 is pressed in the region of the first end face 26 to the outside. However, this deformation can be undesirable.
  • a recess 45 is formed in the outer ring element 14, through which the thrust center 43 of the outer ring element 14 can be displaced.
  • FIG. 11 shows an alternative embodiment variant in which a reinforcement 46 is arranged or formed on the outer ring element 14, by means of which the thrust center 43 can also be displaced.
  • the center of shear 43 is influenced by means of the recess 45 or the stiffening 46 in such a way that the main direction of force 44 is arranged lying exactly in the center of the shear 43 .
  • FIG. 12 shows a further embodiment of the plain bearing 9, which may be independent of itself, with the same reference numerals or component designations as in the previous FIGS. 1 to 11 being used again for the same parts.
  • reference numerals or component designations as in the previous FIGS. 1 to 11 being used again for the same parts.
  • the mating surface 24 of the outer ring element 14 and/or the bearing surfaces 23 of the plain bearing pads 20 have a shape that deviates from the ideal spherical cap shape by a correction value.
  • a measure can be taken that load-related deformations of the inner ring element 13 and/or the outer ring element 14 and/or the plain bearing pad 20 can be compensated for, so that in the loaded state the bearing surfaces 23 of the plain bearing pads 20 bear against the mating surface 24 of the outer ring element 14 over as large an area as possible . This allows the surface pressure to be kept as low as possible.
  • the correction value can be calculated using simulation models, in particular using finite element calculations.
  • All information on value ranges in the present description is to be understood in such a way that it also includes any and all sub-ranges, e.g. the information 1 to 10 is to be understood in such a way that all sub-ranges, starting from the lower limit 1 and the upper limit 10, are also included , i.e. all subranges start with a lower limit of 1 or greater and end with an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Support Of The Bearing (AREA)
  • Sliding-Contact Bearings (AREA)
  • Wind Motors (AREA)
  • Sealing Of Bearings (AREA)

Abstract

L'invention concerne un palier lisse (9) comprenant : un élément annulaire intérieur (13) ; un élément annulaire extérieur (14) ; au moins un élément de palier lisse (15) qui est disposé entre l'élément annulaire intérieur (13) et l'élément annulaire extérieur (14), l'élément de palier lisse (15) comprenant au moins deux coussinets de palier lisse (20) et les coussinets de palier lisse (20) individuels présentant chacun une surface d'appui (23) qui présente la forme de base d'une calotte sphérique.
EP21805344.5A 2020-10-07 2021-10-05 Palier lisse, nacelle d'éolienne équipée de ce palier lisse et une éolienne Pending EP4226057A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020126284.1A DE102020126284A1 (de) 2020-10-07 2020-10-07 Gleitlagerung, sowie eine mit der Gleitlagerung ausgestattete Gondel für eine Windkraftanlage und eine Windkraftanlage
PCT/AT2021/060360 WO2022073050A1 (fr) 2020-10-07 2021-10-05 Palier lisse, nacelle d'éolienne équipée de ce palier lisse et une éolienne

Publications (1)

Publication Number Publication Date
EP4226057A1 true EP4226057A1 (fr) 2023-08-16

Family

ID=78535911

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21805344.5A Pending EP4226057A1 (fr) 2020-10-07 2021-10-05 Palier lisse, nacelle d'éolienne équipée de ce palier lisse et une éolienne

Country Status (6)

Country Link
US (1) US20230228253A1 (fr)
EP (1) EP4226057A1 (fr)
JP (1) JP2023544861A (fr)
CN (1) CN116368308A (fr)
DE (1) DE102020126284A1 (fr)
WO (1) WO2022073050A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2800038A1 (de) * 1977-01-26 1978-07-27 Voest Ag Gleit-gelenklager, insbesondere fuer kippbare konverter
JP2001107953A (ja) * 1999-10-05 2001-04-17 Mitsubishi Heavy Ind Ltd 軸受機構

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Publication number Priority date Publication date Assignee Title
GB401850A (en) * 1932-09-12 1933-11-23 Nomy Ab Improvements in radial thrust bearings
DE678930C (de) * 1935-09-16 1939-07-26 Fast Bearing Company Lager
DE650737C (de) * 1936-06-11 1937-09-30 Kugelfischer Erste Automatisch Gleitlager
DE826807C (de) * 1949-10-28 1952-01-07 Georg Seelmann Eggebert Dipl I Einbaufertiges Gleitlager
FR1464065A (fr) * 1965-11-17 1966-07-22 Palier lisse perfectionné
US4105261A (en) * 1976-10-29 1978-08-08 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Spherical bearing
GB9223721D0 (en) * 1992-11-12 1992-12-23 Neale Michael J A spherical plain bearing with pads
DE10305511B9 (de) * 2003-02-11 2005-01-27 Eduard Küsters Maschinenfabrik GmbH & Co. KG Walze
US7675211B2 (en) * 2007-03-06 2010-03-09 General Electric Company Method of assembling a rotor shaft assembly
AT509625B1 (de) 2010-04-14 2012-02-15 Miba Gleitlager Gmbh Lagerelement
DE102010036093A1 (de) * 2010-09-01 2012-03-01 Becker Marine Systems Gmbh & Co. Kg Lagerelement eines Ruderschaftlagers
EP2758681B1 (fr) * 2011-09-23 2017-11-01 US Synthetic Corporation Ensembles paliers, appareils et procédés de fabrication associés
US9562562B2 (en) * 2014-05-30 2017-02-07 Us Synthetic Corporation Bearing assemblies and apparatuses including superhard bearing elements
DE102019102430A1 (de) * 2019-01-31 2020-08-06 Renk Aktiengesellschaft Lageranordnung eines Rotors
AT522164B1 (de) * 2019-03-07 2020-09-15 Miba Gleitlager Austria Gmbh Gleitlagerung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2800038A1 (de) * 1977-01-26 1978-07-27 Voest Ag Gleit-gelenklager, insbesondere fuer kippbare konverter
JP2001107953A (ja) * 1999-10-05 2001-04-17 Mitsubishi Heavy Ind Ltd 軸受機構

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2022073050A1 *

Also Published As

Publication number Publication date
CN116368308A (zh) 2023-06-30
US20230228253A1 (en) 2023-07-20
WO2022073050A1 (fr) 2022-04-14
DE102020126284A1 (de) 2022-04-07
JP2023544861A (ja) 2023-10-25

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