WO2013182175A1

WO2013182175A1 - Wind turbine

Info

Publication number: WO2013182175A1
Application number: PCT/DE2013/000185
Authority: WO
Inventors: Jochen Exner; Hans-Ullrich SCHULZE
Original assignee: Centa-Antriebe Kirschey Gmbh
Priority date: 2012-06-08
Filing date: 2013-04-11
Publication date: 2013-12-12
Also published as: DE102012011268A1

Abstract

The invention relates inter alia to a wind turbine (10) comprising a machine support (11), a rotor (12) having at least one rotor blade (13), and a drive train (14), which comprises drive train elements (15, 16) such as gears and/or a generator. A coupling unit (100, 110a, 110b) is arranged in the force transmission path between a hub (18) of the rotor (12) and at least one drive train element (15, 16). The coupling unit comprises a drive-side connecting device (112) for indirect or direct connection to the hub and an output-side connecting device (212) for indirect or direct connection to the drive train element, wherein the coupling unit allows an axial offset, a radial offset and an angular offset between the drive-side connecting device (112) and the output-side connecting device (212), and is designed as a synchronising coupling and, irrespective of the offset position, transmits torque from the hub (18) to the drive train element (15, 16) in a manner free from reaction force or virtually free from reaction force.

Description

Wind turbine

The invention initially relates to a wind energy plant according to the preamble of claim 1.

Wind turbines of the generic type, which are also referred to as wind turbines or wind turbines are known and widely used. They usually include a rotatable rotor with one or more rotor blades, which is rotatably mounted on a machine carrier. The machine carrier is arranged at the upper end of a mast.

The hub of the rotor is connected to a drive train. Typically, the powertrain includes a transmission and a generator. The rotational movement of the rotor is translated with the aid of the gearbox. In particular, the transmission is used to achieve higher speeds.

Wind turbines of the prior art are also known in gearless design. The invention relates to all variants of wind turbines.

In the prior art, different types of drive trains are known, which are distinguished in fully integrated, semi-integrated or dissolved designs. The classification of different designs is assessed in particular according to whether the transmission, or the generator with the rotor shaft is on a common shaft or not. In wind turbines of the prior art, problems arise with the bearing of the rotor and the mounting of the elements of the drive train. Due to the large occurring forces and the

CONFIRMATION COPY Extremely high drive torques forces and torques in the transmission, or possibly even be introduced into the generator, which can lead to premature wear of the components of the drive train, or shortened lifetimes.

To counteract these problems, the co-playing components of the drive train including the hub and the bearings are sized accordingly large, resulting in a very rigid and heavy equipment.

Therefore, in the prior art it has already been considered to decouple the rotor from the transmission by disengaging connecting means in order to substantially prevent a transmission of axial movements, radial movements or bending movements on the transmission. For this purpose, WO 2011/058185 A2 proposes connecting means which are formed by elastomeric bodies. The use of elastomeric bodies can cause problems in wind turbines of the generic type, since on the one hand no high torques can be transmitted, and on the other hand due to the expected wear of this elastomer body only very short lifetimes are to be expected, or the maintenance costs increase.

Known coupling units, which have elastomeric bodies, can not necessarily achieve optimum coupling properties with regard to axial offset, radial offset and angular offset.

Based on the described prior art, the object of the invention is to further develop a wind turbine of the type described in such a way that the effect of forced reactions or constraining forces is minimized or largely eliminated on the drive train elements. The invention solves this problem initially with the features of claim 1, and is accordingly characterized in particular in that in Kraftleitungsweg between a hub of the rotor and at least one drive train element, a coupling unit is arranged, which has a drive-side connection device for direct or indirect connection with the hub has a driven-side connecting device for direct or indirect connection to the drive train element,

wherein the drive-side connection device, such as flange, has a drive-side rotation axis and is provided with a multiplicity of drive-side attachment means which are all arranged in a common radial plane of the rotation axis and on a common radius about the rotation axis of the drive-side connection device,

wherein the output-side connection device, such as flange, has an output-side rotation axis and is provided with a multiplicity of output-side fastening means, which are all arranged in a common radial plane of the rotation axis and on a common radius about the rotation axis of the output-side connection device,

- wherein connecting elements, such as handlebar or coupling rod, on the one hand on a drive-side fastening means and on the other hand on a driven-side fastening means by means of a three degrees of freedom enabling joint connection, in particular a spherical hinge connection, are arranged

where the radius on which the drive side

Fixing means are arranged around the drive-side rotation axis and the radius, on which the output-side fastening means are arranged around the output-side rotation axis are identical in terms of amount, - And wherein the drive-side fastening means and coupled thereto by means of a connecting element output-side fastening means with respect to the drive-side rotation axis by 80 degrees to 100 degrees, in particular 85 degrees to 95 degrees, in particular by substantially 90 degrees, circumferentially spaced from each other, are arranged.

The principle of the invention is essentially to arrange a special coupling unit in the power line between the rotor hub and at least one drive train element. In the event that the drive train operates gearless, the coupling unit between hub and generator is arranged. In the event that the drive train has a transmission, the coupling unit between the hub and the transmission is arranged in the power line.

The coupling unit is able to compensate even larger angular and axial misalignment as well as radial misalignment. It can also transmit very high torques from the drive to the output. By using a coupling unit in the force path between the hub and drive train element, with the proviso that the clutch unit allows torque transmission in principle a torque transmission, wherein the clutch is designed as a constant velocity clutch and thus regardless of their offset position transmits the torques reaction force, the drive train element can be decoupled from the hub become. Additional loads from the drive and offset or wind loads and vibrations are no longer transmitted from the hub in a disadvantageous manner to the drive train element. In addition, the wind energy plant can be designed with a reduced number of parts. Finally, the maintenance and installation costs can be reduced. Manufacturing tolerances do not play more so, as was the case in the prior art, a role. The system can be designed more compact, that is smaller, which reduces the required mass of the components. Also, the attachment of the hub of the rotor to the machine frame and the design of the bearings can be simplified.

The coupling unit is characterized in that the radius on which the drive-side fixing means are arranged around the drive-side rotation axis and the radius on which the output-side fixing means are arranged around the output-side rotation axis are identical in terms of amount that the drive-side fixing means and with this by means of a Connection element coupled output-side fastening means with respect to the drive-side rotation axis by 80 degrees to 100 degrees, in particular 85 degrees to 95 degrees, in particular by substantially 90 degrees are arranged circumferentially spaced from one another.

A significant advantage of the wind power plant according to the invention is that the coupling unit forms a constant velocity joint, wherein the connecting elements, also called handlebars, can be fixed to the drive and output without the interposition of length-compensating elastomers. This is due to the fact that the fastening elements of the input and output do not change their distance from each other during one revolution of the coupling unit. As a result, high-strength materials such as steels or fabric materials can be used, which due to their compared to elastomers significantly higher load capacity in the overall system of the coupling unit cause that much higher torques compared to the cited prior art can be transmitted.

This makes it possible to provide a coupling unit that allows a homokinetic power transmission, and a constant velocity clutch represents. This means that the clutch allows a power transmission without resulting in force effects from the operation of the clutch. This applies to any offset position of the clutch. As a result, a transmission of the torques from the rotor hub to the drive train element can take place without reaction forces occurring or in such a way that only a minimum of reaction forces occurs.

The principle of the invention can be used in fully integrated designs of a drive train, but equally also in semi-integrated and dissolved designs of a drive train. Through the use of a clearance enabling clutch unit in the drive train, the forces and torques acting on the drive train elements are minimized. At the same time advantageous definitions of the rotor, or the drive train elements independently of each other on the support structure, d. H. on the machine carrier, done. As a result, the drive train elements can be arranged largely free of force and work. It is now possible to introduce a modular design with respect to the individual drive train elements, since the individual drive train elements can now be developed independently of each other.

The coupling unit used offers above-average offset capability, which is only possible through the use of the handlebars. These high offset capabilities can not be achieved with elastomeric elements.

In contrast to the prior art, which required a rigid and therefore heavy plant structure of the drive train, lightweight and kompacktbauende powertrain elements can now be used, which significantly reduces the total use of material and mass. The solution according to the invention makes it possible, in the case of drive trains having a gearbox, to omit the necessity of mounting the gearbox on the rotor shaft of the propeller. It is possible to store the gearbox - separate from the bearing of the rotor - relative to the machine frame or support frame and to connect to the output side of the coupling unit.

The rotor can be rotatably mounted torque-fixed on the machine carrier, wherein this bearing of the rotor is carried out completely independent of the following in the power flow of the rotor hub drive train elements. The coupling unit, which allows a large axial offset and / or radial offset and / or angular offset, thus decouples the forces.

The optional transmission disposed behind the clutch in the direction of power flow may be a mechanical transmission or a hydraulic transmission. The invention encompasses transmissions which permit a high transmission ratio (of approximately 1 to 100) for high-speed generators, as well as embodiments which have average transmission ratios (of, for example, 1 to 20 to 1 to 30) for so-called medium-speed transmissions Allow generators or permanently energized generators.

Finally, the invention also includes wind turbines which are gearless, or whose drive train is referred to as direct drive, in which the slower speed of the propeller is not translated.

The wind turbine according to the invention is particularly advantageous applicable when low speeds of the rotor to z. B. about 30 revolutions per minute are provided, and drive torques, the input side of the clutch unit, occur in the range of several million Newton meters. Finally, in the wind turbine according to the invention in a particularly advantageous training, dimensioning and positioning of the bearing can be made. Also, particularly compact or maintenance-friendly and also lightweight designs of a wind turbine are possible.

The wind power plant according to the invention has a coupling unit, in which the connecting elements, in particular the handlebars, are arranged on the drive-side fastening means or on the output-side fastening means by means of a hinge connection enabling three degrees of freedom. Such, three degrees of freedom enabling articulation can be formed for example by a spherical hinge connection. However, there are also other joints in question, each allow the handlebar, based on the respective attachment point - or, based on the other end of the handlebar - has three degrees of freedom. Particularly preferred is an embodiment with the features of claim 2, wherein three connecting elements are provided on the coupling unit, each connecting a drive-side fastening means and a driven-side fastening means and in a common, extending over an axial portion of the drive-side axis of rotation radial space between the drive-side connection device and the output-side connecting device are arranged and form a Verbindungsmittelterzett. The invention includes embodiments in which the

Coupling unit further Verbindungsmittelsterzette between the drive-side connection device and the output side Connection device, which advantageously each comprise three connecting elements, and are each arranged in a separate radial space between the drive-side connection device and the output-side connection device.

By means of further Verbindungsmittelterzette as power transmitting links between the drive and output can increase the efficiency of the coupling unit. It is of significant advantage when passing through each one

Connecting piece attached fastener fastener groups form, which are arranged on the same radius, but circumferentially offset from each other and / or the fastening means are arranged at different radii.

If you order the fasteners of input and output in circumferential distance of 80 ° to 100 °, in particular of 90 degrees to each other, you get a coupling unit with three connecting means, which can be used as the simplest and kinematic optimal embodiment within the scope of the invention. In order to increase the power density of the coupling unit, further pairs of fastening elements can be provided on the input and output side, as long as these also have a circumferential distance of 80 ° to 100 °, in particular of 90 degrees to each other. It is conceivable to arrange these other pairs of fasteners on a different radius or circumferentially offset from the first pair of fasteners.

It is conceivable that the spherical hinge connection is formed using steel, plastic, elastomers and / or fabric materials. These materials allow a high load capacity as a hinge connection between the fasteners and fasteners. In special applications, however, the absence of elastomeric connections between the connecting elements and the drive and the output has the advantage that the articulated backrest 11 can be formed without force.

Depending on the design of the connecting elements, it is advantageous if the connecting elements are secured against rotation about their longitudinal axis during operation of the coupling unit. Such a rotation about the longitudinal axis of the connecting elements can be caused for example by centrifugal forces.

A wind energy plant, which provides in accordance with the invention coupling units in doppelkardanischer arrangement, from its construction also in a position to be able to compensate for significant axial misalignment between the rotor hub and the drive train element. This ability is u. a. determined by the articulated arrangement of the connecting elements, their plane spacing and the distance of the fastening means to each other.

When using two coupling units, which are joined together by means of a shaft to a double cardanic constructed shaft coupling, it may be useful to complicate the axial clearance to control axial play movements of the shaft located between the coupling units.

Both the axial play movement and the rotation of the connecting elements about their longitudinal axis can be curbed and / or prevented for example by the skillful use of elastomers, without any negative effects on the smoothness, the angular and Axialausgleichsfähigkeit are to be feared. The invention comprises compensating an angular offset of more than 12 degrees, theoretically almost 90 degrees, and transmitting torques of well over 500,000 Nm, in particular of several million Nm. In embodiments of the invention, an angular offset of 1 to 15 degrees or more, be compensated, which was not achievable in the previously common drive rods.

The invention further relates to a wind energy plant according to the preamble of claim 8.

The invention is in turn the object of further developing a wind turbine of the type described in such a way that the influence of forced reactions or forced forces is minimized or largely eliminated on the drive train elements or a simplified construction is possible.

The invention solves this problem with the features of the claim

8th.

An essential feature of the invention is that a special coupling unit is provided which allows an axial offset, a radial offset, and an angular offset. The clutch is also designed as a constant-velocity clutch, and regardless of the offset position virtually torque-free torques transmitted from the hub to the drive train element. While the use of elastomers necessarily results in reaction forces being transmitted when the clutch is in an offset position, according to the invention a wind turbine can be provided in which the driveline provides for decoupling of the rotor hub from the powertrain elements. The coupling unit may have a clearance, so that the transmission of the torques of the Hub takes place on the drive train element reaction force. In this case, for example, a coupling unit can be used, as has been previously described. In particular, it is advantageous if the coupling unit is designed as a link coupling.

The invention relates according to a further embodiment of the invention, a wind turbine according to the preamble of claim 9. The invention is in turn the object of a

Further develop wind turbine of the type described in such a way that the effect of forced reactions or constraining forces on the drive train elements is minimized or largely eliminated or a simplified construction is possible

The invention solves this problem with the features of the claim

9th

According to one essential aspect of the invention, the wind energy installation is equipped with a coupling unit which has at least three links. The links serve the connection between the drive-side connection device and the output-side connection device. The handlebars are without the interposition of length compensating

Elastomers connected at one end to the drive-side connection device and the other end to the output-side connection device. This means that the handlebars are substantially rigid, ie formed unchangeable length. Intermediate elastomeric elements are not required. This allows almost any amount of torque to be transmitted. According to a further aspect, the invention relates to a wind energy plant according to the preamble of claim 10.

The invention is in turn the object of further developing a wind turbine of the type described in such a way that the influence of forced reactions or forced forces is minimized or largely eliminated on the drive train elements or a simplified construction is possible. The invention solves the problem with the features of the claim

10th

An essential aspect of the invention is that the coupling unit provides an axial offset of more than 10 mm, in particular as a function of the length of the handlebars and as a function of the angular offset capability of the articulated connection of the links to the attachment points. Advantageously, the coupling unit allows an axial displacement of more than 20 mm, more advantageously more than 30 mm, more advantageously more than 40 mm, more advantageously more than 50 mm, more advantageously more than 60 mm, more advantageously more than 70 mm, moreover advantageously more than 80 mm, moreover advantageously more than 90 mm, moreover advantageously more than 100 mm, further advantageously more than 150 mm, further advantageously more than 200 mm, further advantageously more than 250 mm further advantageously greater than 300 mm, more advantageously greater than 350 mm, more advantageously greater than 400 mm.

Furthermore, the coupling unit leaves in particular depending on the length of the handlebars and depending on the angular offset capability of the articulated connection of the handlebars to the attachment points and depending on the distance of the two present in this wind turbine and connected in series Coupling units from each other a radial offset of more than 10 mm, in particular more than 20 mm, in particular more than 40 mm, in particular more than 50 mm, in particular more than 60 mm, in particular more than 70 mm, in particular more than 80 mm, in particular more than 90 mm, in particular more than 100 mm.

According to a further aspect, the invention relates to a wind energy plant according to the preamble of claim 11.

The invention achieves this object with the features of claim 11 and is accordingly characterized in that in the power line between a hub of the rotor and at least one drive train element, a coupling unit is arranged, which has a drive-side connection device for direct or indirect connection to the hub and a driven-side connection device for indirect or direct connection with the drive train element, wherein the coupling unit between the drive-side connection device and the output-side connection device permits an angular offset of more than 1 °.

An essential principle of the invention is that the coupling unit allows an angular offset of more than 1 °. Advantageously, the coupling unit allows an angular offset of more than 3 °, further advantageously more than 5 °, more advantageously more than 7 °, more advantageously more than 9 °, further advantageously more than 11 ° advantageously more than 13 °, more preferably more than 15 °, more preferably more than 17 °, more preferably more than 19 °.

Although the above-described different inventions according to independent claims 1, 8, 9, 10 and 11 are initially independent of one another, they can be combined with one another in any desired manner. As far as described with respect to a more detailed inventions or with respect to an embodiment of one of the several described inventions features, these are also with respect to another embodiment of the same or another invention according to one of the independent claims as disclosed and can be combined with this other embodiment, as far such a combination according to the understanding of the expert is nothing contrary.

To avoid repetition, only certain embodiments are described in detail in their specific embodiment and in terms of their advantages, it being clear to the person skilled in the art that the features described in each case can also be advantageously used in the other inventions.

In the following the invention will be explained in more detail with reference to the description of several embodiments. From this description, there are further advantages. Show it:

1 shows a drive-side connecting device of a coupling unit for use in a wind turbine according to the invention with a connecting element in a first embodiment,

2 shows the connecting device according to FIG. 1 with three connecting elements, FIG. 3 shows the connecting device according to FIG. 1 with six connecting elements, FIG. 4 shows an isometric illustration of an arrangement of two

Coupling units according to FIG. 1,

5 shows the arrangement according to FIG. 4 in side view, FIG. 6 shows a drive-side connection device of FIG

Coupling unit for use in a wind turbine with a connecting element in a second embodiment,

7 shows the connecting device according to FIG. 6 with three connecting elements in a perspective view, FIG.

8 shows the connection device according to FIG. 7 in a top view, FIG.

9 is an isometric view of a coupling unit for use in a wind turbine in a second embodiment using a connection device according to FIGS. 6 to 8 in an isometric view, FIG.

10, the coupling unit of FIG. 9 in side view,

11 shows a schematic, partially sectioned view of a prior art wind energy plant with an integrated drive train, FIG. 12 shows a schematic, partially sectioned view of a first

Embodiment of a wind turbine according to the invention, 13 is a second embodiment of a wind turbine according to the invention in a representation according to FIG. 12,

14 is a third embodiment of a wind turbine according to the invention in a representation according to FIG. 12,

15 shows a fourth exemplary embodiment of a wind energy plant according to the invention in a representation according to FIG. 12, FIG. 16 shows a fifth exemplary embodiment of a wind turbine according to the invention

Wind turbine in a representation of FIG. 12, and

17 shows a sixth exemplary embodiment of a wind energy plant according to the invention in a representation according to FIG. 12.

In FIGS. 4 and 5, a shaft coupling is indicated overall by the reference numeral 100.

The shaft coupling 100 comprises two coupling units indicated overall by the reference numeral 110. The coupling units 110 are arranged axially one behind the other in the force flow direction KF and are coupled to one another by a shaft 114. The power flow runs from the drive, not shown, to the output AB, also not shown. A subsequently described as the drive side component is usually arranged on the drive side relative to a further component, a subsequently referred to as the output side component is arranged on the output side generally relative to another component. FIG. 1 shows a drive-side connection device 112, which is also designated as drive-side flange 112 or drive-side flange ring 112. The flange 112 is annular and is provided with externally circumferentially arranged star-like projections 1 15. These extensions 115 may be uniformly distributed over the circumference and carry the drive-side fastening means 1 13. The ring itself is provided with blind hole-like holes 116 are passed through the bolts, not shown for attachment to a drive-side unit.

Shown in Figure 1 further comprises a connecting means, which is provided with the reference numeral 1 17 and hereinafter also referred to as a link 117 or coupling rod 1 17. Such a link 1 17 has an approximately rod-shaped intermediate piece 1 18 at one end of a drive-side receiving eye 1 19 and at the other end a driven-side receiving lug 120 is arranged. In the illustrated drive-side receiving eye 1 19 sits the drive-side fastening means 113 a, the output-side receiving eye 120 is provided for receiving the driven-side fixing means 213.

In Figure 2, the already described above connecting device 1 12 is shown again. The illustration is supplemented by 2 more handlebar 1 17, the drive-side receiving eyelets 119 are arranged on drive-side fastening means 1 13. Again, the output-side receiving eyelets 120 are provided for receiving output-side fastening means 213. As can be seen from FIG. 2, it bears in the present case

Embodiment every second drive-side fastening element 1 13 a drive-side arm 1 17 on the drive-side receiving eye 119. However, this arrangement is specific to the embodiment described.

FIG. 3 also shows the drive-side fastening flange 112 already known from FIGS. 1 and 2. In addition to those shown in FIGS shown three drive-side arms 117 are now three additional, output-side arm 217 shown.

The output side link 217, also called output side connecting means 217 or output side coupling rods 217, also have an intermediate piece, which is designated by the reference numeral 218. Each driven-side intermediate piece 218 has at one end a drive-side receiving eye 219, which receives drive-side fastening means 113. At the other end, the output-side intermediate piece 218 carries output-side receiving eyes 220 in FIG. 3 for unspecified, output-side fastening means.

It is noticeable on the illustration of the output-side link 217 that both the drive-side receiving eye 219 and the driven-side receiving eye 220 pop out of the material plane of the intermediate piece 218 (not shown), both eyelets 219 and 220 being exposed in the same direction from the material plane of the intermediate piece 218. In contrast, the eyelets 119 and 120 of the drive-side link in the material plane of the intermediate piece 117 are arranged. This design makes it possible for the drive-side links 117 to be arranged in a first radial plane of the coupling unit 110 and for the output-side links 217-and in particular the intermediate pieces 218-to lie in a second radial plane of the coupling unit 110. As a result, the drive-side links 117 do not collide with the output-side links 217 during a rotation of the clutch unit 110.

For reasons of illustration, in Figures 1 to 3, the output-side connection device 212, which in turn can be referred to as the output-side flange 212 or output-side flange ring 212, not shown. However, it can be easily imagined on the basis of the structure resulting from FIGS. 1 to 3, such as this output side Connecting device is now in a further, with respect to the illustration of Figure 3 above the handlebar 217 arranged level. This output-side connecting device (not shown in FIG. 3) is designed to be complementary to the drive-side connecting device 112 in the specific exemplary embodiment and, to that extent, likewise has star-like extensions 215 which carry output-side fastening means 213.

In FIG. 4, the shaft coupling designated overall by 100 and forming a coupling unit as a whole is shown in an isometric view. This has two in the power flow direction KF successively arranged and coupled by means of a shaft 114 coupling units 110. The power flow takes place from a drive AN, which is not shown in FIG. 4 but is arranged on the left-hand side, to a drive AB, likewise not shown, but arranged in FIG. 4 on the right-hand side. Such, designated as shaft couplings coupling units 100 are preferably used to compensate for a radial offset between a drive AN and an output AB in a wind turbine according to the invention.

In Figure 4, not all handlebars are shown for the sake of clarity. Also, the respective drive-side connection device 112 is not identical in construction with the output-side connection device 212. However, this does not affect the functionality described above.

In Figure 5, the shaft coupling 100 is shown in side view showing all the individual parts.

The shaft coupling 100 has a longitudinal central axis L, which in this illustration is identical to the axis of rotation of the shaft coupling 100. In addition fall the longitudinal center axes of the coupling units 110 and the axes of rotation of the drive side and driven side connecting devices 112 and 212 together. However, this situation arises only with an ideal alignment of not shown drive AN with the output AB, not shown, corresponding to FIG. 5. The radial planes are spanned by radii which originate from the axis of rotation of the drive-side connection device 12.

From FIG. 5, it is possible in particular to refer to the individual radial planes of the coupling units 110 that are arranged downstream of one another in the direction of flow of force KF. Thus, the respective drive-side connection device 1 12 is located in an upstream level VE. This is followed by the first plane E1, in which the drive-side arm 1 17 are arranged. In the second plane E2, the output-side link 217 are arranged, followed by the subordinate level VN with the output-side connecting device. The planes E1 and E2 are part of a respective radial space, within which three links forming a connecting means 1 17 and 217 are arranged.

The fastening means 1 13 and 213 are preferably spherical and form together with the eyelets 1 19, 120, 219 and 220 a ball joint, so that the respective drive-side connection device 1 12 can be arranged at an angle to the output-side connection device 212. The ball-joint-like connection also allows an axial offset of the drive-side connection device 12 and the output-side connection device 212. With regard to the representation of FIG. 5, the distance between the connection device 12 and 212 can be increased as a result. This compensates for angular misalignment and axial misalignment between drive ON and output AB.

The interconnection of two coupling units 1 10 according to the invention to form a shaft coupling 100, as shown in FIG. 5 is shown, it makes it possible to compensate for a radial offset of two units by the first in power flow direction KF coupling unit 1 10 a certain angle greater than 0 degrees between the connecting devices 1 12 and 212 and the output side coupling unit 1 10 between their connecting devices 112 and 212 a corresponding Has opposite angle. The selected arrangement of the fastening means 113 and 213 in relation to the axis of rotation of the respective connecting device 1 12 and 212 in conjunction with the circumferential distance of 90 degrees between two fastening means 1 13 and 213 of a handlebar 117 or 217 allows the handlebar without rubber mounting to the fastening means 13 and 213.

The circumferential distance of 90 degrees between two fasteners 1 13 and 213 corresponds to a kinematically ideally designed coupling unit 1 10. Depending on the size of the coupling unit 110 and the tolerances of the components, especially the summed bearing clearance, the circumferential distance may differ from the ideal, as long as the occurring distance change between the fastening means 1 13 and 213 is absorbed by the tolerances or material elasticities.

Due to this arrangement, an angular offset between the drive AN and output AB can be compensated for without the distance between the fastening means 1 13 and 213 of a link 1 17 or 217 being subjected to a change. As a result, no flexible element is necessary, which compensates for this change in distance. In this respect, the angle compensation possibility of an inventive

Coupling element only dependent on that handlebars 1 17 and 217 and fasteners 113 and 213 ensure sufficient angular freedom, which is determined in particular by the distances of the planes VE, E1, E2 and VN. In theory, this means that angles of nearly 90 could be bridged. Under real conditions, angles of 10 degrees to 45 degrees can easily be compensated, which, in contrast to the previous angle compensation capability of known link couplings of the prior art of a maximum of two degrees, represents a considerable improvement. A larger angle compensation capability of the coupling unit 110 according to the invention is also conceivable.

The waiver of elastic elements for connecting the connecting devices 1 13 and 213 to the handlebars 1 17 and 217 also makes it possible to transmit much higher torques with full angle compensation capability of the drive AN to the output AB. Thus, the aforementioned ball joints can be formed for example of steel balls and also steel eyelets 1 19, 219, 120 and 220. Alternatively, high-performance fabric composite materials as well as joint bearing units made of high-performance plastics for forming the spherical joints are conceivable. Twisting the handlebars 117 and 217 about its longitudinal axis or a

Axial play of the shaft 114 of a shaft coupling 100 in operation can be structurally minimized or excluded by suitable, not the actual angular and Axialausgleichsfunktion not affecting damping elements. In order to prevent tilting of the links 117, 217 about their longitudinal axis, suitable elastomers may be provided in the region of the joint connections. These can also serve to avoid uncontrolled axial movements of the shaft 1 14. Alternatively or additionally, elastomeric buffers on the connection devices 112, 212 can prevent uncontrolled axial movements of the shaft 114. The coupling unit 1 10 shown can compensate in excellent manner angular misalignment and axial misalignment. In particular, it can counteract the problems typically encountered in wind power plants and keep away the bending and transverse forces which occur on the rotor side from the drive train elements, in particular from the transmission, and from the generator.

The coupling unit is also able to enable to be transmitted in a wind turbine large torques of several million Newton meters without the use of wear-prone elastomer parts. In addition, it can compensate for very large axial misalignments, very large radial misalignments and very large angular misalignments. Through the use of additional handlebar 1 17 and 217 and more

Fastener 113 and 213 taking into account the features of the invention can be the

Further increase torque transfer capacity without having to compromise on the angular compensation capability of the clutch 100.

Figures 1 - 5 show coupling units 110, which are formed by the structure of the connecting devices 1 12 and 212 for the arrangement of three links 1 17 and three other links 217 in the form of two connecting means in their respective own radial space. For this purpose, the star-beam-like extensions 115 of the first and second Verbindungsmittelterzetts or the drive-side link 1 17 and the output side link 217 with the respective attachment means 1 13 on the same radius of the respective connection device 1 12 and 212, however, circumferentially offset from one another. The basic form of the coupling unit according to the invention will now be illustrated in the following description of FIGS. 6 to 10. In order to ensure a distinctness of the two embodiments, different reference numerals are used for similar components, although an identical or analogous function is given.

The coupling unit of Figures 6 to 10 is shown in their entirety in Figures 9 and 10 and indicated generally by the reference numeral 310.

6, the drive-side connection device 312 in the form of an annular flange 312, including a connecting means 317 (also called handlebar or coupling rod), is initially shown. The drive-side connecting device 312 has three star-like extensions 315 that are distributed uniformly over the circumference and serve to arrange drive-side fastening means 313. These drive-side fixing means 313 are, just as in the previously described embodiment, formed as a joint ball sitting on a shaft, which are enclosed by a sleeve-like ring 330. This bush-like ring 330 of each drive-side fixing means 313 is respectively pressed into a drive-side receiving lug 319 of each link 317. In the same way, the displacement-side fastening means 413 shown in FIG. 6 is moved, which is seated in the driven-side receiving eye 320 of the handlebar 317. The drive-side receiving lug 319 and the driven-side receiving lug 320 are connected by the intermediate piece 318 of the handlebar 317. FIG. 7 shows a representation corresponding to FIG. 6 and thus a perspective view of the drive-side connection device 312, FIG. but here at their three attachment means 313 each carries a handlebar 317 via the drive-side receiving eye 319.

Also in this basic form of the coupling unit 310, the drive-side fixing means 313 and the output-side fixing means 413 are spaced from each other with respect to the rotational axis, not shown, of the drive-side connection device 312 by approximately 90 degrees. There may be deviations from this ideal angle due to material tolerances, fit clearance and material elasticities, without the function of the coupling unit 310 being significantly influenced. As in the previous embodiment, the invention assumes that the actual circumferential distance of the drive-side fixing means 313 and the driven-side fixing means 413 may vary between 80 degrees and 100 degrees.

In FIG. 8, the output-side connecting device 312 according to FIG. 7 is shown once again in a view viewed in the axial direction. This can be the circumferential angle of 90 degrees between the drive-side fastener 313 and output-side fastener 413 of each arm 317 very good. The three handlebars 317 shown form a connecting means index in the sense of a connecting means base assembly. The coupling unit 310 is, as already stated above, shown in a perspective overall view in Fig. 9. Compared to FIG. 7, the output-side connection device 412 with its output-side fastening means 413 has additionally been shown, which engage in the output-side attachment eyelets 320 of the links 317. In Fig. 10, the coupling unit 310 is shown in a side view. The power flow KF runs, as already shown for the previous embodiment, from the drive AN to the output AB. Notable in comparison with FIG. 5 is that the links 317 are not aligned parallel to the connection devices 312 or 412, but enclose an angle with the connection devices 312 or 412. This is a consequence of the compensation of an axial offset between the drive AN and the output AB. As a result, the links 317 occupy a radial space RM which extends over an axial portion of the rotation axis, not shown here, of the drive-side and output-side connection devices 312, 412. An angular offset between drive AN and output AB would compensate the coupling unit 310 if the connection devices 312 and 412 were not arranged parallel to one another but at an angle to one another.

It can easily be seen from the comparison of the two embodiments that the second embodiment illustrated in FIGS. 6 to 10 represents the basic form of the coupling unit. It comprises a single, the drive-side connection device 312 and the output-side connection device 412 non-positively interconnecting Verbindungsmittelterzett.

As illustrated in the exemplary embodiment of a coupling unit in FIGS. 1 to 5, further connection means can be arranged between each drive-side connection device 312 and an output-side connection device 412. These then occupy a second radial space RM and increase the capability, ie the ability to transmit torque of the coupling unit 310. The fastening means associated with each further connecting means grid can be either radiused but circumferentially offset from the fastening means of the other Verbindungsterterzetts be arranged on the connection devices. Alternatively, it is conceivable that they are arranged on a different radius, which leads to different lengths of handlebar between the Verbindungsmittelterzetten.

It is also encompassed by the invention to provide only one or two further links instead of another connecting means tag. Before now a first embodiment of an inventive

Wind turbine 10 is described, a wind turbine 10 'of the prior art will be described with reference to FIG. 1:

A prior art wind turbine 10 'typically includes a rotor 12' rotatably mounted on a machine support 11 'about a rotation axis L'. The rotor 12 'has a plurality of rotor blades 13a', 13b ', the rotor 12', assuming a corresponding wind strength set in rotation about the axis of rotation 1 1 '.

The hub 18 'of the rotor 12' is the drive end of a drive train 14 'which serves to deliver rotational movement of the hub 18' to a transmission 15 'which translates the slow rotational movement of the hub 18' into rapid rotational movement of a shaft 26 ' and finally a generator 16 'feeds. Fig. 1 1 does not show, because this is understandable to those skilled in that of the generator 16 'from power supply lines through the mast 27' through, ie with respect to FIG. 1 1 down, towards the foot of the mast of the wind turbine extending out are to supply the generated electrical power to a power distribution network. 11, which is taken from WO 201 1/058185, uses for damping the forces acting on the rotor 12 ', or for damping the forces and moments resulting from this movement, elastomer elements which keep the planetary gear 15' free of such constraining forces should. However, this is only partially possible with the construction of the prior art proposed in FIG. 11.

The solution according to the invention will now be explained with reference to several embodiments of wind power plants 10 according to the invention according to the different embodiments of FIGS. 12 to 17. The following description of the figures of the exemplary embodiments is to be understood that as far as different embodiments are concerned, identical or mutually comparable parts or elements for simplicity with the same reference numerals, partially with the addition of small letters are designated.

FIG. 12 shows an exemplary embodiment of a wind power plant 10 according to the invention in a very schematic representation. The rotor of the wind turbine 10 is denoted by 12 and its rotor blade 13, but shown only broken off. The other rotor blades are not shown for the sake of simplicity. The designated 18 hub of the rotor is shown in Fig. 12 only half. The lower part of the hub 18 relative to the axis of rotation L is not shown in FIG.

Rotationally fixed to the hub 18 of the rotor 12, a preferably solid or optionally hollow shaft 28 is connected, which is also rotatable about the axis of rotation L. The shaft 28, and moreover the entire rotor 12, is rotatably but axially fixedly connected to the machine carrier 1 1, which is also referred to as a supporting frame or supporting structure, via a torque-proof mounting 19 a, 19 b. The output-side end 29 of the shaft 28 is rotatably connected to a flange 30. The flange 30 represents the drive-side connection device 112a of the coupling units 110 and 100 described in FIGS. 1 to 10.

The coupling units 100 used in the drive train 14 of the exemplary embodiments of wind turbines 10 according to FIGS. 12 to 17 correspond to a device designated in the exemplary embodiments of coupling units according to FIGS. 1 to 10 as a shaft coupling 100. Each coupling unit 100 according to the exemplary embodiments of FIGS. 12 to 17 in this respect has two coupling units 110 according to the previous description of FIGS. 1 to 10 in series connection with the interposition of an intermediate piece 114.

For the sake of simplicity, the drive-side clutch unit in FIG. 12 is designated 110a, and the output-side clutch unit in FIG. 12 is designated 110b. The two coupling units 110a, 110b, together with the intermediate piece 114 form a common coupling unit 100.

The output side connecting device 212b of the output side coupling unit 110b is also formed as a flange and directly connected to a transmission 15. The gear 15 is connected via a gear attachment 21 to the machine frame 11. The bearing of the gear 15 on the machine carrier 11 thus takes place completely independently of the mounting of the rotor 12 via the rotor bearings 19a, 19b on the machine carrier 11.

The transmission 15 is connected via a fast-rotating clutch 31 to a generator 16. The generator 16 has its own Generator attachment 22 also connected to the machine frame 1 1.

The coupling unit 100 of the two coupling units 1 10a and 110b is itself not stored, but only with its drive-side end 112a via the shaft 28 to the hub 18 and with its output side end 212b connected to the transmission 15.

Transverse forces, shear forces, bending moments and the like, which act on the hub 18 via the rotor blades 13, can still act on the drive-side connection device 12a via the shaft 28. As a result of the aforementioned reaction force freedom of the coupling unit 100, however, these forces and moments do not arrive on the input side of the transmission 15, ie in the region of the output-side connection device 212b of the coupling unit 100. The transmission 15 is thus completely or almost completely decoupled from the hub 18 with respect to disturbing constraining forces.

While FIG. 12 shows an exemplary embodiment with a classically broken-down drive train, as shown in FIG. 13, a modified arrangement can also be used. Here, the rotor hub 18 is secured by a fixed bearing 19a, 19b with the aid of a fixed central journal 24, which can also be marked as a hollow shaft, mounted on the machine carrier 11. The coupling unit 100 extends with its drive-side coupling unit 1 10a to the nose 32 of the hub 18. The drive-side connection device 112a is so far easily accessible from the hub 18 for maintenance purposes. The drive-side coupling unit 1 10a is connected to the output side

Coupling unit 110b connected via an axially longer stretched shaft 28, at least partially through the hub 18, along the Rotation axis L, extending therethrough. The transmission 15 and the generator 16 may be arranged radially outside of the coupling unit 100 in this embodiment and be connected via a bearing 21, 22 with the machine frame 11. Such an embodiment is particularly advantageous for medium-speed and / or directly driven generators.

In the embodiment of FIG. 14, an arrangement similar to the embodiment of FIG. 13 is made. Here, the rotor 12 is supported in the same manner on a central pin 24, and thus relative to the machine frame 11, as in the embodiment of FIG. 13.

A difference, however, is that the gear 15, or the generator 16 is not secured with the aid of a bearing 21, 22 on the machine frame 11, but with the aid of a flange 33. In addition, in the embodiment of FIG. 14, the transmission 15th and / or the generator 16 is arranged radially outside the shaft 28 connecting the two coupling units 110a and 110b, but axially between the two coupling units 110a and 110b.

In the embodiment of FIG. 15, the hub 18 has a shoulder 34, on the outside of which the torque-resistant mounting 19 a, 19 b is arranged relative to the machine carrier 11. The drive-side coupling unit 110a is attached to the hub nose 32 remote from the end of this shoulder. The transmission 15 and / or the generator 16 are in turn connected in this embodiment via a bearing 21, 22 to the machine frame 11 and arranged radially outside of the coupling unit 100. This embodiment can be advantageously used when the generator is driven medium-fast or gearless. In the embodiment of FIG. 16, the rotor hub 18 has an internal cavity 35, within which the coupling unit 100 can be completely or almost completely accommodated. The machine support side bearing of the rotor 13 via a torque-resistant pivot bearing 19. The coupling unit 100 may be kept so short in the axial direction (relative to the axis of rotation L) that it is disposed between the boss nose 32 and the torque-resistant bearing 19. In this embodiment, the drive-side is in this respect

Coupling unit 1 10a near the nose 32 of the hub 18 and the output side coupling unit 1 10b near the nose 32 distal end portion of the hub 18. The geometric design is chosen here so that the hub 18, the drive-side coupling unit 1 10a and the output side coupling unit 1 10b covered. For the sake of understanding, it should be noted that this observation takes place in the axial direction, that is to say along the axis of rotation L.

The gear 15, or a generator 16 may optionally be arranged via a bearing 21, 22 relative to the machine frame 1 1, or via a fixed, d. H. immovable attachment 36. FIG. 16 shows both alternatives in a common representation, it being clear to the person skilled in the art that either a bearing of the gearbox or of the generator takes place relative to the machine carrier 11, or alternatively an immovable, d. H. fixed arrangement by a fastening 36.

Finally, the exemplary embodiment of FIG. 17 shows an exemplary embodiment of a wind power plant in which the output-side coupling unit 1 10b is provided with an output-side connection device 212b, which extends very far in the radial direction, relative to the axis of rotation L, and has a significantly larger construction than the drive-side connection device 1 12b of output side coupling unit 110b. Here, the transmission 15 or a generator 16 can interact with the output-side connection device 212b and be positioned relative to the coupling unit 100 such that a supporting frame or machine carrier side mounting 21, 22 is arranged radially within the transmission 15, or the generator 16. As a result, axially very short drive lines 14 can be achieved.

While in the embodiment of FIG. 12 transmission 15 and generator 16 have been shown and designated separately from each other, in the exemplary embodiments of FIGS. 13 to 16 the components shown only schematically, a generator or a transmission and a generator are denoted by 15, 16 , This illustration is intended to illustrate that all exemplary embodiments of FIGS. 13 to 17 represent a drive train 14, which may have a transmission 15, but does not necessarily have to have a transmission.

Similarly, in Figures 13 and 15 to 17, the bearings of this component with 21, 22 denotes, which is to illustrate the skilled person that, as far as a directly driven generator, d. H. a gearless drive train is provided, the generator is connected via a bearing 22 to the machine frame 11, and in the event that a gear 16 is provided, depending on the embodiment, either the gear 15 via a separate gearbox mounting 21 and the generator 16 via a separate generator storage 22 or the gear 15 and the generator 16 may be connected via a common storage on the machine frame 11.

With regard to the embodiments 12 to 17 it is clear that in the respective embodiments of wind turbines 10 each coupling units 100 are used, which are denominated as a shaft coupling, and each having two coupling units, and Although a drive-side coupling unit 110a and a driven-side coupling unit 110b. Each of the two coupling units 110a, 110b has in each case for itself a drive-side connection device 112 and an output-side connection device 212. For the sake of simplicity, the drive-side connection device of the drive-side clutch unit 110a is designated 112a and the output-side connection device of the drive-side clutch unit 110a is designated 212a, and a corresponding designation is made in the output-side clutch unit 110b in the same way.

The drive-side connection device 112a of the drive-side clutch unit 110a is connected directly or indirectly to the hub 18. The output-side connection device 212a of the drive-side coupling unit 110a is connected to the drive-side connection device 112b of the output-side coupling unit 110b with the aid of an intermediate piece 114 or a correspondingly suitable shaft 28, and the output-side connection device 212b of the output-side coupling unit 110b is connected to the corresponding element of the drive train 14, ie in particular with the transmission 15, or if the drive train is gearless formed, connected directly or indirectly to the generator 16.

The inventions expressed in the independent claims comprise both embodiments, which each have two coupling units 110, as well as embodiments which have only one coupling unit 110.

The exemplary embodiments of FIGS. 13 to 17 make it clear that different embodiments and positions of the coupling unit 100 relative to the hub 18 and also relative to the frame 11 are encompassed by the invention. Also are different Formations of the support frame 1 1, as shown in the figures, of the invention with.

The embodiments of Figures 13 to 17 have in common that the hub of the rotor is designed as a hollow shaft, and within this hollow shaft, the coupling unit 100 is partially or completely arranged. This allows particularly short, that is kept short in the axial direction and thus compact designs, low mass and achieving a high weight savings compared to the prior art.

Claims

A wind turbine (10) comprising a machine carrier (11), a rotor (12) with at least one rotor blade (13), and a drive train (14), the drive train elements, such as transmission (15) and / or generator (16), characterized in that in the Kraftleitungsweg between a hub (18) of the rotor and at least one drive train element (15, 16) a coupling unit (100, 110a, 110b) is arranged, the drive-side connection device (112, 112a, 112b) for indirect or direct connection to the hub and a driven-side connecting device (212, 212a, 212b) for direct or indirect connection to the drive-train element (15, 16),

wherein the drive-side connection device (112, 112a, 112b), such as flange, has a drive-side rotation axis and is provided with a plurality of drive-side attachment means (113), all in a common radial plane (E1) of the rotation axis and on a common radius the rotational axis of the drive-side connecting device (112, 12a, 112b) are arranged, - wherein the output-side connecting device (212, 212a, 212b), such as flange, has an output-side rotation axis and is provided with a plurality of output-side fixing means (213), all in a common radial plane (E2) of the axis of rotation and on a common radius about the axis of rotation of the output-side connecting device (212, 212a, 212b) are arranged,

- wherein connecting elements (117, 217), such as handlebar or coupling rod, on the one hand on a drive-side fastening means (113) and on the other hand on a driven-side fixing means (213) by means of a three degrees of freedom enabling articulation, in particular a spherical hinge connection, are arranged wherein the radius on which the drive-side fixing means (1 13) are arranged around the drive-side rotation axis and the radius on which the output-side fixing means (213) are arranged around the output-side rotation axis are identical in magnitude,

- And wherein the drive-side fastening means (1 13) and with this by means of a connecting element (1 17, 217) coupled output-side fastening means (213) with respect to the drive-side rotation axis by 80 degrees to 100 degrees, in particular 85 degrees to 95 degrees, in particular in the Substantially 90 degrees, circumferentially spaced from each other, are arranged.

2. Wind turbine (10) according to claim 1, characterized in that in the power line between the coupling unit (110a) and the drive train element (15, 16) a second, to the first coupling unit (1 10a) similar or substantially identical coupling unit (1 10b ), to the first coupling unit (1 10a) connected in series, is arranged.

3. Wind energy plant (10) according to claim 2, characterized in that a two coupling units (110a, 1 10b) having coupling unit (100) has a axial offset of drive (AN) and output (AB) compensating clearance, but against axial play movement in Coupling operation is secured.

4. Wind energy plant (10) according to one of claims 1 to 3, characterized in that three connecting elements (117, 217) are provided which each connect a drive-side fastening means (1 13) and a driven-side fastening means (213) together and in a common , Radial space between the drive-side connecting device (1 12, 1 12a, 1 12b) extending over an axial portion of the drive-side axis of rotation and the output side connecting device (212, 212a, 212b) are arranged, and form a Verbindungsmittelterzett.

5. Wind energy plant (10) according to one of claims 1 to 4, characterized in that the coupling unit more

Connecting means between the drive-side terminal device (112, 112a, 112b) and the output-side connecting device (212, 212a, 212b), each comprising three connecting elements (117, 217), and in each case in a separate radial space between the drive-side connecting device (112, 112a , 112b) and the output-side connecting device (212, 212a, 212b) are arranged.

6. Wind energy plant (10) according to one of claims 1 to 5, characterized in that the coupling between the

Fastening means (113, 213) and the connecting elements (117, 217) is formed by means of a ball joint connection or a differently designed, three degrees of freedom enabling articulation and in particular takes place using steel, plastic, elastomers and / or fabric materials.

7. Wind energy plant (10) according to one of claims 1 to 6, characterized in that the connecting elements (117, 217) are secured against rotation during operation of the coupling unit, in particular about its longitudinal axis.

8. Wind turbine (10), in particular according to one of the preceding claims, comprising a machine carrier (11), a rotor (12) with at least one rotor blade (13), and a drive train (14), the drive train elements (15, 16), such as Transmission and / or generator, characterized in that in the power line between a hub (18) of the rotor (12) and at least one Drive train element (15, 16) a coupling unit (100, 1 10a, 1 10b) is arranged, which has a drive-side connecting device (1 12, 112 a, 1 12 b) for direct or indirect connection to the hub and a driven-side connecting device (212, 212 a, 212b) for indirect or direct connection to the drive train element, wherein the coupling unit between the drive-side connection device (1 12, 1 12a, 1 12b) and the output-side connection device (212, 212a, 212b) allows axial offset, radial offset, and angular offset , Is designed as a constant velocity clutch, and independent of the offset position reaction force free or almost free of reaction torque from the hub (18) on the drive train element (15, 16) transmits.

9. Wind energy plant (10), in particular according to one of the preceding claims, comprising a machine carrier (1 1), a rotor (12) with at least one rotor blade (13), and a drive train (14), the drive train elements (15, 16), as transmission and / or generator, characterized in that in the power line between a hub (18) of the rotor and at least one drive train element (15, 16) a coupling unit (100, 1 10a, 110b) is arranged, which has a drive-side connection device ( 1 12, 112 a, 112 b) for direct or indirect connection to the hub (18) and a driven-side connecting device (212, 212 a, 212 b) for direct or indirect connection to the drive train element (15, 16), wherein the coupling unit for connection between the drive-side connecting device and the output-side connecting device has at least three links (1 17), the balance without the interposition of length the elastomers are fixed with their one end to the drive-side connection device and with its other end to the output-side connection device.

10. Wind turbine (10), in particular according to one of the preceding claims, comprising a machine carrier (1 1), a rotor (12) with at least one rotor blade (13), and a drive train (14), the drive train elements (15, 16), As transmission and / or generator, characterized in that in the power line between a hub (18) of the rotor and at least one drive train element, a coupling unit (100, 1 10a, 1 10b) is arranged, which has a drive-side connection device (1 12, 1 12a, 1 12b) for direct or indirect connection to the hub (18) and an output-side connection device (212, 212a, 212b) for direct or indirect connection to the drive train element, wherein the coupling unit between the drive-side connection device and the output-side connection device axial displacement of more than 10 mm and a radial offset of more than 10 mm.

1 1. Wind turbine (10), in particular according to one of the preceding claims, comprising a machine carrier (1 1), a rotor (12) with at least one rotor blade (13), and a drive train (14), the drive train elements (15, 16), such as transmission and / or generator, characterized in that in the Kraftleitungsweg between a hub (18) of the rotor and at least one drive train element, a coupling unit (100, 1 10a, 1 10b) is arranged, which has a drive-side connection device (1 12, 1 12a, 1 12b) for direct or indirect connection to the hub (18) and an output-side connecting device (212, 212a, 212b) for direct or indirect connection to the drive train element (15, 16), wherein the coupling unit between the drive-side connection device (12 12 , 1 12a, 1 12b) and the output-side connecting device (212, 212a, 212b) permits an angular offset of more than 1 °.

12. Wind turbine (10) according to one of the preceding claims, characterized in that the hub (18) of the rotor (12) is designed as a hollow shaft, and the coupling unit (100, 110, 110a, 110b) is at least partially disposed in the hollow shaft ,