CN114033623A

CN114033623A - Displacement tuning mass damper for tower of wind generating set

Info

Publication number: CN114033623A
Application number: CN202111203409.XA
Authority: CN
Inventors: 苏泽涛; 岳涛; 林胜; 胡伟辉; 刘文松; 袁鹏飞; 张志弘; 高杨; 徐志良; 刘岩; 李双虎
Original assignee: Beijing Goldwind Science and Creation Windpower Equipment Co Ltd; Zhuzhou Times New Material Technology Co Ltd
Current assignee: Beijing Goldwind Science and Creation Windpower Equipment Co Ltd; Zhuzhou Times New Material Technology Co Ltd
Priority date: 2021-10-15
Filing date: 2021-10-15
Publication date: 2022-02-11
Anticipated expiration: 2041-10-15
Also published as: CN114033623B

Abstract

The invention provides a displacement tuning mass damper for a tower of a wind generating set, which comprises the following components: the bearing support seat is used for being fixedly connected with the tower; the guide system is fixedly arranged on the bearing support seat and comprises a track distributed along the longitudinal direction and a slide block matched with the track, and the slide block can slide along the track; the mass block system is arranged on the guide system and comprises a frequency modulation mass module and a fixed mass module, and the natural frequency of the displacement tuned mass damper can be adjusted through the guide system; the damping system is distributed along the longitudinal direction, one end of the damping system is fixedly connected with the bearing support seat, and the other end of the damping system is fixedly connected with the mass block system; two groups of spring systems symmetrically arranged at the two transverse sides of the mass block system; and the limiting buffer systems are fixedly connected with the mass block system and respectively correspond to the spring brackets, and the limiting buffer systems can collide and absorb energy when the motion displacement of the mass block system reaches a limit position so as to buffer and limit the mass block system.

Description

Displacement tuning mass damper for tower of wind generating set

Technical Field

The invention belongs to the technical field of wind generating set damping, and particularly relates to a displacement tuning mass damper for a tower of a wind generating set.

Background

Wind energy is a clean and continuous energy source, and compared with the traditional energy source, wind power generation does not depend on external energy sources. Wind power generation gradually becomes an important component of the sustainable development strategy of many countries, and the development is rapid. With the development trend of large-scale international wind power market and light weight of equipment, more economic benefits can be brought by building a higher and lighter tower, but the rigidity of the tower is reduced, and the first-order frequency of the tower can be crossed by the 1P rotating speed of the unit. When the 1P rotating speed crosses the tower frequency, transverse resonance can be generated, and potential safety hazards are brought. In order to solve the problem, in the prior art, a large-displacement tuned mass damper is arranged on a rack of a wind generating set, the natural frequency of the tuned mass damper is adjusted to be consistent with or close to the shimmy frequency of the rack, the phase angles of the rack and the tuned mass damper are different when the rack and the tuned mass damper resonate, and the damping provided by the tuned mass damper is used for absorbing the resonant energy of a tower.

In the prior art, there are methods for increasing the damping of a wind turbine generator system and tuned mass dampers, the spring arrangement of the tuned mass dampers causes the tuned mass dampers to achieve the same displacement and require larger product size, and these tuned mass dampers usually adopt oil pressure dampers or friction dampers, which cannot be drawn out from the end part, have complicated structure and great replacement difficulty, and have poor damping effect.

Disclosure of Invention

In view of the technical problems mentioned above, the present invention aims to provide a displacement tuned mass damper for a wind turbine tower,

to this end, according to the invention there is provided a displacement tuned mass damper for a wind turbine tower, comprising: the bearing support seat is used for being fixedly connected with the tower; the guide system is fixedly arranged on the bearing support seat and comprises a track distributed along the longitudinal direction and a sliding block matched with the track, and the sliding block can slide along the track; the mass block system is arranged on the guide system and comprises a frequency modulation mass module and a fixed mass module arranged on the frequency modulation mass module, the frequency modulation mass module is formed by overlapping a plurality of frequency modulation mass blocks, the fixed mass module is formed by overlapping a plurality of fixed mass blocks, the frequency modulation mass module is fixedly connected with the sliding block, and the natural frequency of the displacement tuned mass damper can be adjusted by increasing or decreasing the frequency modulation mass blocks; the damping system is distributed along the longitudinal direction, one end of the damping system is fixedly connected with the bearing support seat through a first support, the other end of the damping system is fixedly connected with the mass block system through a second support, and the damping system can be pulled and pressed to deform along with the sliding of the mass block system so as to provide damping; two groups of spring systems symmetrically arranged at two lateral sides of the mass system, wherein the spring systems are configured to be capable of being pulled and pressed to deform along with the sliding of the mass system so as to buffer the mass system; the limiting buffer systems are fixedly connected with the mass block system and respectively correspond to the spring supports, and the limiting buffer systems can collide and absorb energy when the movement displacement of the mass block system reaches a limit position, so that the mass block system is buffered and limited.

In one embodiment, the guide system further comprises a bottom plate, the bottom plate is fixedly connected with the bearing support seat, and the rail is fixed on the bottom plate.

In one embodiment, a first step and a second step are respectively arranged at two transverse ends of the bottom frequency modulation mass block close to the guide system, the first step is arranged at the lower end face, the second step is arranged at the upper end face, the first step is matched with the sliding block at one transverse side, a pressing block is arranged at the transverse outer side of the second step, and the pressing block transversely presses the sliding block at the other transverse side.

In one embodiment, the damping system comprises a housing, a magnetic pole arranged in the housing, and a stretching rod, wherein a front end plate and a rear end plate are respectively arranged at two ends of the housing, a first end of the stretching rod is fixedly connected with the magnetic pole, a second end of the stretching rod penetrates through the front end plate and extends out of the housing, one end of the housing, which is provided with the rear end plate, and the second end of the stretching rod are respectively configured with a universal ball joint for connecting with the first bracket and the second bracket, and the stretching rod can pull the magnetic pole to move axially relative to the housing.

In one embodiment, the inner wall of the housing is provided with a copper sleeve, and the magnetic pole is in contact with the copper sleeve.

In one embodiment, a wear sleeve is provided between the end plate and the telescoping rod.

In one embodiment, each set of the spring systems includes two first springs distributed side by side, a first end of the first spring on the lateral outer side is fixedly connected with the mass block system through a spring support, a second end of the first spring is fixedly connected with the bearing support, a first end of the first spring on the lateral inner side is fixedly connected with the bearing support through a spring support, and a second end of the first spring is fixedly connected with the mass block system.

In one embodiment, spacing buffer system constructs including the pneumatic cylinder, sets up in the pneumatic cylinder and can follow the axial motion's of pneumatic cylinder collision pole, and the cover is established second spring on the collision pole is in with the setting the cushion of the axial outer end of collision head the free end of collision pole is equipped with the diameter and is greater than the collision head of collision pole, the second spring supports and leans on the collision head, spacing buffer system can the collision head with correspond energy-absorbing when the spring bracket collides.

In one embodiment, the limiting buffer system is fixedly connected with the frequency modulation mass module through a limiting bracket, the outer surface of the hydraulic cylinder is in a screw rod shape and is installed in a matching mode with the limiting bracket, and the initial distance between the limiting buffer system and the corresponding spring bracket can be adjusted by rotating the limiting buffer system.

In one embodiment, the limit bumper system is configured to include a damping mass disposed on the spring support and an impact mass secured to a lower end of the fm mass module, the limit bumper system being capable of absorbing energy when the impact mass collides with the damping mass.

In one embodiment, the lower end of the frequency modulation quality module is provided with right-angle areas which are transversely inwards concave at both sides, and two groups of spring systems are respectively arranged in the corresponding right-angle areas

In one embodiment, the fm mass module is provided with longitudinally inwardly extending grooves at both longitudinal ends thereof, and the first and second brackets are respectively disposed in the corresponding grooves.

In one embodiment, the middle part of the lower end of the frequency modulation mass module is reserved with an installation space extending along the longitudinal direction, and the damping system is installed in the installation space.

In one embodiment, the damping system is mounted at an upper end of the mass system.

Compared with the prior art, the method has the advantages that:

the displacement tuned mass damper can provide damping and buffering, so that the impact force on the tower caused by collision is effectively reduced. The guide system enables the mass block system to slide along a fixed direction, and the damping system can effectively absorb vibration energy, so that vibration is reduced, and damping is provided for the displacement tuning mass damper. The spring systems arranged on the two sides are matched with the weight of the mass block system at the top to increase and decrease, so that the natural frequency of the displacement tuned mass damper can be adjusted, the natural frequency of the displacement tuned mass damper is completely matched with the natural frequency of the tower of the wind generating set, and the vibration reduction and buffering performance of the displacement tuned mass damper is enhanced. The first springs in the spring system do not influence each other in the stretching process, and the arrangement mode of the first springs can ensure that each first spring realizes the maximum deformation, so that the structure of the displacement tuned mass damper is compact enough, and large deformation displacement can be realized in a limited space. The limiting buffer system can play a limiting buffer role for the displacement tuned mass damper under the limiting working condition, so that the operation limiting capacity is provided, and the vibration reduction capacity of the displacement tuned mass damper is further improved. The displacement tuning mass damper can effectively damp the tower of the wind generating set, effectively reduces impact force brought to the tower due to collision, is very favorable for enhancing the stability of the tower and is favorable for improving the safety performance.

Drawings

The invention will now be described with reference to the accompanying drawings.

FIG. 1 shows a configuration of a displacement tuned mass damper for a wind park tower according to the present invention.

Figure 2 shows the structure of the mass system in the displacement tuned mass damper shown in figure 1.

Figure 3 shows the structure of the load bearing seat in the displacement tuned mass damper of figure 1.

Figure 4 shows a mounting arrangement for a guide system mounting and load bearing support block in the displacement tuned mass damper of figure 1.

Fig. 5 shows an enlarged view of the area a in fig. 4.

Figure 6 shows the mounting arrangement between the rails and the base plate in the guide system of figure 4.

Fig. 7 and 8 show the connection between the mass system and the guiding system.

Fig. 9 shows an enlarged view of the region B in fig. 8.

Fig. 10 and 11 show the structure of the damping system in the displacement tuned mass damper of fig. 1.

Fig. 12 shows a connection structure of the universal ball joint of the end of the stretching rod and the first bracket in the damping system shown in fig. 11.

Figure 13 illustrates an installation position of an embodiment of the damping system.

Figure 14 shows the mounting position of another embodiment of the damping system.

Figure 15 shows the distribution positions of the two sets of spring systems in the displacement tuned mass damper shown in figure 1.

Fig. 16 shows the structure of each set of spring systems in fig. 15.

Figure 17 shows the distributed positions of the limiting damping system in the displacement tuned mass damper of figure 1.

Figure 18 illustrates the structure of one embodiment of a positive stop bumper system.

Fig. 19 and 20 show a specific connection relationship between the position limiting buffer system and the mass system shown in fig. 18.

Fig. 21 shows the structure of the spacing bracket of fig. 20.

Figure 22 illustrates the structure of another embodiment of a positive stop bumper system.

FIG. 23 schematically illustrates the location of a displacement tuned mass damper according to the present invention installed on an early wind turbine tower.

In the present application, the drawings are all schematic and are used only for illustrating the principles of the invention and are not drawn to scale.

Detailed Description

The invention is described below with reference to the accompanying drawings.

In this application, it should be noted that the direction indicated by X in fig. 1 is defined as a horizontal direction, the direction indicated by Y is defined as a vertical direction, and the direction indicated by Z is defined as a vertical direction. In addition, directional terms or qualifiers "up", "down", and the like used in the present application are with reference to fig. 1. They are not intended to limit the absolute positions of the parts involved, but may vary from case to case.

Furthermore, the terms "first" and "second" used herein are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

FIG. 1 shows the structure of a displacement tuned mass damper 100 for a wind turbine tower according to the present invention. As shown in fig. 1, the displacement tuned mass damper 100 includes a bearing support 1, a guide system 2 fixedly mounted on the bearing support 1, a mass system 3 mounted on the guide system 2, damping systems 4 distributed along a longitudinal direction, two sets of spring systems 5 symmetrically disposed at two lateral sides of the mass system 3, and a plurality of limit buffer systems 6. The load bearing support base 1 is used for fixed connection with a tower 200 (see fig. 23) of a wind turbine generator set, thereby fixedly mounting the displacement tuned mass damper 100 to the tower 200. The guide system 2 enables the mass system 3 to slide in a fixed direction. The damping system 4 is used for energy absorption, reducing vibration, and providing damping for the displacement tuned mass damper 100. The spring systems 5 arranged on the two sides are matched with the weight of the top mass block system 3 to increase and decrease the weight of the top mass block system 3, so that the natural frequency of the tuned mass damper 100 can be adjusted, and the natural frequency of the tuned mass damper 100 is completely matched with the natural frequency of the tower of the wind generating set. The limiting and buffering system 6 is used for enabling the tuned mass damper 100 to have a limiting and buffering function under the limiting working condition, so that the operation limiting capability is provided for the tuned mass damper 100. The displacement tuned mass damper 100 is capable of providing effective damping of the tower of the wind turbine.

As shown in fig. 2, the mass system includes a fm mass module 31 and a fixed mass module 32, and the fixed mass module 32 is disposed at an upper end of the fm mass module 31. In the embodiment shown in fig. 2, the fixed mass block 32 has a transverse length equal to the transverse length of the fm mass block 31, while the fixed mass block 32 has a longitudinal length less than the longitudinal length of the fm mass block 31, and the fixed mass block 32 is disposed in the longitudinal middle of the fm mass block 31. The frequency modulation mass module 31 is formed by overlapping a plurality of frequency modulation mass blocks, and the fixed mass module 32 is formed by overlapping a plurality of fixed mass blocks. The mass block system 3 fixedly connects a plurality of frequency modulation mass blocks and a plurality of fixed mass blocks into a whole through a plurality of fasteners. The fastener may be, for example, a stud. The natural frequency of the displacement tuned mass damper 100 can be fine tuned by increasing or decreasing the fm mass in the fm mass module 31.

According to the present invention, as shown in fig. 3, the load bearing support 1 includes a support body 11, an upper support plate 12, and a lower support plate 13. The upper supporting plate 12 is fixedly connected to the upper end of the supporting seat body 1 and used for fixedly mounting the guide system 2. The lower support plate 13 is fixedly connected to the lower end of the support base main body 1, and is used for being fixedly connected with a tower 200 of a wind generating set. The middle parts of the two transverse sides of the upper supporting plate 12 are provided with groove structures which are inwards concave along the transverse direction.

As shown in fig. 4, the guide system 2 comprises a rail 21 distributed in the longitudinal direction, a plurality of sliders 22 adapted to the rail 21, and a base plate 23. The rail 21 is fixed to a base plate 23, and a plurality of sliders 22 are slidable along the rail 21. In the embodiment shown in fig. 4, 4 sliders 22 are provided on the rail 21. The guide system 2 is fixedly connected with the upper support plate 12 of the bearing support 1 through the bottom plate 23, so that the guide system 2 is fixedly installed on the bearing support 1. The slider 22 is intended to be fixedly connected to the mass system 3, so that the mass system 3 is mounted to the guide system 2, which enables the mass system 3 to slide along the rail 21 under the action of the slider 22.

As shown in fig. 5 and 6, a mounting groove 231 is provided on the bottom plate 23 for mounting the rail 21. One side (the right side in fig. 6) of the rail 21 abuts against the side wall of the mounting groove 231, and the other side abuts against a thin round steel rod 26, and the round steel rod 26 is gradually pressed by the tapered cap of the tapered head screw 25. Thereby, the rail 21 is press-fitted by the side wall of the fitting groove 231 and the round steel bar 26. The rails 21 can be fixed by the fixing method, so that the mounting accuracy of the two rails 21 can be ensured by the machining accuracy of the mounting grooves 231, and the straightness between the linear guide rails of the rails 21 is ensured. So that it is possible to prevent an increase in sliding friction force due to an error in non-parallelism of the installation of the rail 21 when the slider 22 slides. Meanwhile, compressing the round steel rod 26 by the conical head screw 25 can increase the lateral shear capacity of the rail 21, thereby increasing the lateral load capacity of the tuned mass damper 100.

According to the invention, the mass system 3 is fixedly connected to the slide 22. As shown in fig. 7, the bottom fm mass 310 of the guide system 2 is fastened to the slider 22 by a press block 313. As shown in fig. 8 and 9, the two lateral ends of the bottom proof-mass 310 of the proof-mass module 31 abutting against the guide system 2 are respectively provided with a first step 311 and a second step 312, the first step 311 is located on the lower end face of the bottom proof-mass 310, and the second step 312 is located on the upper end face of the bottom proof-mass 310. The step surface of the first step 311 is in contact fit with the outer side surface of the sliding block 22 at one transverse side, a pressing block 313 is arranged at the transverse outer side of the second step 312, and the pressing block 313 transversely presses the sliding block 22 at the other transverse side. The press block 313 is fastened to the bottom frequency-modulated mass 310 by a fastening screw 314, and by tightening the fastening screw 314, a lateral pressure can be applied to the press block 313 to press the corresponding slider 22, and the step surface of the first step 311 can be pressed against the outer side surface of the corresponding slider 22. Thereby, the mass system 3 is brought into connection with the guide system 2. This mounting of the mass system 3 ensures the lateral shear capacity of the slider 22, further increasing the lateral load capacity of the displacement tuned mass damper 100. For convenience of description, the bottom fm mass of fm mass module 31 is referred to as bottom fm mass 310.

As shown in fig. 10, the damping system 4 is distributed in the longitudinal direction. One end (right end in fig. 10) of the damping system 4 is fixedly connected with the bearing support base 1 through a first bracket 71, and the other end (left end in fig. 10) is fixedly connected with the mass block system 3 through a second bracket 72, and the damping system 4 can be pulled and pressed to deform along with the sliding of the mass block system 3, so that damping is provided. In the embodiment shown in fig. 10, second support 72 is fixedly attached to bottom tuned mass 310 in mass system 3.

According to one embodiment of the present invention, the damping system 4 may employ an electromagnetic damper. As shown in fig. 11, the damper system 4 includes a housing 41, a magnetic pole 42 disposed inside the housing 41, and a stretching rod 43. The inner wall of the shell 41 is provided with a copper sleeve 47, the magnetic pole 42 is contacted with the copper sleeve 47, and a wear-resistant sleeve 48 is arranged between the end plate and the telescopic rod. The housing 41 is provided at both ends thereof with a front end plate 44 and a rear end plate 45, respectively. A first end (right end in fig. 11) of the stretching rod 43 is fixedly connected to the magnetic pole 42, and a second end (left end in fig. 11) of the stretching rod 43 protrudes out of the housing 41 through the front end plate 44. The end of the housing 41 provided with the rear end plate 45 and the second end of the stretching rod 43 are each formed with a ball joint 46, the end of the housing 41 being connected to the second carrier 72 via the ball joint 46, and the second end of the stretching rod 43 being connected to the first carrier 71 via the ball joint 46. The connecting member and the stretching rod 43 are able to slide with the mass system 3, pulling the pole 42 to move axially with respect to the housing 41 to provide damping. The damping system 4 has a stable damping coefficient in the operation process of the displacement tuned mass damper 100, and can effectively avoid the problem of the change of the damping coefficient caused by oil leakage. The damping system 4 can provide damping along with the sliding of the mass block system 3 to absorb energy and buffer the mass block system 3, so that the impact force on the tower caused by collision is effectively reduced.

In an embodiment not shown, the damping system 4 may also employ an oil pressure damper.

As shown in fig. 12, the ball-and-socket joint 46 at the second end of the stretching rod 43 is connected to the first bracket 71 via a connecting element 49. The connector 49 may be a bolt connector, for example. The first bracket 71 is provided with a threaded hole, and the connecting member 49 is inserted through the ball joint 46 and fitted into the threaded hole, so that the ball joint 46 of the second end of the stretching rod 43 is connected to the first bracket 71. The end ball joint 46 of the housing 41 and the second bracket 72 are also connected by a connecting member 49, and the specific connecting structure thereof is the same as that between the ball joint 46 of the second end of the stretching rod 43 and the first bracket 71. The damping system 4 adopts the connection mode of the universal ball joint 46 structure, so that the installation error can be compensated, the abrasion between the stretching rod 43 and the wear-resistant sleeve 48 is reduced, and the service life of the damping system 4 is prolonged.

According to one embodiment of the invention, as shown in fig. 13, the fm mass module 31 is provided with grooves 33 (see fig. 2) extending longitudinally inward at both longitudinal ends thereof, and the first bracket 71 and the second bracket 72 are respectively disposed in the corresponding grooves 33. The middle part of the lower end of the fm mass module 31 is reserved with a longitudinally extending installation space 34, the installation space 34 longitudinally penetrates through the fm mass module 31, and the installation space 34 is located above the bottom fm mass 310. The damper system 4 is installed in the installation space 34, and both ends of the damper system 4 extend into the grooves 33 to be connected to the first bracket 71 and the second bracket 72, respectively. The damping system 4 is thus arranged in the mass system 3 through the frequency-modulated mass module 31. This configuration of the mass system 3 not only facilitates the mounting of the first and

second brackets

71, 72, but also facilitates the maintenance and replacement of the damping system 4.

According to another embodiment of the present invention, as shown in fig. 14, both longitudinal ends of the fm mass module 31 are provided with grooves 33 (see fig. 2) extending longitudinally inward, and the first bracket 71 and the second bracket 72 are respectively disposed in the corresponding grooves 33. Also, the upper end portions of the first and

second brackets

71 and 72 each extend to an upper region of the mass system 3. Both ends of the damper system 4 are connected to the upper end portions of the first bracket 71 and the second bracket 72, respectively. Thereby, the damping system 4 is arranged above the mass system 3.

According to the invention, the two sets of spring systems 5 are arranged symmetrically on both lateral sides of the mass system 3 and in the lower end region of the mass system 3. As shown in fig. 13, the two lateral sides of the lower end of the fm quality module 31 are provided with inwardly concave right-angle regions 35. The spring system 5 is correspondingly arranged in the right-angled region 35 (see fig. 1).

As shown in fig. 15, the two sets of spring systems 5 are distributed along the longitudinal extension on both lateral sides of the guiding system 2. Each set of spring systems 5 comprises two first springs 51. The first spring 51 may be a steel spring, for example. The spring system 5 is able to deform in tension and compression as the mass system 3 slides. The two first springs 51 in each set of spring systems 5 are distributed laterally side by side. One end (left end in fig. 15) of the first spring 51 on the lateral outer side in each set of spring system 5 is fixedly connected with the load bearing support 1 through a spring support 52 and is kept still, and the other end (right end in fig. 15) is fixedly connected with the mass system 3 through the spring support 52. And one end (left end in fig. 15) of the first spring 51 at the transverse inner side in each group of spring systems 5 is fixedly connected with the mass system 3 through a spring support 52 and is kept still, and the other end (right end in fig. 15) is fixedly connected with the bearing support seat 1 through the spring support 52. Fig. 16 schematically shows the mounting principle of the first spring 51 in a set of spring systems 5. The first springs 51 are not affected each other in the stretching process, and the arrangement mode of the first springs 51 can ensure that the maximum deformation of each first spring 51 is realized, so that the structure of the displacement tuned mass damper 100 is compact enough, and the operation displacement of the displacement tuned mass damper is large. This staggered, independently deformed arrangement of the spring system 5 effectively ensures that the first spring 51 can achieve a large deformation displacement in a limited space.

In one embodiment, the spring support 52 is configured as a right angle web. The spring support 52 connected with the load bearing support 1 is fixedly connected to the upper support plate 12 of the load bearing support 1 through screws, and the spring support 52 connected with the mass system 3 is fixedly connected to the lower part of the mass system 3 through screws.

According to the present invention, the first springs 51 are all tension springs. In the initial depressed state, the first springs 51 are each in a pre-tensioned mounted state, the amount of pre-tensioning of which is not less than half of the maximum stroke. In this way, when the mass system 3 slides, all the first springs 51 are always in the stretched state and can automatically return to the equilibrium position, thereby effectively ensuring the motion smoothness of the mass system 3. The two ends of the first spring 51 are connected with the corresponding spring bracket 52 by adopting a threaded joint, nuts are respectively arranged on the two sides of the spring bracket 52, and the stretching amount of the first spring 51 is finely adjusted by adjusting the positions of the inner nuts, so that the first spring 51 is prevented from loosening. At the same time, the equilibrium position of the mass system 3 on the rail 21 of the guide system 2 can also be finely adjusted by adjusting the inner nut, so that the final equilibrium position of the mass system 3 on the guide system 2 is adjusted. The spring system 5 can be stretched or compressed along with the sliding of the mass system 3, so as to absorb energy, buffer the mass system 3 and further reduce the impact force on the tower caused by collision.

According to the invention, a plurality of limiting buffer systems 6 are symmetrically distributed on the two transverse sides of the guide system 2, the limiting buffer systems 6 are fixedly connected to the lower end of the mass block system 3, and the limiting buffer systems 6 are positioned right above the spring system 5. As shown in fig. 17, two limit buffer systems 6 are respectively disposed on both lateral sides of the guide system 2, and each limit buffer system 6 corresponds to a corresponding spring support 52, so that the guide system has a limit buffer function in both directions, and can realize a bidirectional limit. The limiting buffer system 6 can collide with the corresponding spring bracket 52 when the movement displacement of the mass block system 3 reaches the limit position, thereby forming limiting buffer for the mass block system 3.

According to one embodiment of the invention, the limiting buffer system 6 adopts an oil pressure type buffer to absorb energy, so that collision energy is more stable, and the impact on the tower can be effectively reduced. As shown in fig. 18, the position limiting buffer system 6 includes a hydraulic cylinder 61, a collision bar 62, and a second spring 63 fitted over the collision bar 62. The second spring 63 may be, for example, a steel spring. The impact rod 62 is disposed inside the hydraulic cylinder 61, and the free end (left end in fig. 18) of the impact rod 62 protrudes out of the hydraulic cylinder 61, the impact rod 62 being able to move axially along the hydraulic cylinder 61. An impact head 64 is provided at the free end of the impact rod 62, the impact head 64 has a diameter larger than that of the impact rod 62, and the second spring 63 abuts against the axially inner end surface of the impact head 64. The axially outer end of the impact head 64 is provided with an elastic pad 65. In one embodiment, the resilient pad 65 is fixedly attached to the impact head 64 by screws. The elastic pad 65 can increase the collision damping of the cushion system 6, thereby improving the vibration damping capacity of the cushion system 6. The limit cushioning system 6 can absorb energy when the collision head 64 collides with the corresponding spring bracket 52, so as to play a role of limit cushioning.

As shown in fig. 19 and 20, the position limiting buffer systems 6 are fixedly connected with the fm mass module 31 of the mass system 3 through position limiting brackets 66, and the collision head 64 of each position limiting buffer system 6 is opposite to the spring bracket 52 at the corresponding end. The limiting bracket 66 is fixedly connected to the lower end face of the frequency modulation mass module 31. The outer surface of the hydraulic cylinder 61 is externally threaded so as to be configured in a screw shape and fitted with the limit bracket 66, and the initial distance between the collision head 64 and the corresponding spring bracket 52 can be finely adjusted by rotating the limit bumper system 6.

As shown in fig. 20, two protruding mounting portions 313 are disposed on the lower end surface of the fm mass module 31 where the limiting buffer system 6 is correspondingly disposed, and the protruding mounting portions 313 are longitudinally spaced apart from each other, and a locking groove 314 is disposed at the bottom of the protruding mounting portions 313. The limiting bracket 66 is plate-shaped, and the limiting bracket 66 is installed in the clamping groove 314 in an adaptive manner and is fixedly connected with the protrusion installation part 313 through a fastening screw 663. As shown in fig. 21, the middle of the position limiting bracket 66 is provided with a threaded hole 662 for adapting and installing the position limiting buffer system 6. The spacing bracket 66 is provided with a slot 661 extending radially of the threaded bore 662 such that the threaded bore 662 of the spacing bracket 66 forms a slotted configuration. During installation, the spacing cushion system 6 is first inserted through the threaded holes 662 of the spacing bracket 66 in sequence, and the external threads of the hydraulic cylinder 61 are engaged with the threaded holes 662. Then, the limit bracket 66 is fitted into the notch 314, and the limit bracket 66 is fixedly connected to the protrusion mounting portion 313 by the fastening screw 663. The initial distance between the impact head 64 and the corresponding spring bracket 52 is then fine tuned by rotating the positive stop bumper system 6. After the distance adjustment is completed, the fastening screws 663 are further tightened to fix the limit bracket 66 to the mass block system 3, and at the same time, the fastening screws 663 compress the clamping grooves 314 to tighten the threaded holes 662 to fasten the limit buffers 61.

In the working process, the limiting buffer system 6 moves along with the mass block system 3, the spring supports 52 are used as collision points, when the collision head 64 is in contact collision with the corresponding spring supports 52, the second spring 63 and the hydraulic cylinder 61 work simultaneously and begin to absorb energy, and the limiting buffer system 6 can reduce the instantaneous collision energy by compressing the second spring 63 and stably absorbing energy by the hydraulic cylinder, so that the impact force brought to the tower by collision can be effectively reduced. The second spring 63 ensures that the impact head 64 is quickly returned to the initial position after leaving the spring bracket 52.

According to another embodiment of the present invention, as shown in fig. 22, the limit bumper system 6 is configured to include a damper mass 261 provided on the spring holder 52, and an impact mass 262 fixed to the lower end of the fm mass module 31, the impact mass 262 and the damper mass 261 on the respective spring holders 52 being diametrically opposed. The damping block 261 may be made of, for example, a polymer material. The damping block 261 can significantly increase the impact damping. The positive displacement bumper system 6 is capable of absorbing energy when the impact mass 262 collides in contact with the damping mass 261.

In the working process, the collision block 262 moves along with the mass block system 3, and after the collision block 262 is contacted and collided with the damping block 261 on the corresponding spring support 52, the collision block 262 and the damping block 261 absorb energy and buffer, so that the limiting and buffering function is realized, and the impact force brought to the tower by collision can be effectively reduced.

The tuned mass damper 100 according to the present invention provides damping and cushioning to effectively reduce the impact force on the tower due to a collision. The guide system 2 enables the mass system 3 to slide in a fixed direction and the damping system 4 to efficiently absorb vibrational energy, thereby reducing vibration and providing damping for the displacement tuned mass damper 100. The spring systems 5 arranged on the two sides are matched with the weight of the top mass block system 3 to increase and decrease the weight of the top mass block system 3, so that the natural frequency of the tuned mass damper 100 can be adjusted, the natural frequency of the tuned mass damper 100 is completely matched with the natural frequency of the tower of the wind generating set, and the vibration reduction and buffering performance of the tuned mass damper 100 can be enhanced. The first springs 51 in the spring system 5 do not affect each other in the stretching process, and the arrangement of the first springs 51 can ensure that each first spring 51 realizes the maximum deformation, so that the structure of the tuned mass damper 100 is compact enough, and can realize large deformation displacement in a limited space. The limiting buffer system 6 can play a limiting buffer role for the tuned mass damper 100 under the limiting working condition, so that the operation limiting capacity is provided, and the vibration reduction capacity of the tuned mass damper 100 is further improved. The displacement tuned mass damper 100 can effectively damp the tower of the wind generating set, effectively reduce the impact force brought to the tower due to collision, and is very favorable for enhancing the stability of the tower and improving the safety performance.

Finally, it should be noted that the above-mentioned embodiments are only preferred embodiments of the present invention, and do not limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing examples, or that equivalents may be substituted for elements thereof. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A displacement tuned mass damper for a wind turbine tower, comprising:

the bearing support seat (1) is fixedly connected with the tower;

a guide system (2) fixedly mounted on the bearing support seat and comprising a rail (21) distributed along the longitudinal direction and a slide block (22) matched with the rail, wherein the slide block can slide along the rail;

the mass block system (3) is installed on the guide system and comprises a frequency modulation mass module (31) and a fixed mass module (32) arranged on the frequency modulation mass module, the frequency modulation mass module is formed by overlapping a plurality of frequency modulation mass blocks, the fixed mass module is formed by overlapping a plurality of fixed mass blocks, the frequency modulation mass module is fixedly connected with the sliding block, and the natural frequency of the displacement tuned mass damper can be adjusted by increasing or decreasing the frequency modulation mass blocks;

the damping systems (4) are distributed along the longitudinal direction, one end of each damping system is fixedly connected with the bearing support seat through a first support (71), the other end of each damping system is fixedly connected with the mass block system through a second support (72), and the damping systems can be pulled and pressed to deform along with the sliding of the mass block systems so as to provide damping;

two groups of spring systems (5) symmetrically arranged at two lateral sides of the mass system, wherein the spring systems are configured to be capable of tensile and compressive deformation along with the sliding of the mass system so as to buffer the mass system;

the limiting buffer systems (6) are fixedly connected with the mass block system and respectively correspond to the spring brackets, and the limiting buffer systems can collide and absorb energy when the movement displacement of the mass block system reaches a limit position, so that the mass block system is buffered and limited.

2. The displacement tuned mass damper according to claim 1, wherein said guide system further comprises a base plate (23) fixedly connected to said load bearing support, said rail being fixed to said base plate.

3. Displacement tuned mass damper according to claim 1 or 2, characterized in that a first step (311) at a lower end face and a second step (312) at an upper end face are provided next to the lateral ends of the bottom tuned mass (310) of the guide system,

the first step is matched with the sliding block on one transverse side, a pressing block (313) is arranged on the transverse outer side of the second step, and the pressing block transversely presses the sliding block on the other transverse side.

4. Displacement tuned mass damper according to claim 1, characterized in that said damping system comprises a housing (41) provided at its two ends with a front end plate (44) and a rear end plate (45), respectively, a magnetic pole (42) and a stretching rod (43) arranged inside said housing, said stretching rod being fixedly connected at its first end to said magnetic pole and extending at its second end out of said housing through said front end plate,

the end of the shell provided with the rear end plate and the second end of the stretching rod are respectively provided with a universal ball joint (46) which is respectively used for connecting the first bracket and the second bracket, and the stretching rod can pull the magnetic pole to move axially relative to the shell.

5. Displacement tuned mass damper according to claim 4, characterized in that the inner wall of the housing is provided with a copper sleeve (47), the poles being in contact with the copper sleeve.

6. Displacement tuned mass damper according to claim 4 or 5, characterized in that a wear sleeve (48) is provided between the aforementioned end plate and the telescopic rod.

7. Displacement tuned mass damper according to claim 1, characterized in that each set of said spring systems comprises two first springs (51) distributed side by side,

the first end of the first spring at the transverse outer side is fixedly connected with the mass block system through a spring bracket (52), the second end is fixedly connected with the bearing support seat,

the first end of the first spring on the transverse inner side is fixedly connected with the bearing support seat through a spring support (52), and the second end of the first spring is fixedly connected with the mass block system.

8. The displacement tuned mass damper according to claim 7, wherein the limit cushion system is configured to comprise a hydraulic cylinder (61), a crash bar (62) disposed within the hydraulic cylinder and movable in the axial direction of the hydraulic cylinder, and a second spring (63) fitted over the crash bar and an elastic pad (65) disposed at the axially outer end of the crash head,

the free end of the collision rod is provided with a collision head (64) with a diameter larger than that of the collision rod, the second spring abuts against the collision head, and the limiting buffer system can absorb energy when the collision head collides with the corresponding spring support.

9. The displacement tuned mass damper according to claim 8, wherein the position limiting damping system is fixedly connected to the fm mass module by a position limiting bracket (66), the outer surface of the hydraulic cylinder is configured in the shape of a screw and is mounted to fit the position limiting bracket, and the initial distance between the position limiting damping system and the corresponding spring bracket can be adjusted by rotating the position limiting damping system.

10. The displacement tuned mass damper according to claim 7, wherein the positive displacement damping system is configured to include a damping mass (261) disposed on the spring mount and an impact mass (262) secured to a lower end of the fm mass module, the positive displacement damping system being capable of absorbing energy when the impact mass collides with the damping mass.

11. Displacement tuned mass damper according to claim 1 or 7, characterised in that at both lateral sides of the lower end of said FM mass module are provided laterally inwardly concave right angle areas (35), two sets of said spring systems being arranged in respective said right angle areas.

12. Displacement tuned mass damper according to claim 1, characterized in that longitudinally inwardly extending grooves (33) are provided at both longitudinal ends of the FM mass module, said first bracket and said second bracket being arranged in respective said grooves.

13. The displacement tuned mass damper according to claim 12, wherein a longitudinally extending mounting space (34) is reserved in the middle of the lower end of the fm mass module, the damping system being mounted in said mounting space.

14. The displacement tuned mass damper according to claim 12, wherein said damping system is mounted at an upper end of said mass system.