Damper device for reducing transmission of vibrations

Abstract

The invention relates to a method for operating an elongated first component (10; 30) for a vehicle body (10; 140), the first part (10; 30) is arranged in the longitudinal direction (LD) of the connection end (11; 31) for mechanical connection to the second component (20). The damper device (40; 140) comprises at least two damper groups (41a, 41b, 41c, 41d, 41e) which are arranged between the first part (10; 30) having the connection end (11; 31) and an end section (12; 32) and are spaced apart from one another in the longitudinal direction (LD), each of the damper groups (41a, 41b, 41c, 41d, 41e) comprising a plurality of individual dampers (42a, 42b, 42c, 42d, 42e) distributed in the circumferential direction (CD) in the first part (10; 30) on the peripheral wall (14). In order to reduce problems due to tones in the wind turbine (1) in a simple and cost-effective manner, the damper sets have natural frequencies that differ from one another. The invention also relates to a wind turbine (1).

Description

[0001] The invention relates to a damper device for an elongated first component, which is arranged at a connection end in a longitudinal direction of the first component for a mechanical connection with a second component.

[0002] A typical wind turbine comprises a tower, a nacelle with a rotor hub and several rotor blades, each of which is attached to the rotor hub. During operation, vibrations occur and the wind turbine emits sound emissions. So-called "tones" in the sound emissions of wind turbines are considered particularly disturbing. They can lead to a violation of legal limits on noise emissions. In some cases, the power of the wind turbine has to be reduced in order to reduce the noise emissions. This leads to economic disadvantages.

[0003] The cause of the tones is a source of vibrations in the drive train of the wind turbine. The drive train comprises, for example, a generator and a gearbox. The drive train, in particular the generator and the gearbox, is located in the nacelle. The vibrations generated there are transmitted to the rotor blades and the tower and they are further propagated therein, respectively. The main acoustic emitters of the tones are the tower and the rotor blades, not the nacelle itself.

[0004] According to a known method, it is attempted to dampen the vibrations directly at the drive train. By this method, the vibrations are reduced before they are transmitted from the nacelle to the tower and the rotor blades. By passive and active dampers, it is possible to reduce the vibrations directly at the drive train. Designing active and passive dampers directly at the drive train first requires a characterization of the tone problem, i.e. the determination of the relevant frequencies and the tone audibility. The vibrations in the drive train during operation are then usually investigated by using a large number of acceleration sensors and measurement data. From the results (based on the vibration modes and acoustics during operation), the suitable locations of the dampers are derived. This is followed by an analysis of the available installation space and the design task to implement the damper solution on the drive train. Therefore, designing active and passive dampers directly at the drive train is very complex. In addition, there is the problem that the installation space on the drive train is very limited.

[0005] A disadvantage of passive dampers on the drive train is that they only work in a narrow band. This means that they are only effective in a small frequency range. Active dampers on the drive train are very powerful, but also expensive. In particular for slight tone problems, a solution using active dampers on the drive train can be too cost-intensive.

[0006] US 10,408,194 B2 shows an acoustic damping system for a wind turbine tower. This method is directed to a large-area damping of the tower against vibrations. For this purpose, a vibration damper must be installed at all locations on the tower where vibrations exceed a certain threshold. The vibration dampers must be distributed over a large area of the tower and installed at many different locations on the tower. This large-area damping with vibration dampers at many different locations on the tower is disadvantageous due to the high costs, the high additional weight of the vibration dampers and the effort required.

[0007] Another approach is to sufficiently reinforce the respective main emitter. However, this approach also has disadvantages due to the high quality, effort and costs required.

[0008] EP 3 211 218 A1 discloses an acoustic damping system for a wind turbine tower.

[0009] Furthermore, EP 2 238 347 A2 relates to a method for reducing sound emission from a wind turbine tower, and to a wind turbine.

[0010] In CN 114 151 274 A, a wind turbine rotor blade with a plurality of wind-resistant damping components is shown.

[0011] The object on which the present invention is based is to reduce problems in wind turbines due to tonalities in a simple and cost-effective manner.

[0012] The problem is solved by a vibration damper arrangement according to the invention.

[0013] The vibration damper arrangement is for an elongated first component, which is configured at a connection end (in the longitudinal direction of the first component) for a mechanical connection with a second component.

[0014] The vibration damper arrangement comprises at least two vibration damper groups, which are arranged in an end section of the first component having the connection end and are spaced apart from each other in the longitudinal direction.

[0015] Each of the vibration damper groups comprises a plurality of individual vibration dampers, which are distributed in a circumferential direction on a circumferential wall of the first component.

[0016] The vibration damper arrangement is suitable and / or configured to reduce the transmission of vibrations from the connection end, in particular to reduce the transmission of vibrations from the connection end to a section of the first component beyond the end section.

[0017] The vibration transmission caused by vibrations in the drive train is locally reduced in the end section at the connection end, for example in the end section of the tower head or in the end section at the root of the rotor blade. No further vibration damping needs to be implemented on the first component (e.g. tower or rotor blade) outside the end section. This means that the first component does not need to be "globally" damped. This ensures low costs.

[0018] The damper device shields the rest of the first component from the vibrations introduced at the connection end.

[0019] The invention is described below based on its use in a wind turbine. However, it can also be used in other elongated structures and components.

[0020] According to one aspect, the first component can be at least partially hollow.

[0021] In one embodiment, the individual dampers of each damper group are arranged in a ring. Each damper group forms a "damper ring". The damper rings are spaced apart from each other in the longitudinal direction. All damper rings are arranged in the end section. This allows easy planning and installation.

[0022] In one variant, the damper device comprises at least three damper groups (e.g. damper rings). In particular, the damper device can comprise at least five damper groups (e.g. damper rings).

[0023] In one embodiment, the damper device comprises at most twelve damper groups (e.g. damper rings). It has proven to be sufficient in this way to counter the tonal. A smaller number of damper groups saves effort and costs.

[0024] According to one aspect, the individual dampers in the end section can be arranged one after the other spaced apart from each other in the longitudinal direction. "Longitudinal assemblies" are repeated spaced apart from each other at an angular distance in the circumferential direction, preferably around the entire circumference. Thereby, the damper groups spaced apart from each other in the longitudinal direction are formed.

[0025] According to one aspect, the individual dampers of each damper group can be arranged uniformly in the circumferential direction. For example, they can be arranged at equal intervals in the circumferential direction and / or at equal angular distances around the (possibly local) longitudinal axis and / or central axis of the first component at the location of the respective damper ring.

[0026] The second component can be a wind turbine nacelle. The connection end is a nacelle-side end of the first component. The end section is a nacelle-side end section. While the origin of the tonal of the wind turbine is the vibration source in the drive train in the nacelle, the nacelle is not the main acoustic emitter of the disturbing sound emission. The main acoustic emitters are the tower and the rotor blades of the wind turbine. It is sufficient to reduce the vibration transmission in the nacelle-side end section. While vibrations at the connection end (at the nacelle-side end) of the first component can still be transmitted to the first component, their further transmission in the first component is reduced in the (nacelle-side) end section. They cannot propagate freely and the risk of emitting a disturbing tone is reduced. If applicable, active and / or passive dampers in the nacelle itself can be omitted. This saves costs and installation space in the nacelle.

[0027] In one embodiment, the first component is a wind turbine tower and the connection end is an upper end of the wind turbine tower for supporting the wind turbine nacelle.

[0028] The wind turbine tower is a tower of a wind turbine or a tower for a wind turbine.

[0029] In this case, the end section is an upper part of the tower (tower head). The complete damper arrangement can be installed locally in the tower head. The nacelle rests on the tower head. Vibrations from the nacelle are transmitted to the tower head by the connection, but they have already been reduced inside the tower head by the damper arrangement.

[0030] According to one aspect, in particular if the first component is a tower, adjacent damper groups can be spaced apart along the longitudinal direction by less than 300 cm, for example less than 110 cm. Alternatively or additionally, the individual dampers within each of the damper groups can be spaced apart along the circumferential direction by less than 200 cm, for example less than 66 cm.

[0031] It turns out that this arrangement is advantageous for exemplary steel towers with an overall height between 50 m and 150 m, an average diameter between 3 m and 5 m and an average wall thickness between 2 cm and 5 cm. For example, the above-mentioned criteria contribute to achieving a vibration reduction in the important frequency range of around 100 Hz, respectively.

[0032] According to another aspect, the second component can be a wind turbine nacelle with a rotor hub. The first component can be a wind turbine rotor blade, wherein the connection end is a blade root (of the rotor blade) for attachment to the rotor hub.

[0033] The wind turbine rotor blade is a rotor blade of a wind turbine or a rotor blade for a wind turbine.

[0034] According to one aspect, especially if the first component is a rotor blade, adjacent damper groups can be spaced apart in the longitudinal direction by less than 300 cm, for example less than 90 cm. Alternatively or additionally, the individual dampers within each of the damper groups can be spaced apart in the circumferential direction by less than 100 cm, for example less than 34 cm. This applies to blades with a length of 50 m, an average diameter of between 0.5 m and 1.5 m and a wall thickness of between 1 cm and 3 cm.

[0035] If the maximum distance of the individual dampers within each damper group in the circumferential direction and the maximum distance between the damper groups (in the longitudinal direction) is not exceeded, a significant reduction of the transmission of vibrations is achieved. The maximum distances can be determined by simulation and / or measurement. They can be different for different variants of tower and rotor blades.

[0036] According to one aspect, the damper groups (the individual dampers) are attached to the inner side of the peripheral wall. This protects the dampers from weather and facilitates installation.

[0037] In one variant, the damper groups have an inherent frequency in the range of 50 Hz to 500 Hz. In practice, vibrations in this range are often the cause of disturbing tones, which is why their transmission should be reduced in particular.

[0038] Within each of the damper groups, all individual dampers can have the same inherent frequency. Alternatively or additionally, all individual dampers within each damper group can be of the same type. In particular, all individual dampers within each damper group can be structurally identical.

[0039] The inherent frequency of each of the individual dampers can be designed by the damper mass and the stiffness of the individual dampers.

[0040] In one embodiment, the damper groups have different inherent frequencies. Each damper group has a separate inherent frequency. This enables a broader band of vibration reduction and / or reduction in several frequency ranges. In one embodiment, each inherent frequency of the damper groups is designed for a target frequency, respectively, to reduce the tone of the wind turbine.

[0041] The individual dampers of each damper group can differ from the individual dampers of the other damper groups in their damper mass and / or stiffness. This is an effective method to implement vibration reduction for different frequencies or frequency ranges.

[0042] Each of the damper groups can have a frequency reduction range around its natural frequency. In one embodiment, the frequency reduction range of each damper group overlaps at least one of the frequency reduction ranges of another of the damper groups. The frequency reduction range can include a range of frequencies around the natural frequency until a reduction of 80% of the reduction at the natural frequency is reached.

[0043] According to a further aspect, each damper group comprises at least 5 dampers. This facilitates a high reduction of the transmission of vibrations.

[0044] In one variant, at least one of the damper groups is arranged in a portion that extends along the longitudinal direction more than 10% of the total length of the first component from the connection end. Thereby, at least part of the vibrations is reduced in the immediate vicinity of the connection end where the vibrations are introduced into the first component. In particular, at least two, even at least three, of the damper groups can be arranged in a portion that extends along the longitudinal direction more than 10% of the total length of the first component from the connection end.

[0045] In one embodiment, the end portion extends at most 14% from the connection end. The end section does not extend far from the connection end. The reduction of vibrations takes place in the vicinity of the connection end where the vibrations that are decisive for the tone are introduced. This prevents the first component from acting as a strong main acoustic emitter with a large area.

[0046] Alternatively or additionally, the damper device can be located entirely in the end section. All individual dampers of the damper device are located within the end section. Outside the end section, the damper device has no dampers on the first component.

[0047] In one variant, all individual dampers are passive dampers. Passive dampers are easier to design and more cost-effective. The disadvantage of a narrow bandwidth can be compensated by providing several damper groups. The passive dampers can comprise a damper mass and a stiffness. The damper mass is mechanically coupled to the first component by the stiffness. The passive dampers can be made of metal, for example steel. They can have a steel stiffness.

[0048] The frequency range (or the frequency ranges) and the desired amplitude reduction can be designed by adjusting the spacing of the damper groups along the longitudinal direction, the number of individual dampers per damper group, the damper mass of the individual dampers, the number of damper groups, and the tuning of the natural frequencies of the damper groups.

[0049] The individual dampers can be attached to the first component by a magnetic base, an adhesive, a screw, and / or a weld, respectively.

[0050] The above problems are also solved by a first component, such as a wind turbine tower or a wind turbine rotor blade, comprising a damper device according to any of the described embodiments.

[0051] The above problems are also solved by a wind turbine comprising a damper device according to any of the described embodiments.

[0052] The above embodiments and advantages apply accordingly.

[0053] The invention is explained below with reference to embodiments and with reference to the drawings. All features described and / or illustrated herein, individually or in any combination, constitute the subject matter of the invention, regardless of their combination in the claims or their reference to the foregoing claims.

[0054] The drawings schematically show:

[0055] Figure 1 a wind turbine having a tower, a nacelle and several rotor blades, wherein the tower and the rotor blades each have a damper device;

[0056] Figure 2 an embodiment of a damper device for a tower of a wind turbine in Figure 1

[0057] Figure 1 A side view of an embodiment of a wind turbine 1 is shown having a tower 10, a nacelle 20 and several rotor blades 30, more specifically three rotor blades 30. The tower 10 extends vertically upward from a lower end 15 on the ground along a longitudinal direction LD (see Figure 2 ) with a total length L10 to an upper end. The upper end forms a connection end 11 for the nacelle 20. The nacelle 20 is mounted on the connection end 11 of the tower 10.

[0058] The nacelle 20 comprises a rotor hub 21. The rotor blades 30 are attached with their blade roots 31 to the rotor hub 21, respectively. For the rotor blades 30, the blade root 31 is the "connection end" for attachment to the nacelle 20, more specifically to its rotor hub 21. The rotor blades 30 each extend along their longitudinal direction from the blade root 31 over a total length L30. In Figure 1 , the longitudinal direction of the rotor blades 30 is not shown separately. For the lower rotor blades 30, the longitudinal direction is parallel to the arrow indicating the total length L30.

[0059] ​The nacelle 20 contains a drive train, for example comprising a gearbox 22 and a generator 23. During operation of the wind turbine 1, the drive train causes oscillations or vibrations. The vibrations are introduced into the tower 10 at the connection end 11 (upper end) of the tower 10. They are also introduced into the blade roots 31 of the rotor blades 30 through the rotor hub 21. If no measures are taken, the tower 10 and the rotor blades 30 can act as main emitters of disturbing tonal sound emissions.

[0060] In order to reduce the transmission of vibrations from the connection end 11 (upper end) of the tower 10 on which the nacelle 20 rests to the main region 13 of the tower 10, a vibration damper device 40 is installed in the upper end section 12 of the tower 10. The end section 12 of the tower 10 is located directly at the connection end 11 (upper end) of the tower 10 with the nacelle 20. The end section 12 of the tower 10 at the connection end 11 can be said to form a "tower head".

[0061] For the vibration damper assembly 40, the tower 10 forms an elongated first component for connection to a second component, namely the nacelle 20, at the connection end 11 of the tower 10.

[0062] For the vibration damper device 140, the respective rotor blade 30 forms an elongated first component for connection to a second component, namely the nacelle 20, at the connection end, namely the respective blade root 31.

[0063] The tower 10 is at least partially "hollow". It forms a tower interior space at least section-wise. The rotor blades 30 can also be at least partially "hollow". They form a blade interior space at least section-wise, respectively.

[0064] Figure 2 The vibration damper device 40 is shown in detail. It is installed completely in the tower head.

[0065] The vibration damper device 40 comprises a plurality of vibration damper groups 41a, 41b, 41c, 41d, 41e. Here, five vibration damper groups 41a, 41b, 41c, 41d, 41e are shown by way of example. All vibration damper groups 41a, 41b, 41c, 41d, 41e are installed only in the end section 12 of the tower 10 at the connection end 11, i.e. in the tower head.

[0066] Each damper group 41a, 41b, 41c, 41d, 41e comprises a plurality of individual dampers 42a, 42b, 42c, 42d, 42e. The individual dampers 42a, 42b, 42c, 42d, 42e of the respective damper group 41a, 41b, 41c, 41d, 41e are mounted on the peripheral wall 14 of the first component, in this case the tower 10. More precisely, in this example, they are fixed to the inner side of the peripheral wall 14. The individual dampers 42a, 42b, 42c, 42d, 42e of the respective damper group 41a, 41b, 41c, 41d, 41e are distributed in the circumferential direction CD, in this embodiment at equal intervals in the circumferential direction CD. The individual dampers 42a, 42b, 42c, 42d, 42e of the respective damper group 41a, 41b, 41c, 41d, 41e are arranged in a ring, more precisely in a ring around the longitudinal axis LA of the first component, in this case the tower 10. Each damper group 41a, 41b, 41c, 41d, 41e thus forms a separate “damper ring” with the plurality of associated individual dampers 42a, 42b, 42c, 42d, 42e.

[0067] For example, the first damper group 41a (first damper ring) closest to the connection end 11 comprises a plurality of first individual dampers 42a. The first damper group 41 does not necessarily have to be mounted directly on the connection end 11. However, for example, it can be mounted directly on the connection end 11 or in the vicinity of the connection end 11. The adjacent second damper group 42b (second damper ring) comprises a plurality of second individual dampers 42b, and so on.

[0068] The damper groups 41a, 41b, 41c, 41d, 41e are spaced apart from one another in the longitudinal direction LD. In this example, all adjacent damper groups 41a, 41b, 41c, 41d, 41e are uniformly spaced apart from one another by a longitudinal distance LS. In a variant (not shown), the longitudinal distance between individual adjacent damper groups 41a, 41b, 41c, 41d, 41e or all adjacent damper groups 41a, 41b, 41c, 41d, 41e can be different.

[0069] In this embodiment, in the longitudinal distance LS between adjacent damper groups 41a, 41b, 41c, 41d, 41e, there is respectively a “damper-free region” without individual dampers 42a, 42b, 42c, 42d, 42e.

[0070] Each damper group 41a, 41b, 41c, 41d, and 41e has its own natural frequency. The natural frequencies of all damper groups 41a, 41b, 41c, 41d, and 41e are different. This allows the damper unit to reduce vibrations at several different frequencies and / or within several different frequency ranges. Each natural frequency can be designed separately for a specific tone.

[0071] In this example, each of the individual dampers 42a, 42b, 42c, 42d, and 42e comprises a damper mass and a stiffness. The damper mass is attached to the peripheral wall 14 of the tower 10 by a stiffness (e.g., steel stiffness), in this case, to the inside of the peripheral wall 14. The individual dampers 42a, 42b, 42c, 42d, and 42e of the damper group 41a, 41b, 41c, 41d, and 41e have the same natural frequency, which is the natural frequency of the damper group 41a, 41b, 41c, 41d, and 41e. The natural frequencies of individual dampers 42a, 42b, 42c, 42d, 42e, and therefore the corresponding damper groups 41a, 41b, 41c, 41d, 41e, can be adjusted by the size and / or stiffness of the damper mass, thus allowing for specialized design. According to one aspect, all individual dampers 42a, 42b, 42c, 42d, 42e within the same damper group 41a, 41b, 41c, 41d, 41e can be of the same type, and in particular, structurally identical. This reduces costs.

[0072] Here, the individual dampers 42a, 42b, 42c, 42d, 42e of the corresponding damper groups 41a, 41b, 41c, 41d, 41e differ in their damper mass and / or stiffness from the individual dampers 42a, 42b, 42c, 42d, 42e of the other damper groups 41a, 41b, 41c, 41d, 41e.

[0073] According to a further aspect, individual (e.g.) dampers 42a, 42b, 42c, 42d, 42e with different natural frequencies are mounted in series, spaced apart from each other, along the longitudinal direction LD on the peripheral wall 14 in the end section 12. The damper assembly 40 can be formed by repeating this linear “damping chain” along the circumferential direction CD (e.g., around the longitudinal axis LA at uniform angular intervals).

[0074] exist Figure 2 In this design, all individual dampers 42a, 42b, 42c, 42d, and 42e are designed as passive dampers. This makes the damper assembly 40 particularly cost-effective, simple, and reliable.

[0075] In general, the first damper group 41a does not have to be located directly at or immediately adjacent to the connection end 11. However, it can optionally be implemented that at least the first damper group 41a is arranged in a portion of the total length L10 of the first component (here: the tower 10) that extends in the longitudinal direction L10 from the connection end 11 by only 10%. In Figure 2 In the embodiment shown, the first damper group 41a is even arranged directly at or immediately adjacent to the connection end 11. In addition, at least the second damper group 41b is also arranged in a portion of the total length L10 of the first component (here: the tower 10) that extends in the longitudinal direction L10 from the connection end 11 by only 10%. A third damper group 41c, which is adjacent to the second damper group 41b in the longitudinal direction LD and which is located on the opposite side from the first damper group 41a, can also be arranged in this portion.

[0076] In this exemplary embodiment, the end section 12 in which all damper groups 41a, 41b, 41c, 41d, 41e are arranged extends in the longitudinal direction LD from the connection end 11 by at most 14%, for example by at most 14%, of the total length L10 of the first component 10. The main portion 13 of the first component (in this case the tower 10) is correspondingly large. Since the reduction in the transmission of vibrations occurs in the relatively short end section 12 that is located directly at the connection end 11, the proportion of the reduction in the vibrations associated with the tone does not even reach the much larger main portion 13. As a result, the main portion 13 cannot appear as a problematic acoustic emitter, or only to a greatly reduced extent. One advantage is that there is no need to install damper groups 41a, 41b, 41c, 41d, 41e and individual dampers 42a, 42b, 42c, 42d, 42e in the main portion 13. In the embodiment shown, the main portion 13 is “undamped”. This means, in comparison with a large-area damping of the tower 10, a considerably less effort and cost.

[0077] The design of the damping device 40 is generally dependent on the size, shape and material of the tower 10. Only exemplary embodiments are described below.

[0078] Assuming for a tower 10 made of (at least substantially) steel and having a total length L0 of between 50 m and 150 m, an average diameter of between 3 m and 5 m and an average wall thickness (of the peripheral wall 14) of between 2 cm and 5 cm, that a good reduction in the transmission of vibrations is to be achieved at 100 Hz, then the longitudinal distance LS should be less than 300 cm, or even better, less than 110 cm. The circumferential distance CS of the individual dampers 42a, 42b, 42c, 42d, 42e of the respective damper group 41a, 41b, 41c, 41d, 41e should be less than 200 cm, or even better, less than 66 cm, in the circumferential direction CD.

[0079] Assuming the tower 10 is made of steel (at least essentially) and is 50 m high, has an average diameter of 6 m and an average wall thickness of 3 cm. Furthermore, the vibration transmission in the frequency range of about 250 Hz should be reduced by the vibration damper device 40. Then the longitudinal spacing LS should be less than 86 cm. The circumferential distance CS (along the circumferential direction CD) of the individual dampers 42a, 42b, 42c, 42d, 42e of the respective damper groups 41a, 41b, 41c, 41d, 41e should be less than 55 cm.

[0080] Assuming the tower 10 is 100 m high, has an average diameter of 4 m and an average wall thickness of 3 cm. Furthermore, the vibration transmission in the range of 95 Hz to 105 Hz should be reduced (at least) by 10 dB from the connection end 11 to the main region 13 by the vibration damper device 40. This can be achieved, for example, by the vibration damper device 40 having a relative weight in the range of 0.1% to 0.2% relative to the weight of the tower 10. In the exemplary embodiment, the vibration damper device 40 consists of 80 damper groups 41a, 41b, 41c, 41d, 41e, each consisting of approximately 280 individual dampers 42a, 42b, 42c, 42d, 42e. The vibration damper device consists of approximately 22,400 individual dampers 41a, 41b, 41c, 41d, 41e in total, each having a damper mass of 28 g. The end section 11 extends only over the uppermost 10 m of the tower 10. All 80 damper groups 41a, 41b, 41c, 41d, 41e are mounted in the uppermost 10 m of the tower 10.

[0081] The vibration damper device 140 at the blade root 31 of the rotor blade 30 is configured in the same way as the vibration damper device 40 in the tower head. Due to the smaller size of the rotor blade 30, the distance between the vibration damper devices 140 can also be different, in particular smaller. The design of the vibration damper device 140 generally depends on the size, shape and material of the rotor blade 30. Only exemplary embodiments are described below.

[0082] Assuming the rotor blade 30 is made of glass fiber reinforced plastic (at least essentially), is 50 m long, has an average diameter in the range of 0.5 m to 1.5 m, and an average wall thickness of between 1 cm and 3 cm. Furthermore, the vibration transmission in the frequency range of about 100 Hz should be reduced by the vibration damper device 140. In this case, the longitudinal spacing of the damper groups should be less than 300 cm, or even better, less than 90 cm. The circumferential distance (along the circumference) of the individual dampers within the respective damper groups should be less than 100 cm, or even better, less than 34 cm.

Claims

1. A damper device (40; 140) for an elongated first component (10; 30), the first component being arranged along the longitudinal direction (LD) of the first component (10; 30) at a connecting end (11; 31) for mechanical connection with a second component (20), in, The vibration damper assembly (40; 140) includes at least two damper groups (41a, 41b, 41c, 41d, 41e), which are arranged in the end section (12; 32) of the first component (10; 30) having the connecting end (11; 31) and spaced apart from each other along the longitudinal direction (LD). Each of the damper groups (41a, 41b, 41c, 41d, 41e) includes multiple individual dampers (42a, 42b, 42c, 42d, 42e), which are arranged circumferentially (CD) on the peripheral wall (14) of the first component (10; 30). The damper group (41a, 41b, 41c, 41d, 41e) is characterized in that it has different natural frequencies from each other.

2. The vibration damper device (40; 140) according to claim 1, wherein, The individual dampers (42a, 42b, 42c, 42d, 42e) of each of the damper groups (41a, 41b, 41c, 41d, 41e) are arranged in a ring.

3. The vibration damper device (40) according to claim 1 or 2, wherein, The second component (20) is the wind turbine nacelle. The first component is a wind turbine tower (10), and the connecting element (11) is the upper end of the wind turbine tower (10) for supporting the wind turbine nacelle (20).

4. The vibration damper device (40) according to claim 3, wherein, Adjacent damper groups (41a, 41b, 41c, 41d, 41e) are spaced less than 300 cm apart along the said longitudinal direction (LD), and / or The individual dampers (42a, 42b, 42c, 42d, 42e) within each of the damper groups (41a, 41b, 41c, 41d, 41e) are spaced less than 200 cm apart from each other along the circumferential direction (CD).

5. The vibration damper device (140) according to claim 1 or 2, wherein, The second component is a wind turbine nacelle (20) with a rotor hub (21). The first component is a wind turbine rotor blade (30), wherein the connecting end is a blade root (31) for attaching to the rotor hub (21).

6. The vibration damper device (140) according to claim 5, wherein, Adjacent shock absorber groups are spaced less than 300 cm apart along the longitudinal direction, and / or In this embodiment, the individual dampers within each damper group are spaced less than 100 cm apart along the circumferential direction.

7. The damper device (40; 140) according to any one of the preceding claims, wherein, The individual dampers (42a, 42b, 42c, 42d, 42e) within each of the damper groups (41a, 41b, 41c, 41d, 41e) have the same natural frequency and / or belong to the same type.

8. The damper device (40; 140) according to any one of the preceding claims, wherein, The individual dampers (42a, 42b, 42c, 42d, 42e) of each damper group (41a, 41b, 41c, 41d, 41e) differ from the individual dampers (42a, 42b, 42c, 42d, 42e) of the other damper groups (41a, 41b, 41c, 41d, 41e) in terms of their damper mass and / or their stiffness.

9. The damper device (40; 140) according to any one of the preceding claims, wherein, The damper device (40; 140) is completely arranged in the end section (12; 32).

10. The damper device (40; 140) according to any one of the preceding claims, wherein, At least one of the damper assemblies (41a, 41b, 41c, 41d, 41e) is arranged in a region extending along the longitudinal direction (LD) from the connection end (11; 31) beyond 10% of the total length (L10; L30) of the first component (10; 30).

11. The vibration damper device (40; 140) according to claim 10, wherein, At least two of the damper groups (41a, 41b, 41c, 41d, 41e) are arranged in a region extending along the longitudinal direction (LD) from the connection end (11; 31) beyond 10% of the total length (L10; L30) of the first component (10; 30).

12. The damper device (40; 140) according to any one of the preceding claims, wherein, The end section (12; 32) extends along the longitudinal direction (LD) from the connecting end (11; 32) by up to 14% of the total length (L10; L30) of the first component (10; 30).

13. The damper device (40; 140) according to any one of the preceding claims, wherein, All individual dampers (42a, 42b, 42c, 42d, 42e) are passive dampers.

14. A wind turbine (1), characterized in that, The wind turbine (1) includes a damper device (40; 140) according to any one of the preceding claims.

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