WO2018153418A1 - Agencement de rotor principal d'éolienne ayant des moyens pour empêcher le fluage angulaire d'un anneau de roulement externe - Google Patents

Agencement de rotor principal d'éolienne ayant des moyens pour empêcher le fluage angulaire d'un anneau de roulement externe Download PDF

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Publication number
WO2018153418A1
WO2018153418A1 PCT/DK2018/050023 DK2018050023W WO2018153418A1 WO 2018153418 A1 WO2018153418 A1 WO 2018153418A1 DK 2018050023 W DK2018050023 W DK 2018050023W WO 2018153418 A1 WO2018153418 A1 WO 2018153418A1
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WO
WIPO (PCT)
Prior art keywords
shaft
main rotor
bearing
rotor arrangement
retainer element
Prior art date
Application number
PCT/DK2018/050023
Other languages
English (en)
Inventor
Lutz HEUSER
Original Assignee
Vestas Wind Systems A/S
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 Vestas Wind Systems A/S filed Critical Vestas Wind Systems A/S
Publication of WO2018153418A1 publication Critical patent/WO2018153418A1/fr

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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F05B2260/30—Retaining components in desired mutual position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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 main rotor shaft for a wind turbine, and particular an arrangement for a main bearing for use with that shaft.
  • HAWT horizontal axis wind turbine
  • the centrepiece of the wind turbine can be considered to be the main rotor shaft, since it carries the hub and rotor blades and harnesses the rotational energy generated by the blades so that it can be converted to electrical energy by the generator.
  • the main rotor shaft is typically designed to with a life comparable to the rated lifetime of the wind turbine itself, which is usually in the region of 20 years.
  • the main rotor shaft extends through a main shaft or 'bearing' housing and is rotatably supported within that housing by two main shaft bearings: a forward bearing supports the end of the shaft near to the hub, that is the 'front' or 'forward' end, and a rear bearing support the end of the shaft distal from the hub, that is the 'back' or 'rear' end.
  • the bearings function to ensure that the main rotor shaft can rotate smoothly and also transfers axial loads and bending moments to a bed-plate or base-frame via the main bearing housing.
  • This arrangement is generally effective at decoupling the gearbox of the wind turbine from the axial and bending forces of the main rotor shaft, so that only torque is transferred to the gearbox.
  • the trend towards heavier blades and hubs means that the main rotor shaft and, therefore, the supporting bearings, are required to deal with higher loads, and so there is constant pressure to design the rotor shaft assemblies to handle the loads more effectively.
  • the invention provides a main rotor arrangement for a wind turbine, comprising a main rotor shaft that extends in an axial direction and includes a hub connection flange at its hub- connection end, wherein the hub connection flange extends radially inwardly so as to transition into a generally cylindrical shaft region, wherein the shaft region includes a bearing abutment.
  • a forward bearing includes an inner ring, an outer ring and a roller set, wherein the inner ring is carried on the shaft region and abuts against the bearing abutment.
  • a retainer element is attachable to the shaft region and is configured to prevent circumferential movement of the inner ring relative to the main rotor shaft.
  • the main rotor arrangement of the invention is to be considered in the context of a utility- scale wind turbine, which would typically have a power rating of at least 1 MW.
  • the invention therefore extends to such a wind turbine comprising a main rotor arrangement in accordance with the invention.
  • a benefit of the invention is that the retainer element provides an elegant means to guard against circumferential 'creep' of the bearing relative to the shaft. Such a 'creep' phenomenon can occur under heavy bearing loads and can cause undesirable wear at the interface between the shaft and the bearing.
  • the size and relative dimensions of the main rotor shaft may be such that the diameter of the second shaft portion may fall in the range of 80% and 98% of the diameter of the first shaft portion; and the diameter of the first shaft portion may fall in the range of 25% and 200% of the length of the main rotor shaft.
  • the retainer element may be removably fastened to the shaft region by any means, for example by bolts or a bonding medium.
  • the retainer element may take the form of relatively thin structures that are positioned on the shaft, extend towards the bearing and so as to engage the bearing in some way to prevent circumferential movement thereof. Several such retainer elements of this type may be used to increase the force with which circumferential creep can be prevented.
  • the retainer element may extend circumferentially, and so be shaped like a partial ring. Two or more such ring-like components can be joined together to provide a retaining ring that extends about the shaft, is connected thereto, and engages with the bearing so prevent circumferential creep.
  • the retainer element may have an arm portion that opposes the bearing and includes engagement means for engaging bearing, and particularly the inner ring thereof.
  • the engagement means may include a locking element that cooperates with the retainer element and the bearing so as to lock the bearing to the retainer element.
  • the engagement element may be in the form of a pin or bolt, that is received through corresponding holes in the bearing and retainer element, but it may also be in the form of cooperating/meshing teeth, for example.
  • Figure 1 is a front view of a wind turbine, comprising a main rotor arrangement according to the invention
  • Figure 2 is a schematic view of a drivetrain of the wind turbine of Figure 1 , including a main rotor arrangement;
  • Figure 3 is a perspective view of a main rotor arrangement;
  • Figure 4 is a longitudinal section view of the main rotor arrangement comprising known arrangements of main shaft and main bearings;
  • Figure 5 is an illustrative view of a main shaft arrangement in accordance with an embodiment of the invention
  • Figure 6 is a perspective view of a portion of a main rotor shaft in accordance with an embodiment of the invention.
  • Figure 7 is a perspective view of a locking member of a main shaft arrangement in accordance with an embodiment of the invention in isolation.
  • the present invention relates to an improved arrangement for a main bearing and main rotor shaft of a wind turbine.
  • the arrangement includes a retainer element that is configured to apply an axial retaining force to the main bearing to prevent axial and circumferential movement of the bearing on the rotor shaft.
  • a wind turbine 2 includes a nacelle 4 that is supported on a generally vertical tower 6, which is itself mounted to a foundation 8.
  • the foundation 8 may be on the land, or wholly or partially underwater.
  • the nacelle 4 houses a number of functional components, some of which are shown schematically in Figure 2, by way of example. Such a configuration would be well known to a skilled person.
  • the nacelle 4 is shown as housing at least in part, the main rotor arrangement 10, a gearbox 12 and a generator 14.
  • the main rotor arrangement 10 for example a power converter and yaw drive.
  • the presence of such components is implicit and such component would be well understood by the skilled reader.
  • the main rotor arrangement 10 includes a hub 16 coupled to a main rotor shaft 18, which is rotatably supported in a main shaft housing 20 by a bearing arrangement 22.
  • the main shaft housing 20 is sometimes referred to in the art as a main bearing housing, and will be referred to as such from now on.
  • the bearing arrangement 22 comprises a forward bearing 24 and a rear bearing 26.
  • the hub 16 is connected to a plurality of rotor blades 27, although three blades are typical in a HAWT. The blades 27 are acted on by the wind and therefore torque is applied by the hub 16 to the main rotor shaft 18 which causes it to rotate within a main bearing housing 20.
  • An input or 'forward' portion of the main rotor shaft 18 comprises a hub connection flange 18a, by which means the main rotor shaft 18 is connected to, and driven by, the hub 16.
  • the flange 18a is shown as being connected to a further flange 29 that is associated with the hub 16, such that the two flanges form a coupling between the hub 16 and the main rotor shaft 18.
  • the flange 18a can therefore be considered to be at the hub-connection end of the main rotor shaft 18.
  • An output portion 18b of the shaft 18 provides input drive to the gearbox 12.
  • the gearbox 12 steps up the rotational speed of the main rotor shaft 18 via internal gears (not shown) and drives a high-speed gearbox output shaft 28.
  • the high-speed output shaft 28 in turn drives the generator 14, which converts the rotation of the high-speed output shaft 28 into electricity.
  • the electrical energy generated by the generator 14 may then be converted by other components (not shown here) as required before being supplied to the grid, for example, or indeed any electrical consumer. So-called "direct drive" wind turbines that do not use gearboxes are also known.
  • the gearbox 12 may therefore be considered optional.
  • the main bearing housing 20 is supported on a base frame 30, which can also be known as a bed plate.
  • the base frame 30 may be coupled to a yaw drive at the upper part of the wind turbine tower 6 to enable the base frame 30 and, thus, the entire nacelle 4 to yaw with respect to the tower 6 so as to enable the direction of the hub 16 to be adjusted with respect to the wind direction.
  • the base frame 30 is typically a cast component, for example of iron or steel, and has the function to transfer the main shaft loads from the shaft 18, through the bearings 24, 26, the main bearing housing 20, and the base frame 30, and into the wind turbine tower 6.
  • Figures 3 and 4 illustrate a more practical realisation of a main bearing housing 20 and main rotor shaft 18 for a better understanding of the configuration of the relevant components.
  • the main rotor shaft 18 is tapered along its length to provide a relatively larger circumference at the forward end 32 of the shaft 18 and a relatively smaller circumference at the rearward end 34 of the shaft 18. It should be noted that it is not essential that the main rotor shaft 18 is tapered. However, this configuration may provide certain advantages as it allows the shaft 18 to support a larger forward bearing 24, capable of more effectively managing the substantial loads applied to it in use.
  • the forward and rear bearings 24, 26 are situated between the main rotor shaft 18 and main bearing housing 20, at forward and rearward positions respectively along the length of the shaft 18.
  • the forward and rear bearings 24, 26 together enable the main rotor shaft 18 to freely rotate with respect to the main bearing housing 20 during wind turbine operation, about a rotor axis R that extends through the centre of the main rotor shaft 18.
  • the forward and rear bearings 24, 26 each include an inner ring 36, an outer ring 38 and a plurality of generally cylindrical rolling elements 40, more simply referred to as rollers, supported therebetween.
  • the inner ring may sometimes in the art be referred to as a cone, whereas the outer ring may sometimes be referred to as a cup.
  • a typical wind turbine bearing, for use in utility-scale applications, typically exceeding 1 MW in power output, must withstand high loads and operate reliably over an extended lifetime.
  • the forward and rear bearings 24, 26 are tapered roller bearings having tapered inner and outer races 42, 44 and tapered rolling elements 40 designed to accommodate combined axial and radial loads.
  • bearings in practice would also include a roller cage that keeps the rollers is a spaced configuration about the circumference of the cup and cone of the bearing, although this feature is not illustrated here for clarity.
  • different types of bearings may be used, for example cylindrical roller bearings or spherical roller bearings (not shown).
  • Cylindrical roller bearings utilise rows of cylindrical rolling elements that are in linear contact with races of the inner and outer rings.
  • Spherical roller bearings include two rows of barrel- shaped rolling elements, which are supported between an outer race and two inclined inner ring races.
  • the main bearing housing 20 comprises a front flared portion 46 that defines a forward bearing seat 48 and a rear flared portion 50 that defines a rear bearing seat 52.
  • the main rotor shaft 18 includes a forward bearing retainer 54 or 'rib' for retaining the forward bearing 24 in the front bearing seat 48 and a rear bearing retainer groove 56 for holding a backing element such as a rear bearing clip 58, circlip, lock nut or similar structure that retains the rear bearing 26 in the rear bearing seat 52.
  • a standard forward bearing retainer 54 of the current state of the art may comprise a rib 60 in the form of a protrusion that extends radially outwards from an outer surface 62 of the main rotor shaft 18, and extends about the entire circumference of the main rotor shaft 18.
  • This retaining rib 60 includes an abutment surface (not shown) facing away from the forward (hub) end 32 of the shaft 18, against which a corresponding abutment surface (not shown) of the inner ring 36 of the forward bearing 24 contacts in use.
  • the forward bearing 24 is located at the correct position along the length of the shaft 18, and is prevented from drifting towards the hub-end 32 of the shaft 18 during operation.
  • this configuration provides no means for preventing axial or circumferential movement of the forward bearing 24 on the rotor shaft 18. That is to say, the forward bearing 24 of the main rotor arrangement 10 described above is not restricted from shifting about the circumference of the main rotor shaft 18 or from shifting away from the hub-end of the main rotor shaft 18 in an axial direction along the main rotor shaft during wind turbine 2 operation. Movement of the bearing 24 from its correct position may result in damage to the bearing 24 or other turbine components, and may impair proper operation of the wind turbine 2.
  • the above-described arrangement presents challenges in terms of the processing time and material cost associated with machining the retaining rib 60 into the main rotor shaft 18.
  • the retaining rib 60 must be precisely dimensioned and positioned on the shaft 18, resulting in strict tolerance requirements that increase the cost and time required to produce this retaining feature 54.
  • any enhancement to the configuration of the main rotor arrangement 10 to address these issues would be beneficial.
  • Figure 5 shows a main rotor arrangement 10 in accordance with an embodiment of the present invention. Specifically, Figure 5 shows a portion of the main rotor arrangement 10 in the vicinity of the forward bearing 24. At its outermost point, the flange 18a is in a plane that is perpendicular to the axis of the rotor shaft 18.
  • the hub connection flange 18a of the main rotor shaft 18 extends radially inwardly towards the rotor axis R (shown in Figure 2) such that the flange 18a transitions along the length of the shaft into a generally cylindrical shaft region 67 including a first shaft portion 68 having a first diameter and a second shaft portion 70 having a second diameter.
  • the first shaft portion 68 transitions to the second shaft portion 70 at a bearing abutment 72, the first and second shaft portions 68, 70 being spaced axially along the rotor shaft 18.
  • the bearing abutment 72 takes the form of a shoulder that defines a step extending about the circumference of the rotor shaft 18 between the first and second shaft portions 68, 70, such that the second diameter of the second shaft portion 70 is smaller than the first diameter of the first shaft portion 68.
  • the shoulder 72 provides a shoulder surface 74 against which the forward bearing of the main rotor arrangement abuts in use.
  • This configuration of the main rotor shaft 18 is further illustrated in Figure 6, which shows a portion of the main rotor shaft 18 in isolation from the main shaft housing 20 and bearings 24, 26.
  • the diameter of the first shaft portion 68 is approximately 1600mm, whereas depth of the shoulder 72 is approximately 80mm, although it is envisaged that the depth should be no greater than 100mm.
  • the diameter of the second shaft portion 70 is approximately 95% of the diameter of the first shaft portion 68.
  • the diameter of the first shaft portion 68 of the main rotor shaft 18 is approximately 50% of the length of the main rotor shaft 18. It should be noted that these dimensions are specific to this embodiment, and may vary in other embodiments on the invention.
  • the diameter of the second shaft portion 70 may fall anywhere in the range of 80% and 98% of the diameter of the first shaft portion 68, and the diameter of the first shaft portion 68 may fall anywhere in the range of 25% and 200% of the length of the main rotor shaft 18.
  • the shoulder surface 74 provides the transition region between outer surfaces 76, 78 of the first and second shaft portions 68, 70, respectively.
  • the shoulder surface 74 is substantially perpendicular to the outer surfaces 76, 78 of the first and second shaft portions 68, 70, but it should be noted that this is not essential.
  • the shoulder surface 74 may be inclined with respect to the outer surfaces 76, 78 such that, in some embodiments, the shoulder surface 74 forms an angle with the outer surface 78 of the second shaft portion 70 that is up to 10° off-vertical.
  • the shoulder surface 74 may be inclined to provide either a slope or an overhanging ledge between the first and second shaft portions 68, 70. In this way, the shape and size of the shoulder 72 may vary, provided the shoulder 72 is still able to perform its required function as a robust stop for the inner ring 36 of the forward bearing 24.
  • the inner ring 36 of the forward bearing 24 comprises a slanting radially outer surface 80 defining an inner ring raceway or track 82 in which the rolling elements 40 of the forward bearing 24 are received and guided between front and rear guiding ribs or flanges 76a, 76b defined by respective walls or ribs 88.
  • the inner ring also defines a stepped radially inner surface 84 that includes a shoulder abutment surface 86 of the inner ring 36.
  • the side ribs 88 of the inner ring 36 comprise a first, relatively large side rib 90 and a second, relatively small, side rib 92, where the first side rib 90 is located closer to the hub-end 32 of the main rotor shaft 18 than the second side rib 92 when assembled on the rotor shaft 18 for use.
  • the inner ring 36 of the forward bearing 24 further includes two openings provided at opposing sides of the inner ring 36; a first opening 94 provided in the shoulder abutment surface 86 of the inner ring 36 and a second, fastener-receiving opening 96 located on the opposing second side rib 92 of the inner ring 36.
  • the first and second openings 94, 96 may be used during transport of the bearing 24.
  • the main rotor arrangement 10 further comprises a retainer element 98.
  • the retainer element 98 is configured to retain the forward bearing 24 in its correct circumferential position along the main rotor shaft 18 of the wind turbine 2 during operation, such that the forward bearing 24 sits between the retainer element 98 and a corresponding retaining feature of the main rotor shaft 18 in use (for example, a shoulder 72 or retaining rib 60 of the main rotor shaft).
  • the retainer element 98 is positioned next to the forward bearing 24 on the main rotor shaft 18, and may abut or brace against the forward bearing 24 to prevent the forward bearing 24 from moving circumferentially on the main rotor shaft 18 during use.
  • the retainer element 98 may include e.g.
  • a pin or bolt for engaging with a corresponding feature of the inner ring 36, as will be described later.
  • Other forms of engagement means, such as teeth, are also envisaged.
  • just a single retainer element 98 may be included in the arrangement 10, or a plurality of retainer elements 98 may be equally spaced about the circumference of the main rotor shaft 18 to ensure the forward bearing 24 does not drift out of position at any point about the shaft 18.
  • Another possible alternative is to provide the retainer element 98 in two semi-circular parts configured to form a closed loop or ring when assembled on the main rotor shaft 18 for use.
  • the retainer element 98 may also function to prevent axial movement of the forward bearing 24 on the main rotor shaft 18.
  • the retainer element 98 comprises a main body 100 including a shaft attachment portion 102 and a retaining arm 104.
  • the shaft attachment portion 102 and arm 104 of the retainer element 98 are provided at opposing ends of the main body 100 and each include a fixing hole 106 for receiving a bolt or screw (or other appropriate fastening means) in use.
  • the shaft attachment portion 102 transitions to the main body 100 at an elbow 109 such that the main body 100 is slightly angled with respect to the shaft attachment portion 102.
  • the shape of the retainer element 98 corresponds to the shape of the rotor shaft 18 in the region of the shaft 18 on which the retainer element 98 sits in use.
  • the angle between the main body 100 and the shaft attachment portion 102 of the retainer element 98 may vary in dependence on the shape of the main rotor shaft 18.
  • the arm 104 is provided as a flange extending from the main body 100 of the retainer element 98.
  • a retaining portion 105 of the arm 104 may abut or brace against the inner ring 36 of the forward bearing 24 to secure the inner ring 36 in position on the rotor shaft 18.
  • the retainer element 98 may be positioned to provide a small gap between the arm 104 and the inner ring 36.
  • retainer elements 98 are included in the main rotor arrangement 10, spaced equidistantly about the circumference of the main rotor shaft 18 to prevent the forward bearing 24 from shifting away from the rotor shaft shoulder 72 about the circumference of the shaft 18.
  • other embodiments of the invention may include fewer retainer elements 98, or additional retainer elements 98.
  • the retainer elements 98 may not be spaced equidistantly from each other about the circumference of the main rotor shaft 18, but may be clustered or spaced at varying intervals about the circumference of the rotor shaft 18.
  • the retainer element 98 may also be configured to extend a significant way about the circumference of the shaft, so as to be shaped like a ring, either fully or in part.
  • the shape and dimensions of the retainer element 98 may also vary in other embodiments of the invention in dependence on, for example, the corresponding shape of the rotor shaft 18 in the region of the retainer element or the required strength of the retainer element for a forward bearing 24 of a given size.
  • the forward bearing 24 is positioned between the main rotor shaft 18 and the main shaft housing 20, and is received in the forward bearing seat 48.
  • the inner ring 36 of the forward bearing abuts the shoulder 72 of the main rotor shaft 18, such that the shoulder abutment surface 86 of the inner ring 35 bears against the shoulder surface 74 of the rotor shaft 18.
  • the retainer element 98 is positioned so that the arm 104 abuts or opposes the second side rib 92 of the inner ring 36.
  • Fasteners 108 are received in the fixing holes 106 of the arm 104 and the rotor attachment portion 102 to secure the retainer element 98 to the inner ring 36 of the forward bearing 24 and to the main rotor shaft 18.
  • the retainer element 98 is removably attached to the forward bearing 24 and rotor shaft 18 by means of screws.
  • other appropriate engagement means 108 may be used in other embodiments.
  • pins or dowels may removably attach the retainer element 98 to the forward bearing 24 or main rotor shaft 18, or a more permanent attachment method such as gluing or riveting may be used.
  • the retainer element 98 may be secured to the forward bearing 24 and/or rotor shaft 18 by means of cooperative gripping features, for example serrations or teeth, provided on the retainer element 98, bearing 24, and/or main rotor shaft 18.
  • the retainer element 98 may be attached to the forward bearing 24 using different fastening means to those used to attach the retainer element 98 to the main rotor shaft 18.
  • the retainer element 98 acts to retain the inner ring 36 in abutment with the bearing abutment 72 of the main rotor shaft 18.
  • the retainer member 98 retains the forward bearing 24 in its correct circumferential position on the main rotor shaft 18 and thereby prevents movement of the forward bearing 24 in a circumferential direction about the surface of the rotor shaft 18.
  • the retainer member 98 may be configured to engage with the forward bearing 24 in various different ways.
  • the retaining member 98 may be configured to apply an axial force on the forward bearing 24 to retain the bearing 24 in place.
  • a small gap may separate the retainer element 98 from the forward bearing 24 when assembled on the main rotor shaft 18 for use, such that the retainer element 98 guards against significant movement of the forward bearing 24 without initially contacting the forward bearing 24. This arrangement allows the retainer element 98 to be less precisely positioned on the main rotor shaft 18 on assembly and allows the forward bearing to elastically deform due to external loading or an intentional preload.
  • the retainer element 98 is not limited for use on the specific main rotor shaft 18 arrangement that has been described in the above embodiment.
  • the retainer element 98 may be included in an arrangement in which the main rotor shaft 18 is provided with a forward bearing retainer 54 in the form of a retaining rib 60 (as is standard in the current state of the art), rather than the bearing abutment 72 described in the above embodiment of the invention.

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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)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un agencement de rotor principal pour une éolienne, comprenant un arbre de rotor principal qui s'étend dans une direction axiale et comprend une bride de raccordement de moyeu au niveau de son extrémité de raccordement de moyeu, la bride de raccordement de moyeu s'étendant radialement vers l'intérieur de façon à passer dans une région d'arbre généralement cylindrique, la région d'arbre comprenant une butée de roulement. Un roulement avant comprend une bague interne, une bague externe et un ensemble de rouleaux, la bague interne étant portée sur la région d'arbre et venant en butée contre la butée de roulement. Un élément de retenue peut être fixé à la région d'arbre et est conçu pour empêcher un mouvement circonférentiel de la bague interne par rapport à l'arbre de rotor principal. L'agencement de rotor principal selon l'invention doit être envisagé dans le contexte d'une éolienne à grande échelle qui a typiquement une puissance nominale d'au moins 1 MW. Un avantage de l'invention est que l'élément de retenue fournit un moyen élégant pour protéger contre le "fluage" circonférentiel du roulement par rapport à l'arbre. Un tel phénomène de "fluage" peut se produire sous des charges de roulement lourdes et peut provoquer une usure indésirable au niveau de l'interface entre l'arbre et le roulement.
PCT/DK2018/050023 2017-02-21 2018-02-02 Agencement de rotor principal d'éolienne ayant des moyens pour empêcher le fluage angulaire d'un anneau de roulement externe WO2018153418A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA201770127 2017-02-21
DKPA201770127 2017-02-21

Publications (1)

Publication Number Publication Date
WO2018153418A1 true WO2018153418A1 (fr) 2018-08-30

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633190A1 (fr) * 2018-10-01 2020-04-08 Siemens Gamesa Renewable Energy A/S Agencement de palier d'une éolienne, éolienne et procédé de fabrication d'une éolienne
CN113757263A (zh) * 2021-08-13 2021-12-07 太原重工股份有限公司 风力发电机组的主轴轴承座
WO2023062145A1 (fr) 2021-10-15 2023-04-20 thyssenkrupp rothe erde Germany GmbH Ensemble palier principal pour éolienne
BE1029857B1 (de) * 2021-10-15 2023-05-15 thyssenkrupp rothe erde Germany GmbH Hauptlageranordnung für eine Windenergieanlage

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DE102004058905A1 (de) * 2004-12-07 2006-06-14 Aktiebolaget Skf Wälzlager mit segmentierten Lagerringen
DE102009015827A1 (de) * 2009-04-01 2010-10-07 Ab Skf Lageranordnung zur drehbaren Lagerung eines Maschinenteils und Verfahren zum Fixieren eines Kegelrollenlagers an einem Maschinenteil
WO2014031055A1 (fr) * 2012-08-21 2014-02-27 Aktiebolaget Skf (Publ) Ensemble arbre de rotor d'éolienne comprenant une partie de fixation à expansion
EP2754893A1 (fr) * 2012-06-29 2014-07-16 Mitsubishi Heavy Industries, Ltd. Procédé d'assemblage d'une ligne d'arbres d'un dispositif générateur de puissance à énergie récupérée, et outil d'assemblage d'une ligne d'arbres
EP2772646A2 (fr) * 2013-02-28 2014-09-03 Mitsubishi Heavy Industries, Ltd. Eolienne

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004058905A1 (de) * 2004-12-07 2006-06-14 Aktiebolaget Skf Wälzlager mit segmentierten Lagerringen
DE102009015827A1 (de) * 2009-04-01 2010-10-07 Ab Skf Lageranordnung zur drehbaren Lagerung eines Maschinenteils und Verfahren zum Fixieren eines Kegelrollenlagers an einem Maschinenteil
EP2754893A1 (fr) * 2012-06-29 2014-07-16 Mitsubishi Heavy Industries, Ltd. Procédé d'assemblage d'une ligne d'arbres d'un dispositif générateur de puissance à énergie récupérée, et outil d'assemblage d'une ligne d'arbres
WO2014031055A1 (fr) * 2012-08-21 2014-02-27 Aktiebolaget Skf (Publ) Ensemble arbre de rotor d'éolienne comprenant une partie de fixation à expansion
EP2772646A2 (fr) * 2013-02-28 2014-09-03 Mitsubishi Heavy Industries, Ltd. Eolienne

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633190A1 (fr) * 2018-10-01 2020-04-08 Siemens Gamesa Renewable Energy A/S Agencement de palier d'une éolienne, éolienne et procédé de fabrication d'une éolienne
CN113757263A (zh) * 2021-08-13 2021-12-07 太原重工股份有限公司 风力发电机组的主轴轴承座
WO2023062145A1 (fr) 2021-10-15 2023-04-20 thyssenkrupp rothe erde Germany GmbH Ensemble palier principal pour éolienne
BE1029857B1 (de) * 2021-10-15 2023-05-15 thyssenkrupp rothe erde Germany GmbH Hauptlageranordnung für eine Windenergieanlage

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