Gear and planetary gear reducer with gear

Abstract

The invention relates to a reduction gear, in particular a planetary reduction gear, having a sun gear, and to a wind turbine having a rotatably arranged nacelle, the toothing of the sun gear having an interruption, i.e. A first toothing region of the toothing is spaced apart from a second toothing region of the toothing in the axial direction, wherein a predetermined breaking point is arranged in the axial direction between the first tooth region and the second tooth region.

Description

Technical Field

[0001] The present invention relates to a speed reducer, in particular a planetary gear speed reducer / planetary gear transmission mechanism, which has a sun gear; the present invention also relates to a wind power generation device with a rotatably arranged nacelle. Background Art

[0002] As is known, a planetary gear reducer has a sun gear which meshes with planet gears which mesh with a ring gear.

[0003] As the closest prior art, a locking device is known from German patent document DE 10 2017 107 892 A1.

[0004] A wind turbine is known from Austrian patent specification AT 512 436 A1. Summary of the invention

[0005] The object of the present invention is therefore to efficiently operate a device driven by a planetary gear reducer, in particular a wind power plant.

[0006] According to the invention, the above object is achieved by a reduction gear according to the features of claim 1 and a wind power plant according to the features of claim 15 .

[0007] In a reduction gear having a sun gear, in particular a rotatably arranged sun gear, in particular a planetary gear reduction gear, an important feature of the present invention is that the toothing of the sun gear has an interruption, that is, a first toothing area of ​​the toothing is spaced apart from a second toothing area of ​​the toothing in the axial direction.

[0008] wherein a predetermined breaking point is arranged between the first tooth region and the second tooth region in the axial direction,

[0009] In particular, the axial direction is parallel to the axis of rotation of the sun gear.

[0010] The advantage here is that the device equipped with this reducer can operate efficiently. Since in the event of an overload, the first sun gear will be damaged, the components of the device driven by the reducer are protected from the overload. For example, this component can be a large and therefore very expensive ring gear. For maintenance, only the first sun gear of the reducer, that is, the smallest sun gear of the reducer, needs to be replaced. The subsequent reducer stages and ring gears can continue to be used. Especially for wind power plants, the installation of the ring gear is complicated, which not only leads to high manufacturing costs, but also high installation costs. Therefore, the replacement or maintenance costs of the first sun gear of the multi-stage reducer are low, thereby ensuring efficient operation of the entire device during its service life (including maintenance).

[0011] In an advantageous embodiment, the predetermined breaking point is designed as a constriction.

[0012] The minimum outer diameter of the predetermined breaking point is smaller than the root diameter of the toothed portion. The advantage here is that the predetermined breaking point can be produced as a constriction in a simple manner.

[0013] In an advantageous embodiment, the predetermined breaking point is formed as a rotational body segment, the rotational symmetry axis of which is coaxial with the rotational axis of the sun gear.

[0014] The curve that generates the rotational body is a semicircle or a semi-ellipse. The advantage here is that when the curve is generated by a semicircle, the production is very simple, while when the curve is generated by a semi-ellipse, the predetermined breaking point can be realized in a more clearly defined manner than with a design using a semicircle. In any case, the predetermined breaking point is designed to be concave. The axial position of the predetermined breaking point with the smallest outer diameter is preferably arranged axially centrally, so that starting from this point, the outer diameter increases in both axial directions. When a semi-ellipse is used, almost no or only very little fragmentation occurs in the event of overload.

[0015] In an advantageous embodiment, the rotating body is concave and / or the outer diameter of the rotating body section increases strictly monotonically with increasing axial distance from the narrowest part of the rotating body, i.e. the axial position at which the rotating body has the smallest outer diameter. An advantage here is that the predetermined breaking point breaks essentially axially centrally.

[0016] In an advantageous embodiment, the toothing is designed as a spur toothing, which has the advantage that it can be produced simply and cost-effectively.

[0017] In an advantageous embodiment, the shaft is connected to the sun gear in a rotationally fixed manner by meshing the toothing with the internal toothing of the shaft. This has the advantage that the sun gear also functions as a tooth coupling component. Although the shaft is connected to the first sun gear in a rotationally fixed manner, compensation can still be achieved if the axes of rotation of the shaft and the first sun gear are not aligned.

[0018] In an advantageous embodiment, the shaft has a blind hole with an internal toothing, into which the toothing of the sun gear partially engages. This has the advantage that an easy-to-implement connection is provided.

[0019] In an advantageous embodiment, the sun gear has a flange, in particular a cylindrical section, on its side facing away from the shaft in the axial direction, the outer diameter of the flange being smaller than the tooth root diameter of the toothing and larger than the minimum outer diameter of the predetermined breaking point.

[0020] In particular, the collar is axially spaced apart from the predetermined breaking point. This has the advantage that the toothing is spaced apart from the sliding disk, so that the toothing is protected. Furthermore, the end face of the first sun gear can be designed as a flat surface, so that the radially directed recesses machined into the sliding disk form channels through which the oil flowing axially through the sliding disk can flow.

[0021] In an advantageous embodiment, the first sun gear is a one-piece component.

[0022] In particular, the first sun gear is not a hollow component. The advantage here is that the oil cannot flow through the first sun gear in the axial direction and is forced to flow out in the radial direction. Therefore, the oil first flows through the hollow second sun gear and then flows through the sliding plate, where the oil is turned in the radial direction and flows out. This not only achieves better lubrication, but also dissipates the lost heat, thereby reducing the peak temperature in the reducer and improving the heat dissipation to the surrounding environment.

[0023] In an advantageous embodiment, in the region covered by the predetermined breaking point in the axial direction and / or in the region located between the first toothing region and the second toothing region in the axial direction, radially inside the smallest outer diameter of the predetermined breaking point, the material of the first sun gear is designed to be gap-free and / or interruption-free and / or is designed to be uniform. This has the advantage that a clearly defined region for overload is provided and that the number of fragments is very low or even zero due to a corresponding semi-elliptical design.

[0024] For this purpose, the semi-ellipse has a major semi-axis, in particular a main axis, whose length is at least twice as long as a minor semi-axis, in particular a minor axis.

[0025] In an advantageous embodiment, the first sun gear meshes with the planetary gears, which mesh with the ring gear having an internal toothing.

[0026] The planetary gear is rotatably mounted on the planetary carrier.

[0027] The planet carrier has a hole with an inner toothing, into which the toothing of the second sun gear is partially inserted. The advantage here is that a high transmission ratio can be achieved in a small space.

[0028] In an advantageous embodiment, the second sun gear has an axially penetrating, in particular centrally arranged, notch. The advantage here is that material can be saved, the dynamics of the reducer can be improved, the moment of inertia can be reduced, and the lubrication and cooling effect can be improved due to the axial flow of oil. However, in contrast to the second sun gear, the first sun gear is not hollow, but is designed as a solid component. Because only in this way can a clearly defined predetermined breaking point be obtained. Therefore, oil cannot flow through the first sun gear, and heat dissipation must be achieved by oil surrounding the second toothing area and oil flowing through the predetermined breaking point designed as a constriction.

[0029] In an advantageous embodiment, the second sun gear is hollow. The advantages are that material can be saved, the dynamics of the reducer can be improved, the moment of inertia can be reduced, and the lubrication and cooling effect can be improved due to the axial flow of oil. However, in contrast to the second sun gear, the first sun gear is not hollow, but is designed as a solid component. Because only in this way can a clearly defined predetermined breaking point be obtained. Therefore, the oil cannot flow through the first sun gear, and heat dissipation must be achieved by the oil surrounding the second tooth area and the oil flowing through the predetermined breaking point designed as a constriction.

[0030] In an advantageous embodiment, a sliding disk is accommodated in the first planet carrier, which axially limits the first sun gear, in particular the flange of the first sun gear. This has the advantage that the sliding disk is made of a hardened material, which reduces friction. In addition, oil flows through the radially directed channels, which is also conveyed under the action of centrifugal forces and forms a hydrodynamic buffer layer / hydraulic cushion (hydrodynamic Polster) for the first sun gear. As a result, axial limiting can be achieved at low cost and with low friction despite different rotational speeds.

[0031] In an advantageous embodiment, the sliding disk is held in the first planet carrier by force-locking means, in particular by means of a spring washer. This has the advantage that a simple and cost-effective fixing method can be used.

[0032] In an advantageous embodiment, the first planet carrier has an axially penetrating stepped hole.

[0033] The sliding plate abuts against the first step portion of the stepped hole.

[0034] In particular, the bearing of the first planetary gear abuts against the second step portion of the stepped hole. The advantage here is that the sliding plate can be reliably fixed. In addition, the first sun gear abuts against the sliding plate on the side of the sliding plate facing away from the first step portion. Therefore, the sliding plate is pressed against the first step portion and is thus reliably fixed. The advantage here is that efficient operation can be achieved, because the first sun gear is kept at a certain distance from the second sun gear (i.e., the center gear of the second planetary gear stage) by the sliding plate having a higher hardness than the end face hardness of the second sun gear. Therefore, the material of the sliding plate is different from the material hardness of the second sun gear, and in particular, the second sun gear and the first sun gear are made of the same material.

[0035] In an advantageous embodiment, the sliding disk is made of steel and is nitrided. This has the advantage that simple production can be achieved and a low friction coefficient can be obtained.

[0036] In an advantageous embodiment, the sliding disk has a centrally arranged, axially penetrating hole. This has the advantage that the lubricating oil can flow through the hole, i.e. without being influenced by centrifugal forces. Since there is no radial distance at this location, there is no centrifugal force either.

[0037] In an advantageous embodiment, one or more recesses are formed on the side of the sliding disk facing the first sun gear, and the recesses extend from a centrally arranged axially penetrating hole to a radially outer edge of the sliding disk.

[0038] In particular, a channel is formed which is delimited by the sliding disk and the first sun gear,

[0039] In particular, the recesses and / or channels are spaced equidistantly from one another in the circumferential direction. This has the advantage that lubricating oil can flow through the holes and can then be conveyed radially. In this way, planetary wheels arranged at positions with a radial distance other than zero can be easily lubricated, in particular needle bearings of the planetary wheels can be easily lubricated, because the planetary wheels are supported by needle bearings which are pushed onto pins of the planet carrier.

[0040] In an advantageous embodiment, the channel cross section increases first and then decreases with increasing radial distance. The advantage here is that the buffer volume is provided by the channel cross section increasing to a maximum value with increasing radial distance, and even with discontinuous filling of lubricating oil, the buffer volume can be continuously discharged at a greater radial distance, because when the radial distance increases further, the channel cross section decreases again from the maximum value. The channel then opens to the planetary gear, in particular to the bearing of the planetary gear, at this maximum radial distance.

[0041] In an advantageous embodiment, the reduction gear has more than two planetary gear stages arranged in series. This has the advantage that high transmission ratios can be achieved.

[0042] An important feature of a wind turbine with a rotatably arranged nacelle and a generator arranged in the nacelle is that the wind turbine has a reducer driven by an electric motor according to any of the preceding claims, the output shaft of which is connected to a pinion in a rotationally fixed manner, the pinion meshing with a ring gear, in particular wherein the toothing of the pinion meshes with the outer toothing of the ring gear,

[0043] In particular, the rotational position of the ring gear is the rotational position of the nacelle and / or determines the rotational position of the nacelle.

[0044] In particular, the reducer is connected to the nacelle, and the rotational position of the nacelle, in particular the rotational position of the nacelle relative to the ring gear, can be controlled by the rotational position of the ring gear relative to the reducer.

[0045] The advantage here is that in the event of an overload, the first sun gear is damaged. The ring gear is therefore protected and cannot be damaged by overload. This avoids expensive replacement of the ring gear.

[0046] Further advantages may be derived from the dependent claims. The invention is not limited to the combination of features in the claims. Other meaningful combinations of the claims and / or of the features of the individual claims and / or of the features of the description and / or of the features of the drawings will be apparent to the person skilled in the art, in particular from the objectives proposed and / or from the comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The invention will now be described in more detail with the aid of the accompanying schematic drawings:

[0048] FIG. 1 shows a planetary gear reducer according to the invention in a sectional view.

[0049] FIG. 2 shows the sun gear 1 of the planetary gear reducer in an oblique view.

[0050] FIG. 3 shows the sun gear 1 in a sectional view. DETAILED DESCRIPTION

[0051] As shown in the figures, a shaft 5 , in particular an input shaft of a planetary gear reducer, is rotatably supported by a bearing 2 mounted in a housing part, in particular a bearing flange 9 .

[0052] The shaft sealing ring 4 which is also mounted in the bearing flange 2 forms a seal against the shaft 5 .

[0053] Therefore, the bearing 2 is isolated from the oil coming from the inside of the planetary gear reducer.

[0054] In order to provide a bearing receptacle for the bearing 2 and a sealing ring receptacle for the shaft sealing ring 4 , the bearing flange has a hollow cylindrical supporting section which projects into the interior of the planetary gear reducer.

[0055] The bearing 2 and the shaft sealing ring 4 are spaced apart from one another in the axial direction, in particular in the direction of the rotation axis of the shaft 5 .

[0056] The channel 3 that radially penetrates the hollow cylindrical support section enables oil filling on the outer circumference of the hollow cylindrical support section. Another radially penetrating channel 6 is arranged on the hollow cylindrical section diametrically opposite to the first channel 3. Therefore, excessive filling of oil can be avoided.

[0057] The shaft 5 is connected to the first sun gear 1 in a rotationally fixed manner. For this purpose, the first sun gear 1 has a toothing that is interrupted in the axial direction (i.e., along the direction of the rotation axis of the first sun gear 1). Therefore, the first sun gear 1 has a first toothing area 20 and a second toothing area 21 spaced apart from the first toothing area 20 in the axial direction.

[0058] The two toothing regions 20, 21 have the same number of teeth, module and involute tooth profile parameters; only the tip circle diameters differ, since the tip circle diameter of the first toothing region 20 is smaller than the tip circle diameter of the second toothing region 21. In addition, the first toothing region has a guide chamfer, in particular a chamfered top region, on its end region axially facing away from the second toothing region 21. Therefore, the tip circle diameter of the first toothing region 20 increases monotonically as the distance from the second toothing region 21 decreases.

[0059] The second toothing region 21 meshes with the teeth of the first planetary gear 7, which in turn meshes with the internally meshing first toothed ring 8, which is non-rotatably connected to the bearing flange 9. The first planetary gear 7 is rotatably mounted on the first planet carrier 11, which drives the subsequent transmission stage.

[0060] For this purpose, the running gear of the second sun gear 12 is inserted into the inner gear region of the first planet carrier 11 in the first planet carrier 11, wherein the running gear is made uninterrupted. Thus, the second sun gear 12 is connected to the first planet carrier 11 in a rotationally fixed manner.

[0061] A first sliding plate 10 is accommodated on the side of the first planet carrier 11 that faces the first sun gear 1 in the axial direction. The outer diameter of the first sliding plate is larger than the tip circle diameter of the second toothing region of the first sun gear 1 .

[0062] The second sun gear 12 meshes with the second planetary gears 13 , which in turn mesh with the ring gear 8 having an internal toothing, or alternatively with another ring gear in other exemplary embodiments of the invention.

[0063] The second planetary gears 13 are rotatably mounted on a second planetary carrier 16 , which in turn is connected to the third sun gear 15 in a rotationally fixed manner by the running toothing of the third sun gear 15 engaging in the region of the inner toothing of the second planetary carrier 16 .

[0064] The first sun gear 1 is not hollow, but is in particular designed as a solid component. However, the second sun gear 12 is an axially through hollow structure, in particular designed as a hollow component. The clear inner diameter of the second sun gear 12 is in particular larger than the smallest outer diameter of the predetermined breaking point 30 of the first sun gear 1 which is implemented as a constriction.

[0065] The tip circle diameter of the second toothing region 21 is larger than the clear inner diameter of the hollow second sun gear 12 .

[0066] Therefore, the maximum transmittable torque of the first sun gear 1 is determined by the predetermined breaking point 30. In particular, the maximum transmittable torque of the second sun gear 12 is at least five or ten times the maximum transmittable torque of the first sun gear.

[0067] In this way, it can be ensured that, when the reducer is overloaded, although the first sun gear 1 may be damaged, other components of the reducer will not be damaged.

[0068] The second planet carrier 16 accommodates the second sliding disk 14 , which limits the second sun gear 12 in the axial direction.

[0069] The first sliding plate 10 limits the first sun gear 1 in the axial direction.

[0070] The first sun gear 1 has a flange 31 at its axial end region facing the first sliding disk 10 , so that the outer diameter of the axial end face of the first gear 1 that can abut against the sliding disk 10 is smaller than the tip circle diameter of the second toothing region 21 of the first sun gear 1 .

[0071] The predetermined breaking point 30 is designed as a constriction whose minimum outer diameter is smaller than the minimum root circle diameter of the first toothing region 20 and also smaller than the minimum root circle diameter of the second toothing region 21 .

[0072] As shown in Fig. 3, the predetermined breaking point 30 has a rounded portion, and the cross section of the rounded portion is semicircular, so that simple manufacturing can be achieved by utilizing the radius.

[0073] However, it is particularly advantageous if the rounding is not a semicircular rounding but a semi-elliptical rounding, because in particular if the rounding is designed as a rotating body section with a semi-elliptical cross section, the maximum transmittable torque can be predefined as accurately as possible and in the event of an overload, zero or at least as few fragments as possible can be achieved in the event of a predetermined break.

[0074] In this way, although the first sun gear 1 is damaged and the input shaft 5 can rotate freely relative to the output shaft of the reducer, there are only a few metal particles inside the reducer filled with oil, so when repairing (i.e. replacing) the first sun gear 1, simply replacing the first sun gear 1 is sufficient to put it back into operation.

[0075] Preferably, the reducer according to the present invention is applied to the yaw angle adjustment mechanism of the wind power plant, specifically, in particular, in a device for rotating the nacelle of the wind power plant. To this end, the motor drives the input shaft 5, and the output shaft therefore only rotates slowly, but can generate a torque large enough for the yaw angle adjustment of the wind power plant. During operation, if the torque required for yaw angle adjustment exceeds a threshold value, for example, because the yaw angle adjustment mechanism is stuck, the torque transmitted through the first sun gear 1 will exceed the threshold value, and the first sun gear 1 will be damaged at the predetermined fracture position 30. In this way, other components, especially those with high manufacturing costs, are protected, because after the first sun gear 1 is damaged, the output shaft of the reducer is still in a freely rotatable state. As a result, the nacelle will adjust itself according to the air resistance, and the wind power plant can stop operating.

[0076] The output shaft of the reducer is connected to the pinion in a non-rotatable manner, and the pinion is meshed with the ring gear. Therefore, by controlling the motor driving the input shaft 5, the rotation angle of the ring gear can be adjusted, and then the rotation angle of the wind power generation equipment cabin can be adjusted.

[0077] Preferably, the outer diameter of the ring gear is at least five times the outer diameter of the pinion which is connected to the output shaft in a rotationally fixed manner.

[0078] In the event of an overload, the ring gear, which is expensive to manufacture, can be protected by causing the first sun gear 1 located on the input side to be destroyed at the predetermined breaking point 30 .

[0079] In other embodiments of the present invention, a plurality of geared motors according to the present invention are arranged in a wind turbine, and all of the geared motors act on the same gear ring, in particular for rotating the nacelle.

[0080] List of reference numerals:

[0081] 1 Sun gear

[0082] 2 Bearings

[0083] 3 channels

[0084] 4 Shaft seals

[0085] 5-axis

[0086] 6 channels

[0087] 7 Planetary gear

[0088] 8 Gear ring

[0089] 9 Bearing flange

[0090] 10 Sliding plate

[0091] 11 Planet carrier

[0092] 12 Second sun gear

[0093] 13 Second planetary gear

[0094] 14 Second sliding plate

[0095] 15 Third sun gear

[0096] 20 First tooth area

[0097] 21 Second tooth area

[0098] 30 Predetermined fracture site

[0099] 31 Flange

Claims

1. A reduction gear, in particular a planetary gear reduction gear, comprising a first sun gear (1), in particular a first sun gear (1) arranged in a rotatable manner, The toothing of the first sun gear (1) has an interruption such that a first toothing region (20) of the toothing is spaced apart from a second toothing region (21) of the toothing in the axial direction. In the axial direction, in the region between the first tooth region (20) and the second tooth region (21), the minimum outer diameter of the first sun gear (1) is smaller than the tooth root diameter. In particular, the toothing is designed as a straight toothing. In particular, the axial direction is parallel to the rotation axis of the first sun gear (1).

2. The reducer according to claim 1, It is characterized in that The predetermined breaking point (30) is designed as a constriction. The minimum outer diameter of the predetermined breaking point (30) is smaller than the root circle diameter of the tooth portion.

3. A reducer according to any one of the preceding claims, It is characterized in that The predetermined breaking point (30) is formed as a rotating body segment, the rotational symmetry axis of the rotating body segment is coaxial with the rotation axis of the first sun gear (1), The curve that generates the solid of revolution is a semicircle or a semi-ellipse.

4. A reducer according to any one of the preceding claims, It is characterized in that The body of revolution is concave and / or the outer diameter of the body of revolution sections increases strictly monotonically with increasing axial distance from the narrowest point of the body of revolution, ie the axial position at which the body of revolution has the smallest outer diameter.

5. A reducer according to any one of the preceding claims, It is characterized in that The toothing is designed as a spur toothing.

6. A reducer according to any one of the preceding claims, It is characterized in that The toothed portion meshes with the internal toothed portion of the shaft (5), so that the shaft (5) and the first sun gear (1) are connected in a manner that they cannot rotate relative to each other. and / or, The shaft (5) has a blind hole with an internal toothing, into which the toothing of the first sun gear (1) is partially inserted.

7. A reducer according to any one of the preceding claims, It is characterized in that The first sun gear (1) has a flange (31) on the side axially facing away from the shaft (5), i.e., a cylindrical section, the outer diameter of the flange being smaller than the tooth root diameter of the toothing and larger than the minimum outer diameter of the predetermined breaking point (30), In particular, the flange (31) is spaced apart from the predetermined breaking point (30) in the axial direction.

8. A reducer according to any one of the preceding claims, It is characterized in that The first sun gear (1) is an integral component. In particular, the first sun gear (1) is not a hollow component.

9. A reducer according to any one of the preceding claims, It is characterized in that In a region covered by the predetermined breaking point (30) in the axial direction and / or in a region located in the axial direction between the first toothing region (20) and the second toothing region (21), Radially inside the smallest outer diameter of the predetermined breaking point (30), the material of the first sun gear (1) is designed to be gap-free and / or interruption-free and / or is embodied uniformly.

10. A reducer according to any one of the preceding claims, It is characterized in that The first sun gear (1) meshes with the planetary gears, and the planetary gears mesh with the gear ring (8) having an internal tooth portion. The planetary gears are rotatably arranged on the planetary carrier (11). The planet carrier has a hole with an internal toothing, into which the toothing of the second sun gear (12) is partially inserted.

11. The reducer according to claim 10, It is characterized in that The second sun gear (12) has an axially extending, in particular centrally arranged, recess. and / or, The second sun gear (12) is hollow.

12. The reducer according to claim 10 or 11, It is characterized in that A sliding disk (10) is received in the first planet carrier (11), and the sliding disk axially limits the first sun gear, in particular limits the flange (31) of the first sun gear (1).

13. The reducer according to claim 12, It is characterized in that The sliding plate (10) is axially arranged between the first sun gear (1) and the second sun gear (12). In particular: - the sliding disk (10) has an axially continuous, in particular centrally arranged, hole; - and / or, the sliding plate (10) is made of steel and is nitrided; - and / or, one or more recesses are formed on the side of the sliding plate (10) facing the first sun gear (1), the recesses respectively extending from a centrally arranged, axially penetrating hole to the radial outer edge of the sliding plate (10), In particular, channels (3, 6) are formed which are respectively delimited by the sliding disk (10) and the first sun gear (1), in particular the flange (31). In particular, the recesses and / or channels are spaced equidistantly from one another in the circumferential direction. In particular, the channel cross section first increases and then decreases with increasing radial distance. In particular, the bore opens into the recess and / or the channel (3, 6), in particular such that lubricating oil entering through the bore can be conveyed radially outwards through the channel (3, 6).

14. A reducer according to any one of the preceding claims, It is characterized in that The speed reducer has more than two planetary gear stages which are arranged in series.

15. A wind power plant with a rotatably arranged nacelle, in which a generator is arranged, The wind power plant comprises a reducer according to any one of the preceding claims, which is driven by an electric motor, wherein the output shaft of the reducer is connected to a pinion in a rotationally fixed manner, the pinion meshes with a ring gear, in particular, the toothed portion of the pinion meshes with the outer toothed portion of the ring gear, In particular, the rotational position of the ring gear is the rotational position of the nacelle and / or determines the rotational position of the nacelle. In particular, the reduction gear is connected to the nacelle, and the rotational position of the nacelle, in particular the rotational position of the nacelle relative to the ring gear, can be controlled by the rotational position of the ring gear relative to the reduction gear.

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