WO2015018382A1 - Ensemble palier de pale - Google Patents

Ensemble palier de pale Download PDF

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Publication number
WO2015018382A1
WO2015018382A1 PCT/DE2013/000447 DE2013000447W WO2015018382A1 WO 2015018382 A1 WO2015018382 A1 WO 2015018382A1 DE 2013000447 W DE2013000447 W DE 2013000447W WO 2015018382 A1 WO2015018382 A1 WO 2015018382A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing assembly
connection element
bearing
blade
toothed
Prior art date
Application number
PCT/DE2013/000447
Other languages
German (de)
English (en)
Inventor
Hubertus Frank
Erwin RUSS
Volker Dietz
Original Assignee
Imo Holding 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 Imo Holding Gmbh filed Critical Imo Holding Gmbh
Priority to PCT/DE2013/000447 priority Critical patent/WO2015018382A1/fr
Priority to DE112013007311.0T priority patent/DE112013007311A5/de
Publication of WO2015018382A1 publication Critical patent/WO2015018382A1/fr

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
    • 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
    • F03D1/0658—Arrangements for fixing wind-engaging parts to a hub
    • 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
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • F03D7/0224—Adjusting blade pitch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/74—Adjusting of angle of incidence or attack of rotating blades by turning around an axis perpendicular the rotor centre line
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/76—Adjusting of angle of incidence or attack of rotating blades the adjusting mechanism using auxiliary power sources
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/79—Bearing, support or actuation arrangements therefor
    • 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 is directed firstly to a blade bearing or a compact blade bearing assembly for the rotatable mounting of a rotor blade on the hub of a wind turbine with a device for adjusting the rotor blade pitch, comprising two rotationally symmetrical connection elements, each with a flat connection surface for non-rotatable connection to two different Machine or system elements or to a machine or system element on the one hand and a chassis or foundation on the other hand, wherein the two rotationally symmetrical connection elements are aligned such that their axes of symmetry coaxially to each other and their connection surfaces are remote from each other, wherein further between the two connection elements, a gap wherein at least one rolling bearing is arranged as a main bearing for supporting the two connecting elements to each other, rotatably about a main bearing axis of rotation, which the common axis of symmetry of both Ans corresponds to flow elements, and wherein at least one lateral surface of a connecting element is provided with a completely running toothing; and on the other to a wind turbine with
  • WKA wind energy or wind turbines
  • a wind turbine which is rotatably mounted about an approximately horizontal rotor axis, which is adjustable within a horizontal plane and thereby the respective wind direction trackable, so in that it always runs approximately parallel to this.
  • This wind turbine carries at its hub a plurality of elongate rotor blades whose longitudinal axis of the rotor axis projects approximately radially.
  • Such wind turbines are also a tower and a rotatable nacelle at its upper end; on the nacelle, the hub of the wind turbine with the rotor blades is stored.
  • Such wind turbines serve the technical principle of initially transferring the energy of the wind-induced air flow into the mechanical rotational energy of the rotating wind turbine and then converting it into the electrical energy form as a rule.
  • generators are used for the latter, which are either mounted directly on the shaft of the rotating hub or drive a generator via a main gear.
  • the rotor blades are rotatably mounted on the hub, in particular rotatable about its longitudinal axis, and can thereby be rotated as needed in and out of the wind, whereby the inflow area is varied .
  • Such modern wind turbines are so called in terms of the wind direction tracking and angle of attack, also known as pitch in the art, adjustable. With several rotor blades, these are offset by approximately the same angle about the rotor axis. Due to the high altitude of modern wind turbines, therefore, each rotor blade generally experiences different wind conditions; this applies in particular to the wind speeds, as these can sometimes vary considerably depending on the current height of the relevant rotor blade over ground.
  • a single blade adjustment is preferred, that is, the angle of attack is adjustable for each rotor blade independently of the angles of incidence of the other rotor blades.
  • an adapter for securing rotor blades of a wind turbine to a rotor hub.
  • This adapter has an approximately cylindrical jacket-shaped shape, whose two end faces serve as connecting surfaces for connection to the hub on the one hand and to the rear end of the relevant rotor blade on the other hand.
  • the hub-facing end face is a ring of a moment bearing screwed, on which two round-running ball rows a second ring is rotatably mounted. That second ring is toothed on its inner side, and with this toothing meshes a pinion of a drive motor whose housing is fixed to an inwardly projecting collar of the adapter.
  • the drive motor itself is located - as well as these driving circuit elements - within the adapter.
  • the adapter gets a large height, which corresponds approximately to its radius or even larger than that.
  • This known adapter brings a number of disadvantages: On the one hand shortens its high height, the aerodynamically usable inflow surface of the rotor blade; On the other hand, the motor rotates with the adapter, so it is not firmly mounted on the hub, but on the adapter itself.
  • the pinion is supported by the all-round toothing of the adapter ring connected to the rotor hub and thus presses the motor or transmission housing in the appropriate direction away, and this movement is finally passed from the relevant housing via its anchorage to the adapter itself, and finally transmitted by means of the same to the relevant rotor blade.
  • the anchoring of the engine or transmission housing in the axial direction of the blade axis is far away from the pinion, while twisting the pinion axis are preprogrammed, including the quality of the meshing engagement between the pinion and along the ring circumferential teeth suffers, which not only increased wear but also brings with it an increased gearing game and thus can lead to regulatory technical instabilities.
  • the invention initiating problem to design a blade bearing for the rotatable coupling between the hub of the wind turbine of a wind turbine and a rotor blade such that the device for adjusting the rotor blade angle of attack as possible wear and is free of play and if possible, the distance of the blade end from the hub can be kept as low as possible, thus a maximum inflow surface of the rotor blade can be used.
  • the Inventive design provide a compact bearing sheet bearing assembly for the rotatable mounting of a rotor blade ready, which "can be transported as a whole" to the place of assembly without - as previously known from the prior art - a large amount of individual components assembled on site / must be attached.
  • the untoothed connection element has a toothing of the toothed connection element facing portion with one or more, open to the teeth cavities for receiving toothed gears, wherein in the untoothed connection element for each gear an end opening is provided whereby the respective gear is accessible to the rotary drive, as well as at least one closed ring area with this opening for supporting a arranged in the axial direction between the pads of the two connection elements storage for the respective gear as the wheel bearing, so that the respective gear around a eccentrically offset relative to the main bearing axis of rotation, but rotates about parallel to the secondary rotational axis and meshes with the toothing of the toothed connection element.
  • This integrated overall arrangement basically offers the possibility of freedom from the center and only requires a single, annular machine element in the form of the toothed connecting element, into which all the gear wheels introduce their torque.
  • the entire blade bearing assembly can be designed as a closed system. Since the gears generally have a significantly smaller diameter than the teeth of the toothed connection element and therefore significantly fewer teeth, simultaneously with the torque addition also Drehbaumunter- and a torque translation, so that from a faster speed of a rotary drive motor slower rotational movement of the rotor blade to whose longitudinal axis results. Thus, it is possible to work with a considerably more favorable speed range for electric motors, and at the same time motors with a comparatively low rated torque can be used.
  • n M / n B z A / z G ;
  • the invention allows the use of a plurality of rotary drive units for controlling the flow of energy between the rotor blade and the rotor hub, which are preferably arranged uniformly or at least symmetrically with respect to the main axis of rotation, so that no imbalance inherent in the system can arise therefrom.
  • a certain amount of redundancy can be provided by a plurality of such rotary drive units, and, moreover, the necessary control energy can be divided into a plurality of drive units, which can thereby be built considerably more easily and are thus significantly cheaper.
  • two rotary actuators can be set to minimum setpoint values that are shifted from each other so that they reach a medium setpoint value to work against each other;
  • two rotary actuators can be set to minimum setpoint values that are shifted from each other so that they reach a medium setpoint value to work against each other;
  • different or even mutually opposite forces are introduced into the relevant rotor blade via the respective tooth engagement, so that a mutual tension is built up, as a result of which the rotor blade is clamped completely without play.
  • Another advantage is the increased ease of assembly and disassembly of the invention, since you only need a substantially closed blade bearing assembly, including all force-transmitting elements, preferably under separate design of subsequently attachable or flanged hydraulic, gear or electric motors.
  • the invention is not an interconnection of individual components and combinations, as described in the prior art, but a flat, cylindrical or annular assembly, in particular as a ready to install overall arrangement, what directly the hub, a rotor blade and a or multiple rotary actuators can be connected to adjust the angle of attack.
  • the present invention provides a universal assembly as part of a wind turbine in the form of a complete assembly ready for installation for transmitting energy from mechanical forces and moments from a rotor blade to the hub, wherein the amount of energy absorbed by the flowing air can be influenced by the coupled to the control ports rotary drive units ,
  • the leaf bearing assembly according to the invention has at least one first main rolling bearing ring, in particular as an inner or outer ring of a multi-row large roller bearing or moment bearing, and at least one second Mannicalzlagerring, in particular as an inner or outer ring of a preferably multi-row large roller bearing or moment bearing;
  • the assembly further has at least one raceway with rolling elements, wherein the respective at least one raceway, the Haupticalzlagerringe rotatably supported against each other. It is characteristic that one of the mechanical elements present for the transmission of energy from mechanical forces and moments from the blade side to the hub side, namely one of the two main roller bearing rings, is toothed and at the same time carries at least one of said race
  • the blade bearing assembly according to the invention has centerlessness, ie, has a central opening around the main bearing axis, which can of course optionally be closed by cover plates or other housing, but also when needed a simplified access, for example, to the rotor blade of a wind turbine allows. Sensor signal lines or other lines can also be placed in this center.
  • a rotor blade can even be walked on through the middle duct, so that a service technician can enter the rotor blades through the hub from the side of the machine carrier and thus reach all the essential parts of a wind turbine.
  • the height L of the assembly according to the invention ie the axial extent between its two pads, are kept very low, in particular smaller than the radial extent of the ring cross-sections from its outermost periphery to the clear opening in the middle, if necessary with removed cover plates.
  • the rotor blades Due to this low height L, the rotor blades can be moved very close to the hub, and therefore is available for a given diameter of the wind turbine, a maximum flow area per rotor blade for the conversion of wind energy into mechanical energy available.
  • the energy to be supplied to the control rotary connections is normally smaller by a multiple than the energy flowing to the hub and usable there.
  • the leaf bearing according to the invention is - optionally with the exception of a central opening around its main or center axis - preferably enclosed by a housing at least on one side.
  • the connection elements are designed in the manner of an inner and outer ring of a preferably multi-row large roller bearing, each having at least one raceway for rolling elements, so that the connection elements are rotatably mounted against each other, forming a bearing gap.
  • a pinion in particular each of the existing pinion can be partially enclosed by a separate pinion housing, but is at least radially completed from the main axis of rotation, so that the respective pinion against physical interference from the radial center of the Cylindrical or annular overall arrangement is protected here.
  • the protective effect should be such that the pinion housing is substantially only subject to engagement with the respective meshing element.
  • the pinion housing can be made in one piece or several pieces, in particular, a design as a concentric around the center axis housing ring is conceivable. This can be integrated with the untoothed connection element or be connected to this, for example on and unscrewed or flanged.
  • this acting as a pinion housing ring portion can also be designed as a coaxial extension of the relevant connection element itself, in particular as a single casting.
  • Recesses and / or holes can be provided for receiving the gear wheels or pinions, ie exactly where a pinion should be inserted during assembly or disassembly.
  • the drive-side cover plate is not physically connected to the pinion housing, but preferably non-rotatably connected to the toothed connection element. Therefore remains within the housing thus enclosing a gap to the not with the relevant mounting side with rotating connection element or pinion housing, which ensures a smooth twistability between these elements.
  • the toothing is arranged on the radially inner lateral surface of the inner ring, so that the transmission gears are located radially within the inner ring and the blade bearing according to the invention has only a minimal space requirement. Incidentally, this smaller design usually goes hand in hand with a lower weight, which is not insignificant especially in the wind turbine of a wind turbine.
  • large rolling bearing used in the following refers to a moment bearing of mechanical and plant engineering, which can accommodate both axial, radial and tilting moment loads.
  • the untoothed connection element is configured in such a case in the manner of a non-toothed outer ring of a large roller bearing and can be assembled from several parts, if this is necessary or advantageous for assembly reasons, for example.
  • a gap for the sealing of which a sealing system may be present, preferably in the form of an annular sealing system, for example comprising at least one circumferential sealing ring with at least one sealing lip, or else comprising a system of two or more in the gap direction arranged one behind the other sealing rings.
  • a complete seal of the entire leaf bearing allows this with a lubricant, preferably lubricating grease, partially or completely to fill, in order to optimize its running properties.
  • a lubricant preferably lubricating grease
  • the housing part is preferably designed as a dynamically loadable component of the untoothed main rolling bearing ring of the main bearing of the blade bearing assembly according to the invention, on the track of which the rolling elements, such as roller, ball, cylinder, barrel or conical rolling elements, roll.
  • the shape of a three-row roller bearing is preferred.
  • Said housing part can be an integral part of the untoothed ring of the main bearing of the sheet bearing assembly according to the invention be; It could be made in one piece with that or positively or positively or positively and non-positively coupled to the respective ring of the main bearing or at least be coupled, for example, together with the untoothed ring of this main bearing as a single, rockschraubbares, part executed.
  • the toothed connection element can be constructed in one piece, whereby on the one hand the assembly is simplified and on the other hand, the relevant connection element receives maximum stability.
  • At least one raceway for a row of rolling elements of the main bearing is arranged on one of the toothing opposite lateral surface of the toothed connection element.
  • a division of career on the one hand and toothing on the other hand on two lateral surfaces with the result that with minimal gearbox height a maximum meshing engagement is possible and at the same time a possibly multi-row main storage.
  • at least one track of the toothed connecting element is produced together with its toothing by preferably machining or other shaping of a single, common base body.
  • the invention is further characterized by at least one row of fastener elements distributed in a ring-like manner in the toothed connection element, in particular in the connecting surface opening blind holes with internal thread, which is preferably arranged in the radial direction between the teeth and at least one raceway for a row of rolling main bearing.
  • This makes it possible to anchor the relevant connection element by means of (fastened) in these fasteners (machine) screws or (stationary) bolt on a machine or system part or on a chassis or foundation.
  • These mounting holes of the toothed connection element can be made as well as its teeth by machining or other shaping of a single, common body.
  • toothing and / or the raceway (s) for the row of rolling elements (s) of the main bearing and / or the fastening elements in particular blind holes with internal thread, formed by machining or shaping of the same connection element body, so these machine elements in a single, common clamping of the body are incorporated, which can reach a maximum of precision.
  • the invention can be further developed to the effect that on one of the toothing opposite lateral surface of the toothed connection element, a all-round collar is provided on which one or more raceway (s) is arranged for the rolling elements of the main bearing (are).
  • a collar has a pointing in the radial direction, cylindrical edge surface and two facing in different axial directions, each flat annular surfaces, which can absorb compressive forces in different axial directions as the top and bottom of the federal government. Overall, a variety of radial and axial forces and tilting moments can record.
  • an open to a front side all-round recess for receiving the untoothed connection element is provided, which preferably has a T-shaped cross-section.
  • the untoothed connection element should have a T-shaped cross-section.
  • the cross-section of the untoothed connection element is smaller than the cross-section of the recess in the toothed connection element, it is ensured that the two connection elements can easily rotate against one another.
  • the raceways exhibiting portion of the untoothed connection element are encompassed by the toothed connection element on three sides, in particular on one of its end faces and on two lateral surfaces.
  • the toothed portion of the toothed connection element is encompassed by the non-toothed connection element on three sides, in particular on one of its end faces and on two lateral surfaces.
  • the main bearing may have several rows of rolling elements, for example.
  • each own, specially adapted rolling elements each own, specially adapted rolling elements.
  • the invention recommends that the main bearing has at least one thrust bearing with at least one row of rolling elements whose support angle is equal to or greater than 45 °. Due to their large support angle such rolling elements are optimally equipped for the transmission of axial forces and for the absorption of tilting moments.
  • the main bearing comprises a radial bearing with at least one row of rolling elements whose support angle is less than 45 °. These rolling elements are optimized for special loads, namely for about radial loads.
  • the main bearing comprises at least one row of elongated rolling elements, such as roller, barrel, needle or conical rolling elements.
  • rolling elements generally have a higher load capacity than spherical rolling elements of comparable size.
  • the rolling elements are designed to transmit axial forces as tapered rollers, in particular such that the main axis of rotation of the sheet storage facing roller end face has a smaller diameter than the main axis of rotation facing away from the roller end face. Consequently, the all-round collar on which these tapered rollers run along, have no rectangular cross-section, but a trapezoidal cross-section.
  • cylindrical rollers are also preferred for tapered roller bodies for the axial transmission of force for the transmission of radial forces or possibly spherical rolling elements.
  • the main bearing may also comprise at least one row of spherical rolling elements, preferably at least two rows of spherical rolling elements, in particular four or more rows of spherical rolling elements.
  • At least four rows of spherical rolling elements are each provided with a support angle equal to or greater than 45 °, wherein formed within a sectional plane transverse to the circumferential direction of the blade bearing assembly, the connecting lines between the four ball centers a right-angled quadrangle, in particular a rectangle or square.
  • An advantageous embodiment of the invention is that the toothed connection element is encompassed by the untoothed connection element on one of its end faces and on at least two lateral surfaces.
  • the blade bearing assembly according to the invention undergoes further optimization by fixing elements arranged in a ring-shaped manner in the untoothed connecting element, for example bores opening into its connecting surface, in particular blind holes with internal threads, which are preferably arranged in a section facing away from the toothing of the toothed connecting element.
  • fixing elements arranged in a ring-shaped manner in the untoothed connecting element, for example bores opening into its connecting surface, in particular blind holes with internal threads, which are preferably arranged in a section facing away from the toothing of the toothed connecting element.
  • raceway (s) for at least one row of rolling elements of the main bearing and / or the fastening elements For example, blind holes with internal thread, formed by machining or shaping a common (partial) body of the untoothed connection element.
  • this measure leads to a maximum of precision;
  • the raceways can be kept free of any joints along its entire circumference, which can achieve a longer service life.
  • the untoothed connection element in its toothing facing away from the cross-sectional area has a approximately aprotic or cross-sectionally approximately L-shaped or even C-shaped or T-shaped track portion having at least one, preferably directly incorporated raceway for a row of rolling main bearing.
  • Its cross-sectional shape depends primarily on the number and type of rolling element rows used. For example, in a single- or multi-row four-point bearing a skirt-like shape would be sufficient, while in a - more resilient - roller bearing with a radial row and two axial rows a C-shaped cross-section should be preferred, or even a T-shaped symmetrical cross-section, what more Arrange raceways for additional rows of rolling elements.
  • the cross-section of the untoothed connecting element may have at least one annular disk-shaped connecting portion which engages around the end face of the toothed connecting element. This is primarily responsible for non-rotatably and dimensionally stable to connect the gear teeth receiving gear portion of the untoothed connection element with its raceway section beyond the toothed connection element.
  • the non-toothed connection element in its toothing facing cross-sectional area has an approximately aprotic or cross-sectionally approximately L-shaped gear portion, which adjoins the annular disc-shaped portion and engages or receives the gears.
  • the transmission gears should be mounted primarily in recesses of the connecting part; a apron-shaped gear portion would be the gears at the main axis of rotation embrace the surrounding lateral surface and therefore protect against interventions from this direction, which is particularly important if the blade bearing is not completely closed by cover plates, but is centerless.
  • the blade bearing also has a flat, annular disk-shaped section which extends parallel to the likewise flat annular disk-shaped connecting section. In the overlapping region of these two planar sections, the gear wheels are arranged such that their axis of rotation passes through both sections. This makes it possible to store a transmission gear in or between two mutually planar sections.
  • the untoothed connection element is composed of several parts, for example of at least one raceway part, a connecting part and a transmission part. Since the untoothed connection element on the one hand surrounds the toothed connection element on three sides and on the other hand should still store the gears, it receives a very complex overall shape, which can be produced as a casting due to undercuts neither with a reasonable effort by machining. This complex shape can be subdivided to simplify their production in simpler parts, which can be made of simple basic bodies by machining or even produced as castings.
  • the transmission section has an approximately L-shaped cross-section with an all-round cavity for common reception of all gears.
  • the gear section itself has a particularly simple geometry; However, together with the connecting portion results in an undercut, which makes a one-piece production as a casting difficult or even impossible.
  • the gear portion and the connecting portion made separately and then joined together, so you can either produce the simple geometry of each of the two parts as a casting or obtained from simple basic bodies by machining and / or joining.
  • the transmission section with L-shaped cross section For example, be made by welding a flat, circular-disc-shaped part with a skirt-shaped or cylinder jacket-shaped part.
  • gear portion has a varying approximately in the azimuthal direction cross-section with a plurality of spaced apart by intermediate webs cavities for receiving one gear.
  • these webs are not essential for the dynamic function of the blade bearing assembly; However, they can increase the dimensional stability by angularly mutually extending ring sections are stiffened against each other. Such webs are created simply by the fact that the individual compartments, which each accommodate a single gear wheel, are drilled with mutual distances in a solid annular body, preferably in the axial direction.
  • an annular region closed around a secondary rotational axis is provided for supporting a wheel bearing for the respective gear wheel.
  • the / preferably annular disc-shaped connecting portion or part serve as a shield to optimally support the wheel bearing in question.
  • the invention makes use of prefabricated rolling bearings with their own raceway rings, the outer raceway ring of which is inserted into the relevant, annularly closed edge region of the untoothed connecting element.
  • this measure should in most cases be simpler than the incorporation of the raceways into the connecting element itself.
  • the invention provides an attached and fixed to the untoothed connection element mounting ring with a tapered inner cross-section, which is fixed in the axial direction of the untoothed connection element, for example. Screwed into an all-round internal thread. Due to its tapered inner diameter, such a fastening ring surrounds in any case the outer ring of a roller bearing in the axial direction and can therefore press this in the axial direction to a second, preferably similar storage.
  • gear wheel can not only be guided in the radial direction, but also be positioned in the axial direction.
  • each bearing placed in such a groove can transmit radial forces to the tapered wheel portion as well as axial forces in the direction of the radially expanded central region.
  • the flat surfaces of these grooves may be provided with an axial step, so that the radially expanded and toothed Peripheral area against the respective groove in the axial direction recedes.
  • the invention For connecting a rotary drive to a gear wheel, the invention provides in one end face of a gear at least one connection element, in particular a blind hole, the inner cross section along its circumference at least one radial extension or taper, so that a rotationally fixed connection is possible. If such has a standardized or standardized cross-section, a connection of any rotary actuators is possible, as far as they have a standard output shaft. In this case, different gears with different cross-sectional shapes of the connecting element can be kept ready and used as needed to achieve a match to the respective units to be connected. In order to form a rotary closure, it is possible, for example, to provide a round circumferential toothing, or else a groove running in the axial direction, in which a wedge can be inserted, etc.
  • a provided on the non-serrated connecting element concentric with each sub-axis of rotation or fixable base element serves to anchor the housing of a rotatably connected to the gear rotary drive.
  • the base element may have radially forward or backward jumping elements and / or screw connections od.
  • the region radially within an annular connection element can be closed by a cover, preferably approximately in the plane of the respective connection surface.
  • the toothing of the toothed connection element is located on the radially inner circumferential surface. This makes it possible for the pinions to be radially intermeshed To arrange connecting element, whereby the arrangement is particularly space-saving, while maintaining a high transmission ratio.
  • the two large, annular connection elements can protectively surround even the rather smaller gear wheels or pinions so that damage is scarcely to be feared even in extremely harsh operating conditions.
  • an imaginary, all sub-axes of rotation or symmetry center of the pinion connecting polygon can give a preferably equal or regular polygon, which increases with increasing Number of rotary actuators can approach a ring shape more than a square.
  • each of these pinions has standardized dimensions, in particular to ensure rapid interchangeability during operation.
  • the thickness of the housing part can be at least 5 mm where the pinions are positioned, but usually approximately between 50 mm to 150 mm, for large and heavy structures also up to 250 mm.
  • pinions there should be more than two such or more such pinions, for example, three or four or more such pinions, which are preferably arranged concentrically and symmetrically about the central axis of the WKA.
  • these pinions are evenly spaced from each other, wherein the distance angle is designated by angle PHI. For example, if there were four such pinions which were equally spaced, this distance or center angle would each be 90 °.
  • the existing pinion according to the invention should have identical dimensions and design, in particular a cylindrical design with an outer diameter of at least 100 mm, for example of 200 mm or more, in particular between 200 mm to 400 mm, with a height of at least 100 mm, for example of 250 mm or more, especially from about 300 mm to 500 mm.
  • the at least one-side closed housing having a central opening about its center axis may be made in one piece or in several pieces, wherein the multi-piece embodiment contains at least one cover plate which can be connected to the housing part.
  • This at least one cover plate may be of lesser thickness than the housing part, in particular of less than 50 mm thickness, said cover plate may be detachably connected to the housing part, in particular by means of screw connections.
  • this part of a casting so that this plate is completely insoluble from the housing part and rather is designed as a unit.
  • the blade bearing assembly according to the invention may have a central, for example annular, opening on a first side, wherein this aperture is generally arranged centrally about a center axis.
  • a second side in particular on the opposite side, a second cover plate may be present parallel to the housing contour of the first side.
  • This second cover plate may be of lesser strength than the housing part, for example, of lesser thickness than 50 mm, and this cover plate may be detachably connected to the housing part, or else be releasably connected in particular by means of screw connections.
  • the distance parallel to the main axis of rotation between the two outer housing end faces should be at most twice the dimension of the axial height of each pinion measured in the inner space between the two housing front sides.
  • this annular energy transfer assembly according to the invention between the two outer housing contours is approximately between about 200 mm and about 1000 mm wide.
  • the hub of a wind turbine preferably rotating about an axis extending in the wind direction of a wind turbine according to the invention is coupled to a rotor blade via a blade bearing assembly according to the invention, to which two or more rotary actuators can be connected to adjust the pitch of the rotor blade
  • the blade bearing assembly two rotationally symmetric, preferably having annular connection elements with in each case at least one flat connection surface for non-rotatably coupling to the hub of the wind turbine on the one hand and to the relevant rotor blade on the other hand, wherein the two connection elements are aligned such that their axes of symmetry coaxial with each other and their preferred pads are facing away from each other, wherein further between the two connection elements a gap
  • at least one rolling bearing is arranged as a main bearing for supporting the two connecting elements to each other, rotatably about a main bearing axis of rotation, which corresponds to the common axis of symmetry of both connecting elements, and wherein at least one lateral surface of a connecting element is provided with an
  • Such an arrangement is approximately synonymous with an overall arrangement consisting of a wind turbine, and a cylinder or annular leaf bearing assembly according to the invention for transmitting energy from mechanical forces and moments from a drive side to a driven side as part of the wind turbine of this wind turbine, neither the Blattlagerbauer still the power plant has central gear or sun gears, which overlap the main or center axis and rotate around the same;
  • such an overall arrangement comprises: one, two or more, arranged distributed around the main or center axis and each separately on the housing part on the output side fixed, each about their own axis of symmetry rotatably mounted pinion with equal distances to the center axis,
  • At least one two-row or multi-row main bearing in the manner of a large rolling bearing, for example comprising cylindrical rolling elements in cross-sectionally orthogonally oriented raceways,
  • a housing of which the blade bearing assembly according to the invention is enclosed on at least one side, in particular for the protection of the main bearing against external influences, optionally with additional attachment of several, approximately parallel to each other aligned cover plates,
  • the main bearing having at least one first main rolling bearing ring and at least one second main rolling bearing ring, the one main rolling bearing ring receiving the forces and (rotational) moments and transmitting them to the output side,
  • Main rolling bearing ring with one or more rotary actuators for adjusting the rotor blade angle of attack takes place.
  • the invention is further distinguished by the freedom of the middle and the compactness of the overall arrangement.
  • a low overall height L of the transmission according to the invention with a large diameter D is advantageous, for example with a ratio D / L> 3, wherein the diameter D is preferably about 3 m or larger, while the overall height L is preferably about 0, 5 m or less.
  • the pinions each have on at least one end face via a central concentric opening, which is adapted to accurately record a centrically arranged shaft fit and rotationally rigid to be able to transmit rotational movements with the intention.
  • Each of these pinions has at least one point of its longitudinal extent, but in particular at two different locations (above and below), each fastening options before, where the attachment of each pinion bearing is possible, in particular as a rolling or rotary joint bearing.
  • This mounting options can, for example.
  • Grooves are formed with a tapered diameter, whereupon a rolling bearing can be frictionally postponed.
  • the existing pinion according to the invention are each directly coupled or coupled, in particular coupled or coupled via a separate shaft, with at least one fastened to the housing part or can be introduced or flange-mounted rotary drive unit, such as a hydraulic motor or an electric motor.
  • these rotary drive units have in common that they can be designed as hydraulic motors for swallowing fluid media, for example highly or low-viscosity fluid media, in particular oil.
  • Each of these rotary drive units should have the same weight, on the one hand to ensure rapid interchangeability in operation and thus to increase the service capability, and on the other hand so that the wind turbine receives no imbalance.
  • the rotary drives are by means of a support structure, in particular by means of a flange, attached to the housing part or introduced or flanged so that an output shaft of the relevant rotary drive can be inserted through the center of this support structure and then extend to the respective gear, for the purpose of rotationally fixed coupling with that, with the intention of being able to influence in this way the angle of attack of the relevant rotor blade.
  • the carrier structure just mentioned can be attached or inserted or flanged directly onto the housing part, so that the fastening can be designed with conventional connecting elements, if necessary by means of detachable connecting elements, in particular Screw connections and optionally with the additional use of suitable sealing materials for sealing existing fluid media.
  • At least one ring can be inserted, in particular a clamping ring for stabilizing the position of the pinion bearing or a sealing ring for sealing.
  • the ring center is equal to the axis of rotation of the encompassed by the ring, as described above, output shaft of the respective rotary drive.
  • FIG. 1 shows a section through a blade bearing assembly according to the invention, parallel to its main axis of rotation, partially broken off;
  • Fig. 2 is a representation corresponding to Figure 1 of another embodiment of the invention.
  • Fig. 3 is a representation corresponding to Fig. 1 again modified
  • Fig. 4 is a representation corresponding to FIG. 1 another turn
  • Fig. 5a shows the detail V of FIG. 4 according to another embodiment of the
  • Fig. 5b shows detail V of Fig. 4 according to yet another embodiment of the invention.
  • Fig. 6a is a plan view of a gear wheel of the blade bearing assembly of Fig. 1;
  • FIG. 6b shows the gear wheel from FIG. 6a in a perspective view and cut along its axis of rotation;
  • FIG. 6a is a plan view of a gear wheel of the blade bearing assembly of Fig. 1;
  • FIG. 6b shows the gear wheel from FIG. 6a in a perspective view and cut along its axis of rotation;
  • FIG. 6a is a plan view of a gear wheel of the blade bearing assembly of Fig. 1;
  • FIG. 6b shows the gear wheel from FIG. 6a in a perspective view and cut along its axis of rotation;
  • FIG. 6c shows a section through FIG. 6a along the plane A-A;
  • FIG. 7 the blade bearing assembly of FIG. 1 in a perspective view seen from an end side, wherein the respective cover plate and a
  • FIG. 8 shows the blade bearing assembly from FIG. 1 in a perspective view from the driven side, wherein the section line B - B is shown, along which the section of FIG. 1 has taken place;
  • FIG. 9 shows a representation corresponding to FIG. 8, the center angle PHI being entered
  • Fig. 10 is a representation corresponding to FIG. 9 another turn
  • FIG. 1 1 a of FIG. 9 corresponding representation of a further modified
  • Embodiment of the invention such as
  • Fig. 12 is a representation corresponding to FIG. 1 a modified again
  • FIGS. 1 to 4 show various embodiments of a blade bearing assembly 1 according to the invention, which, however, do not differ in their function from one another, but only with regard to their construction in some details, which will be explained later. First of all, the mode of operation common to all three embodiments will be set forth.
  • a sheet storage unit 1 is designed as a ready-to-assembly, as part of a wind turbine with a
  • the blade bearing assembly 1 has a rotationally symmetrical structure substantially. Their essential components extend annularly around a main axis of rotation 2. In their area, the blade bearing assembly 1 at best by two approximately parallel cover plates 21, 22 completed, in the space but normally no functionally relevant parts are arranged; Preferably, this gap only serves as a reservoir for a lubricant.
  • the sheet storage unit 1 is substantially centerless and can be operated without the cover plates 21, 22 in special cases, so that could be passed through a then existing, central opening 10 around the main axis of rotation 2 cables or other cables.
  • This can be particularly important in wind turbines, since in such a short term access from the rear area of the nacelle through the hub 7 through to a rotor blade 30 is created, so that in large systems technicians can inspect the same short term.
  • annular housing part which serves the connection to a preferably fixed part of the plant, for example.
  • this annular connecting element comprises a plurality of annular sections 5, 5 ', 11 and 23, which are rigidly connected to one another in the installed state and thus are united to form a single ring.
  • connection element 5 has a flat connection surface in the form of an outer end side, which is shown in Fig. 1 bottom left.
  • connection surface lies in the installed state over a large area and flat on just such a flat connection surface of the relevant machine part, in particular the hub 7, and thus experiences a corresponding orientation.
  • fastening elements in the form of ring bores distributed in parallel around the main axis of rotation 2 are provided in the connecting surface in the form of bores parallel to the main axis of rotation 2, either through bores or at least partially provided with internally threaded blind bores.
  • connection takes place at an end face of the blade bearing 1; At the other end face a connection with the rotor blade 30 of the wind turbine is to be established. Since the rotor blade 30 is to be able to rotate relative to the hub 7, the rotor blade 30 is not fixed to the connection element 5 forming the transmission housing, but instead to a connection element 4 which is separate therefrom.
  • the terminal 4 has an annular structure, but is preferably not composed of several pieces, but integrated into a single, annular piece.
  • This connection element 4 also has a flat connection surface in the form of an outer end face, which, however, faces away from the connection surface of the connection ring 5 and is shown on the right in FIG. 1, approximately in the lower third of the drawing.
  • This connection surface is in the installed state over a large area and flat on an equally flat, rear connection surface of a rotor blade 30 and thereby contributes to a corresponding orientation of the rotor blade 30 at.
  • fastening elements in the form of bores parallel to the main axis of rotation 2, in particular completely or partially internally threaded blind bores, are also provided in the connecting surface of the second connecting element 4 in a circle around the main axis of rotation 2.
  • fastening elements in the form of bores parallel to the main axis of rotation 2 in particular completely or partially internally threaded blind bores, are also provided in the connecting surface of the second connecting element 4 in a circle around the main axis of rotation 2.
  • threaded bolts od.
  • the slight rotatability of the inner connecting element 4 relative to the housing-like firing element 5 results from a gap X between the two connecting elements 4, 5.
  • the inner connecting element 4 if necessary, assume the task of an exact alignment of the rotor blade 30 of the wind turbine according to a desired blade pitch can, it must be experienced in turn on the gear-like housing part 5 precise guidance.
  • This assumes a arranged in the gap X between the two gear parts 4, 5 main bearing in the form of a single or preferably multi-row roller bearing with raceways 29 on both connection elements 4, 5, on which rolling elements 6 roll along.
  • roller bearing 6, 29 Since, in addition to the desired drive torque, unwanted but unavoidable axial and radial forces and tilting moments also occur at the blade bearings of a wind turbine, the roller bearing 6, 29 has a robust construction.
  • roller-shaped rolling elements 6 are preferably used. There are several, in particular at least three rows of such roller-shaped rolling elements 6 are provided, for example.
  • a radial row which ensures that the axes of symmetry of the two rotationally symmetrical connection elements are concentric with each other, and at least two rows of axial, from which transmits a compressive forces, while the other for Traction forces is designed; Tilting moments are equally absorbed by both and delivered to the hub 7, whereby a permanent parallel alignment of the two connection elements or a coaxial alignment of their two axes of symmetry is ensured.
  • one of the two connection elements 4, 5 is designed as a so-called "nose ring” with a collar-like elevation 13 running around along its side facing the gap X.
  • this collar-like elevation 13 has an approximately rectangular cross-section, with - viewed in the axial direction - each have a flat top and bottom and a cylindrical outer side while the latter serve as a raceway (s) 29 for the radial bearing (s), starts running the annular top and bottom each one of the two axial rows along.
  • an equal number of raceways 29 must also be provided on the respective other connection element 5, 4. This has for that purpose as a C-shaped geometry, so to speak with an all-round groove in which the collar-like elevation 13 of the other connection element 4, 5 engages.
  • connection ring 5 is subdivided with C-shaped geometry in the region of the groove bottom in an upper ring portion 5 'and a lower ring portion 5.
  • the separation can, for example.
  • Run surface that is, for example, at the upper or lower end of the radial bearing raceway 29.
  • the gap X extends up to the connection surface of the rotatable connection element 4 and is preferably filled with lubricant, in particular with lubricating grease. So that this lubricant can not escape, located in the gap opening a seal 26th
  • the blade bearing assembly 1 is encapsulated as far as possible.
  • the outer sides are in each case aligned with one of the two connecting surfaces of the blade bearing assembly 1 facing away from one another. These are preferably in each case an all-round groove in the relevant connecting element 4, 5 inserted and, for example, fixed by means of screws, for example. By means of countersunk screws.
  • the blade bearing assembly 1 is hermetically sealed.
  • connection surface there is raised in relation to the adjacent end face of the other connection element 5, so that upon a relative rotation of these two surfaces of different connection elements 4, 5, the "uninvolved" end face does not touch the one on the Can run along the connection surface connected plant part.
  • the distance L between the two connection surfaces - and thus the overall height of the blade bearing assembly 1 - is thus slightly larger than the axial extent of the larger or higher connection element 5.
  • connection element 5 preferably on the hub 7 fixed to be anchored connection element 5 consists not only of the two ring sections 5, 5 ', but further comprises an approximately annular disk-shaped connecting part 1 1, on which the actual connection surface GA is arranged, and which is therefore placed on the opposite of the other Anschuss Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stuclear surface.
  • GZ end face of the ring portion 5' Good to see in the drawing, the minimum thickness SG of the connecting part 1 1.
  • the ring sections 5, 5 ', 1 1 can, for example, be determined by common screwed together.
  • the annular disk-shaped connecting part 1 1 engages over the terminal face GZ opposite end face of the other connection element 4 at a distance, so that the gap X continues there, and also dominates the all round current collar or bearing section 13 opposite lateral surface of the other connection element 4 in radial direction.
  • This connection element 4 is provided at just that, the collar or bearing portion 13 facing away from lateral surface with a completely running teeth 12, which serves to initiate the output from the rotary actuators 17 control energy.
  • This toothing 12 need not extend over the entire height of the toothed connection element 4; it may be a straight toothing, but also a helical toothing.
  • This control energy of the rotary actuators 17 is received by one or preferably two or more, toothed gears 8, the respective shell-side teeth 16 is in meshing engagement with the teeth 12 of the toothed connection element 4 and drives or stops them, depending on the control or Control generated target for the angle of attack.
  • the diameter of the gear wheels 8 will be significantly smaller than the diameter of the teeth 12; For this reason, it is also common among the Transmission gears 8 as the smaller gears of pinions to speak; This term is therefore used in this text synonymous with gear (tooth) wheels.
  • FIGS. 6a to 6c The geometry of a gear wheel 8 is shown in FIGS. 6a to 6c. It can be seen clearly the basically cylindrical base body with two flat faces and a respective groove U1, U2 between each of the two end faces and the jacket for receiving a respective wheel bearing 14, 15. Between the two grooves U1, U2 is the straight, originally purely cylindrical shell provided with an all-round toothing 16, depending on the type of toothing 12 on the toothed connection element 4 in the form of a straight or oblique toothing.
  • the respective flat annular surface of the two grooves U1, U2 is provided with a small step, the toothed lateral surface region 16 being opposite the actual surface Groove U1, U2 is set back by the height of the stage and thus a distance between the teeth 16 and the wheel bearings 14, 15 is maintained.
  • the pinion bearings 14, 15 therefore do not contact or touch the toothing elements 16 of the pinion 8. Nor do the wheel bearings 14, 15 come into contact with the tooth-shaped elements 12 on the toothed connection element 4.
  • connection 27 for non-rotatable connection with a Shaft 9 of a rotary drive 17, for example.
  • the connecting element 27 is preferably a bore parallel to the axis of symmetry 3 of the gear wheel 8, the diameter of which is approximately between one fifth and one-half of the diameter DR of the gear wheel 8 including its toothing 16, in particular between one quarter and one third of the diameter DR the toothing 16.
  • connection element 27 causes.
  • this bore jacket does not have a completely rotationally symmetrical, in particular no purely cylindrical shape, but has at least one radial forward and / or return, wherein a counterpart on the inserted shaft 9 or another connection part can engage positively.
  • the jacket of the connection bore 27 is provided with radially projecting teeth and radially receding tooth spaces, so that a shaft provided with a complementary toothing is coupled in a rotationally fixed manner to the transmission wheel 8 after insertion into the connection bore 27.
  • Fig. 1 is further illustrated how such a pinion or gear 8 is installed in the transmission 1.
  • These may preferably be ball bearings, for example radial ball bearings or four-point ball bearings.
  • a single row of rolling elements per wheel bearing 14, 15 may be sufficient, with larger or more heavily loaded blade bearing assemblies 1, it may also be useful to provide several rows of rolling elements per wheel bearing 14, 15.
  • a rotor blade side wheel bearing 14 Shown are a rotor blade side wheel bearing 14, and a hub-side wheel bearing 15th While the respective inner ring of a wheel bearing 14, 15 of the respective groove U1, U2 is applied directly, are for supporting the respective outer ring on the connecting part or portion 1 1 and / or attached thereto or attaching gear part or section 23 in itself annularly closed Provided contact surfaces, wherein the outer ring is inserted or even pressed.
  • the gear member 23 may have an annular shape two cross-sectional portions, for example, a first, about apron or cylinder jacket-shaped portion which is in contact with the connecting part 1 1 and is screwed to that, and a second, approximately annular-shaped portion which is in communication with the free edge of the first portion for example, is integrally molded together with that, for example, is solidified together with that in a mold, or which is welded, glued, screwed or otherwise combined with that.
  • the two sections taken together form an approximately L-shaped cross-sectional geometry, as shown in FIG. 1.
  • the circular disk-shaped portion of the gear part 23 forms together with the connecting part 1 1 each type of bearing plate each one of the two wheel bearings 14, 15.
  • the bearing seats are in these two parts 1 1, 23 for each gear 8 in pairs aligned holes introduced, with hollow cylindrical inner sides, wherein the outer rings are inserted or pressed with their complementary, cylindrical outer sides.
  • a bearing seat in the transmission part 23 may have a different, in particular smaller diameter than the associated bearing seat in the connecting part 1 1.
  • a support in the opposite axial direction is effected by a clamping ring 20, which, for example, in a on the inside of the bore in the connecting part 1 1 above the bearing seat for the local wheel bearing 15 incorporated, the sub-axis of rotation 3 enclosing internal thread can be screwed; instead of a screw the clamping ring 20 may also be welded or - glued. Since its inner diameter is smaller than the outer diameter of the respective wheel bearing 15, this is firmly clamped in the axial direction and thereby the gear 8 held in position such that a rotation of the same about the respective sub-axis of rotation 3 is its only authorized movement.
  • a rotary drive 17 When plugged into a connection hole 27 shaft is the output shaft of a rotary drive 17, for example.
  • a rotary drive 17 In the form of an electric motor or a hydraulic motor.
  • an anchoring possibility in the form of a concentric to the respective sub-axis 3 concentric base member 18 is provided, which in turn is fixed to the connecting part or section 1 1, for example.
  • the base member 18 may have radial projections or recesses and / or screw connections, what the connected rotary drive 17 can be anchored rotationally fixed.
  • the blade bearing embodiment 1 "according to FIG. 2 differs from the one described above in that, according to FIG.
  • a raceway 29 of the main bearing namely that for the upper row of axial rollers 6, does not rest on its own raceway part 5, 5 'of the untoothed connecting element 5
  • the geometry of the connecting part 1 1 can be further simplified by reducing its shape to a virtually pure disk shape.
  • the untoothed connection element 5 in this embodiment only consists of three parts, namely a raceway part 5, a connecting part 1 1 and a transmission part 23.
  • the connecting part 1 1 has been combined or integrated with the gear part 23 to form a new, integral connecting and gear part 24.
  • the gear portion of the integrated Vietnamesesund gear part 24 may be made more massive, ie, for example, more or less completely meet the cavity or throat area between the apron-shaped and the annular disk-shaped portion.
  • the receiving spaces for those would have to be incorporated into this massive ring body, in particular drilled.
  • a separate cavity is created in the latter construction variant for each gearwheel 8, which from the adjacent through the left standing part of the originally massive Transmission section as it is separated from each other by webs.
  • the advantage of this embodiment is on the one hand in an increased rigidity of the arrangement, because the remaining between the compartments webs stiffen the gear portion relative to the connecting portion and thereby improve the dimensional stability;
  • the introduction of holes in the joint connecting and gear body 24 may possibly be accomplished simpler than the preparation of an undercut area between two flat but staggered portions of the respective body 24, which almost excludes the production as a casting with a reusable form almost ,
  • the untoothed connection element 5 consists of three parts, namely two raceway parts 5, 5 'and an integrated connection and transmission part 24. If the embodiments according to FIGS. 2 and 3 were combined with one another, Thus, the connection element 5 could be further simplified and would then only consist of two parts, namely a raceway part 5 and an integrated connection and transmission part 24th
  • FIG. 4 Yet another embodiment of a sheet bearing 1 ⁇ 3) according to the invention is shown in Fig. 4. This differs from the embodiment of FIG. 1, especially with regard to the main storage.
  • the basic principle - a total of multi-row storage with at least one row of rolling bearings for the transmission of axial compressive forces and axial tensile forces and with at least one row of rolling bearings for the transmission of radial forces - similar, but practically implemented in other form.
  • the blade bearing 1 (3) uses spherical rolling elements 6 (3) instead of rollers.
  • two rows of balls 6 (3) are provided for the transmission of axial compressive and tensile forces; However, these rows of balls 6 (3) are not in direct contact with each other, but are each spaced apart.
  • the plane of the ball row pair is for the transmission of radial forces between the planes the ball row pairs for the transmission of axial compressive forces, preferably approximately centrally between the latter two.
  • the spherical rolling elements 6 (3) of the four rows of balls for the transmission of axial forces preferably each have the same diameter, which is larger than the diameter of the rolling elements 6 (3) for the transmission of radial forces according to the usual requirements for a blade bearing.
  • the untoothed connection element 5 ( FIG. 3) has an approximately T-shaped cross-section, the base of which is integrated with or attached to the plate 11 ( FIG. 3) , for example screwed on, in particular by means of screws 32, while the two halves of the T-bar project in radially opposite directions from the head of the vertical T-socket, as seen in Fig. 4.
  • These two, radially projecting halves of the T-bar carry the raceways for the spherical WälzSystem Research Institute 6 (3) , in particular three such raceways, one at the bottom, one at the top and one at the front of the relevant T- crossbar half.
  • each T-bar half can transmit both radial and axial tensile and compressive forces.
  • the two T-crossbar halves - which are preferably mirror images of the longitudinal axis of the vertical T-bar - therefore double the bearing capacity of the bearing against an example. L-shaped cross-sectional arrangement and also create a mutual redundancy.
  • a circumferential recess is provided in the toothed connecting element as a counterpart with also approximately T-shaped, but larger cross section, so that a gap remains between the two elements, wherein the different rolling elements 6 (3) find space.
  • the cross section of the toothed connection element can also be referred to as "U-shaped".
  • the untoothed connecting element 5 (3) is assembled from several, respectively annular sections, namely an approximately flat central part and two thereof projecting in the same direction, approximately cylindrical side parts, which the two legs of the U shaped cross section represent.
  • the raceways for the balls 6 (3) are curved in cross-section, preferably concave, in particular along circular paths.
  • the tracks for the axial traction transfer follow the respective circular path in each case over a center angle of 90 ° or more, relative to the center of the respective ball 6 (3) ; This generally results in a relatively large Schmiege Scheme.
  • the shape of the raceways for the axial pressure force transmission depends on the design of the free end face of the cross-sectionally T-shaped, untoothed connection element. In the embodiment of FIG. 5, this is relatively flat. Since the tracks are only slightly deepened therein, results in a Schmiege Scheme of less than 90 °; In contrast, the associated track of the toothed connection element is in the region of the transition from a flat part of the inner boundary surface of the cross-sectionally T-shaped recess in a cylinder jacket-shaped part thereof, where easily a Schmiege Scheme of 90 ° or more can be realized.
  • a side effect of the different track shapes for the ball row 6 ( FIG. 3) for axial thrust transfer is a comparatively wide, horizontal gap portion between the two rows of balls for axial thrust transfer.
  • the embodiment of a journal bearing assembly 1 l 'according to Fig. 5a differs from the previously described journal bearing assembly 1 (3) only in the area of this horizontal gap section, which is 5a narrower in the Fig.
  • the raceways in the Connection element formed deeper and are each arranged in the region of an edge between a flat surface portion and a cylindrical or hollow cylindrical surface portion of the untoothed connection element.
  • the crimping ranges of all the axial thrust transfer raceways extend across a center angle of at least 90 ° with respect to the center of the respective ball 6 (4) .
  • grease can be made available within the cavity defined by the spacers; on the other hand, one or more sheets, which are curved undulatingly along a cylinder jacket, may also be formed there, which deform during rolling over by the balls 6 (5) and thereby the lubricant , in particular lubricate grease, and thereby set in motion, which is actively transported to the rolling elements 6 (5) out.
  • gearwheels 8 can be distributed at regular intervals over the circumference, or under the same central angles.
  • the gearwheels 8 there are, for example, ten gear wheels 8 equidistantly distributed around the circumference, with adjacent gear wheels 8 being spaced from each other by a center angle PHI of 36 ".
  • a plurality of gears 8 are combined into clusters, wherein a different gear 8 is preferably arranged diametrically opposite to the main rotational axis 2 for each gear 8, so that a total of symmetrical or balanced arrangement results, which has as possible no imbalance.
  • All pinions 8 have the same dimensions in terms of component diameter DR and component height BR. Each of these pinion 8 has approximately the same distance K from the center axis 2, and each of these pinions 8 is driven directly, without intermediary (gear) stages, of the teeth 12 mounted directly on the connection element 4.
  • the imaginary one is shown in FIG Traverse P for connecting all imaginary secondary axes of rotation or Symmetrieschmay 3 between all pinions 8.
  • This symmetrical arrangement was chosen according to the invention to a uniform (concentric) moment load around the Center axis, and is better from this point of view than other, asymmetric or polygonal polygons.
  • the Pinion 8 are arranged concentrically and symmetrically about the main axis of rotation or center axis 2 and these uniformly objected to each other, at the same distance E. If ten pinion 8 are present and they each have the same distances E to each other, so there is an intermediate angle PHI of 36 ° ,
  • a support structure is provided in the form of a base member 18 which (s) for example or in particular by means of a flange 28 on the housing part 1 1 attachable or einbringbar that a Centric shaft 9, with the intention to transmit rotational movements can be introduced through the center of this support structure 18.
  • This centrically arranged shaft 9 then rotates about the respective secondary rotation axis 3, ie about the common axis of rotation 3 of the gear wheel 8 and the rotary drive 17, with the intention of transferring in each case part of the control energy for the angle of attack of the relevant rotor blade to the toothed connection element 13.
  • the Jardinkonstutation 18 can be attached directly to the housing part 11 or introduced or flanged. Its attachment can be designed with conventional connecting elements 31, if necessary, releasable connecting elements 31 such as screw connections 31 can also be used. Optionally, in particular in the case of lubrication by means of oil, optionally suitable additional sealing elements and / or materials for sealing against leakage of the lubricant between the flange 28 of the support structure 18 and the connection or housing part 1 1 can be used. It is also possible that between the indicated shaft 9 and the support structure 18 separate shafts (tight) rings are used.
  • At least one circumferential ring 20 may be present, for example a clamping ring 20 for position stabilization of the pinion bearing 15 or a sealing ring 20 for additional sealing.
  • the center of the circle of such a ring 20 is then equal to the secondary axis of rotation 3 of the surrounded by the respective ring 20 shaft.
  • the housing 1 1 which is essentially closed at least on one side, has a central opening 10 according to the invention about a center axis 2, which ensures center-freedom of the overall arrangement 1.
  • the housing 1 1 can be made in one piece or even several pieces.
  • This plate 21 may be of lesser strength than the housing part 11, in particular of a thickness less than 50 mm.
  • the cover plate 21 is detachably connected to the housing part 1 1, for example, connected by means of screw. According to the invention would also be a permanent connection between the connecting or housing part 11 on the one hand and the plate 21 on the other.
  • Parallel to the perpendicular to the center axis 2 extending end face GA, ie also parallel to the plane in which the exemplary Congressnannte plate 21 is arranged, may be present on a second side, in particular on the opposite side, a second cover plate 22.
  • This second cover plate 22 may also be of lesser strength than the connecting or housing part 1 1, in particular of lesser thickness than 50 mm.
  • this cover plate 22 is not connected to the connection or housing part 1 1, but with the toothed connection element 4, and maintains a relation to the transmission part 23 or the integrated connection and transmission part 24 a distance S.
  • a distance L between the outer housing contour GA at the first bearing end side and the outer housing contour GZ at the second, opposite, bearing end face is defined.
  • this distance L is at most twice the dimension in relation to the overall height BR of a space in the interior between the two housing contours GA; GZ arranged pinion 8.
  • Example according to the axial extent or height L of the transmission assembly 1 is between about 100 mm and at most 1000 mm, preferably less than 500 mm.
  • the gap X between the two main rolling bearing rings 5; 4 is sealed by a conventional sealing system 26 as an annular sealing system.
  • a conventional sealing system 26 as an annular sealing system.
  • Materials for this are, for example, the common materials such as FPM, ECO, NBR, etc., although other, similar rubber-based materials suitable are.
  • This system 26 includes at least one circumferential sealing ring, each having at least one sealing lip. Multi-part designs, including two or more radially juxtaposed sealing rings are also conceivable within the meaning of the invention.
  • each of the existing pinion 8 could be partially enclosed by a respective separate pinion housing 23, in particular but at least radially enclosed by sides of the center axis 2, so that the respective pinion 8 is spatially separated against physical interference from this direction.
  • a respective separate pinion housing 23 in particular but at least radially enclosed by sides of the center axis 2, so that the respective pinion 8 is spatially separated against physical interference from this direction.
  • Fig. 1 is shown as an example that the respective pinion housing or transmission part 23 on the connecting part 1 1 screwed 19 or flanged 25; 19 can be executed; but according to the example it could also be welded (see FIG. 2), which would save screws and a wide flange 25.
  • the toothing of the toothed connection element does not necessarily have to be arranged on the same basic body, which also has at least one raceway. Rather, here the part 13 has no teeth, but keeps a gap to the gear 8 a. Nevertheless, the cover plate 22 extends to the part 13 and is screwed to that.
  • a separate part is arranged, what the actual gearing is located. This part is also fixed by screws to the cover plate 22.
  • This embodiment has the advantage that a toothed section does not have to be designed to run all the way round, but may be limited to, for example, a center angle of approximately 90 ° to 120 °. It can therefore be provided, for example, one or more such toothed segments.
  • connection element 31 screw connection

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Wind Motors (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne d'une part un ensemble palier de pale (1), servant à supporter en rotation une pale de rotor, qui comprend deux ou plus de deux éléments de raccordement (4, 5), de préférence symétriques en rotation et de forme annulaire, qui possèdent chacun au moins une face de montage plane (ΑΝ, ΑΒ) destinée au raccordement solidaire en rotation au moyeu commun de la roue éolienne ou de la centrale éolienne d'une part et à une pale de rotor d'autre part. En particulier, les éléments de raccordement annulaires (4, 5) sont orientés de telle façon que leurs axes de symétrie sont coaxiaux ou alignés l'un par rapport à l'autre et que leurs faces de montage (ΑΝ, ΑΒ) se trouvent à l'opposé l'une de l'autre. En outre, au moins un écartement (X) est ménagé entre au moins deux des éléments de raccordement (4, 5) et au moins un système de palier à roulement (6, 29) est disposé dans cet écartement afin de supporter les éléments de raccordement (4, 5) autour d'un axe de rotation principal (2) ou axe de symétrie commun. L'invention est caractérisée en ce que la surface d'enveloppe intérieure d'au moins un élément de raccordement (4) est dotée d'une denture (12), de préférence périphérique ou du moins réalisée sous la forme d'un segment annulaire et réalisée le cas échéant de manière démontable et interchangeable au moyen d'assemblages vissés (K1, K2). Pour au moins deux ou trois, dans l'idéal pour jusqu'à dix ou douze roues d'engrenage (8) excentriques dont les centres respectifs sont disposés le long d'une trajectoire circulaire imaginaire autour de l'axe de rotation principal (2), l'ensemble palier de pale (1) comporte sur l'une au moins des deux face de montage (AB) une ouverture circulaire respective telle que la roue d'engrenage (8) concernée peut être entraînée en rotation sur un axe de rotation secondaire (3) excentré par rapport à l'axe de rotation principal (2) et s'engrène avec la denture (12) afin de produire un déplacement relatif d'au moins un élément de raccordement (4) par rapport à un élément de raccordement (5) non engrené supporté sur celle-ci.
PCT/DE2013/000447 2013-08-08 2013-08-08 Ensemble palier de pale WO2015018382A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/DE2013/000447 WO2015018382A1 (fr) 2013-08-08 2013-08-08 Ensemble palier de pale
DE112013007311.0T DE112013007311A5 (de) 2013-08-08 2013-08-08 Blattlagerbaugruppe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE2013/000447 WO2015018382A1 (fr) 2013-08-08 2013-08-08 Ensemble palier de pale

Publications (1)

Publication Number Publication Date
WO2015018382A1 true WO2015018382A1 (fr) 2015-02-12

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DE (1) DE112013007311A5 (fr)
WO (1) WO2015018382A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112088249A (zh) * 2018-05-07 2020-12-15 利勃海尔比伯拉赫零部件有限公司 用于调节大型滚动轴承的致动驱动器
CN113188425A (zh) * 2021-04-30 2021-07-30 邵东智能制造技术研究院有限公司 风轮同心度调整检测装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202005007450U1 (de) 2004-05-17 2005-07-14 Hehenberger, Gerald, Dipl.-Ing. Adapter zum Befestigen von Rotorblättern einer Windkraftanlage an einer Rotornabe und Windkraftanlage mit solchen Adaptern
EP1596064A2 (fr) * 2004-05-11 2005-11-16 REpower Systems AG Dispositif de réglage du pas de l'hélice pour turbine éolienne
DE102005026141A1 (de) * 2005-06-06 2006-12-07 Imo Momentenlager Gmbh Lagereinheit für ein langgestrecktes Rotorblatt einer Windkraftanlage sowie Verfahren zum Betrieb einer Windkraftanlage mit wenigstens einem derartig gelagerten Rotorblatt
US20110142631A1 (en) * 2010-08-30 2011-06-16 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
US20110142618A1 (en) * 2010-10-29 2011-06-16 Bradley Graham Moore Wind turbine pitch assembly enclosure system
US20110243729A1 (en) * 2009-11-11 2011-10-06 Amsc Windtec Gmbh Device for adjustment of a rotor blade, wind energy converter, and method for adjusting a rotor blade
DE102011019002A1 (de) * 2011-04-28 2012-10-31 Imo Holding Gmbh Energieübertragungsbaugruppe mit mehreren Abtriebsaggregaten
EP2708739A2 (fr) * 2012-09-17 2014-03-19 IMO Holding GmbH Logement de pale pour le logement rotatif d'une pale de rotor au niveau du moyeu d'une installation éolienne et installation éolienne équipée de celui-ci

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1596064A2 (fr) * 2004-05-11 2005-11-16 REpower Systems AG Dispositif de réglage du pas de l'hélice pour turbine éolienne
DE202005007450U1 (de) 2004-05-17 2005-07-14 Hehenberger, Gerald, Dipl.-Ing. Adapter zum Befestigen von Rotorblättern einer Windkraftanlage an einer Rotornabe und Windkraftanlage mit solchen Adaptern
DE102005026141A1 (de) * 2005-06-06 2006-12-07 Imo Momentenlager Gmbh Lagereinheit für ein langgestrecktes Rotorblatt einer Windkraftanlage sowie Verfahren zum Betrieb einer Windkraftanlage mit wenigstens einem derartig gelagerten Rotorblatt
US20110243729A1 (en) * 2009-11-11 2011-10-06 Amsc Windtec Gmbh Device for adjustment of a rotor blade, wind energy converter, and method for adjusting a rotor blade
US20110142631A1 (en) * 2010-08-30 2011-06-16 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
US20110142618A1 (en) * 2010-10-29 2011-06-16 Bradley Graham Moore Wind turbine pitch assembly enclosure system
DE102011019002A1 (de) * 2011-04-28 2012-10-31 Imo Holding Gmbh Energieübertragungsbaugruppe mit mehreren Abtriebsaggregaten
EP2708739A2 (fr) * 2012-09-17 2014-03-19 IMO Holding GmbH Logement de pale pour le logement rotatif d'une pale de rotor au niveau du moyeu d'une installation éolienne et installation éolienne équipée de celui-ci

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112088249A (zh) * 2018-05-07 2020-12-15 利勃海尔比伯拉赫零部件有限公司 用于调节大型滚动轴承的致动驱动器
CN112088249B (zh) * 2018-05-07 2023-11-03 利勃海尔比伯拉赫零部件有限公司 用于调节大型滚动轴承的致动驱动器
CN113188425A (zh) * 2021-04-30 2021-07-30 邵东智能制造技术研究院有限公司 风轮同心度调整检测装置
CN113188425B (zh) * 2021-04-30 2023-03-24 邵东智能制造技术研究院有限公司 风轮同心度调整检测装置

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