CN114033623B - Displacement tuning mass damper for wind generating set tower - Google Patents

Abstract

The application provides a displacement tuning mass damper for a wind generating set 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 rails distributed along the longitudinal direction and sliding blocks matched with the rails, and the sliding blocks can slide along the rails; 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 tuning mass damper can be adjusted through the guide system; damping systems distributed along the longitudinal direction, wherein one end of each damping system is fixedly connected with the bearing support seat, and the other end of each damping system is fixedly connected with the mass block system; two groups of spring systems symmetrically arranged on two lateral sides of the mass block system; the limiting buffer systems are fixedly connected with the mass block system, correspond to the spring brackets respectively, and can absorb energy in a collision manner when the movement displacement of the mass block system reaches the limit position so as to form buffering limit for the mass block system.

Description

Displacement tuning mass damper for wind generating set tower

Technical Field

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

Background

Wind energy is a clean perpetual 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 sustainable development strategies in many countries, and development is rapid. Along with the development trend of large-scale and light-weight equipment of the international wind power market, more economic benefits can be brought by constructing a higher and lighter tower, but the rigidity of the tower can be reduced, and the rotating speed of the unit 1P can possibly span the first-order frequency of the tower. Transverse resonance occurs when the 1P rotational speed crosses the tower frequency, bringing a potential safety hazard. In order to solve the problem, in the prior art, a large-displacement tuned mass damper is arranged on a stand of a wind generating set, the natural frequency of the tuned mass damper is adjusted to be consistent with or similar to the shimmy frequency of the stand, the phase angles of the stand and the tuned mass damper are different, and the damping provided by the tuned mass damper is used for absorbing the resonance energy of a tower.

In the prior art, there are a method for increasing damping of a wind generating set system and a tuning mass damper, wherein the spring arrangement mode of the tuning mass damper causes that the same displacement is realized, and the tuning mass damper needs larger product size, and usually adopts an oil pressure damper or a friction damper, which cannot be extracted from an end part, has complex structure, high replacement difficulty and poor damping effect.

Disclosure of Invention

Aiming at the technical problems, the application aims to provide a displacement tuning mass damper for a tower of a wind generating set.

To this end, according to the application 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, wherein the frequency modulation mass module is formed by superposing a plurality of frequency modulation mass blocks, the fixed mass module is formed by superposing 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 tuning 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 bracket, the other end of the damping system is fixedly connected with the mass block system through a second bracket, and the damping system can be pulled, pressed and deformed along with the sliding of the mass block system, so that damping is provided; two sets of spring systems symmetrically disposed on both lateral sides of the mass system, the spring systems being configured to be capable of tensile and compressive deformation as the mass system slides, thereby cushioning the mass system; the limiting buffer systems are fixedly connected with the mass block system, correspond to the spring brackets respectively, and can collide and absorb energy when the movement displacement of the mass block system reaches the limit position, so that buffering and limiting are formed for the mass block system.

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

In one embodiment, a first step and a second step are respectively arranged at the two lateral ends of the bottom frequency modulation mass block close to the guide system, the first step is positioned on the lower end face, the second step is positioned on the upper end face, the first step is matched with the sliding block positioned on one lateral side, a pressing block is arranged on the lateral outer side of the second step, and the pressing block is laterally pressed against the sliding block positioned on the other lateral 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 stretches out of the housing, one end of the housing, which is provided with the rear end plate, and a second end of the stretching rod are respectively provided with a universal ball joint, and are respectively connected with the first bracket and the second bracket, and the stretching rod can pull the magnetic pole to axially move 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 tension rod.

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

In one embodiment, the limit buffer system is configured to include a hydraulic cylinder, an impact rod which is arranged in the hydraulic cylinder and can move along the axial direction of the hydraulic cylinder, an impact head which is arranged at the free end of the impact rod and has a diameter larger than that of the impact rod, a second spring which is sleeved on the impact rod and is abutted against the impact head, and an elastic pad which is arranged at the axial outer end of the impact head, wherein the limit buffer system can absorb energy when the impact head collides with the corresponding spring bracket.

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

In one embodiment, the limit buffer system is configured to comprise a damping block arranged on the spring bracket and an impact block fixed at the lower end of the frequency modulation mass module, and the limit buffer system can absorb energy when the impact block collides with the damping block.

In one embodiment, two transverse sides of the lower end of the frequency modulation mass module are provided with transverse inward right-angle areas, and two groups of spring systems are respectively arranged in the corresponding right-angle areas.

In one embodiment, grooves extending longitudinally inwards are arranged at two longitudinal ends of the frequency modulation mass module, and the first bracket and the second bracket are respectively arranged in the corresponding grooves.

In one embodiment, a mounting space extending along the longitudinal direction is reserved in the middle of the lower end of the frequency modulation mass module, and the damping system is mounted in the mounting space.

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

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

the displacement tuning mass damper can provide damping and buffering, so that impact force on the tower due to collision is effectively reduced. The guide system can enable 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 top mass block system, so that the natural frequency of the displacement tuning mass damper can be adjusted, the natural frequency of the displacement tuning 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 tuning mass damper is enhanced. The first springs in the spring system are not mutually influenced 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 tuning mass damper is compact enough, and large deformation displacement can be realized in a limited space. The limiting buffer system can play a role in limiting and buffering for the displacement tuning mass damper under the limiting working condition, so that the operation limiting capacity is provided, and the vibration reduction capacity of the displacement tuning mass damper is further improved. The displacement tuning mass damper can effectively damp the tower of the wind generating set, effectively reduce the impact force on the tower caused by collision, and is very beneficial to enhancing the stability of the tower and improving the safety performance.

Drawings

The present application will be described below with reference to the accompanying drawings.

Fig. 1 shows the structure of a displacement tuned mass damper for a wind park tower according to the application.

Fig. 2 shows the structure of a mass system in the displacement tuned mass damper of fig. 1.

Fig. 3 shows the structure of the load bearing support in the displacement tuned mass damper of fig. 1.

Fig. 4 shows a mounting structure of a guide system mounting and carrying support in the displacement tuned mass damper of fig. 1.

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

Fig. 6 shows the mounting structure between the rail and the base plate in the guide system of fig. 4.

Fig. 7 and 8 show the connection structure between the mass system and the guide system.

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

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

FIG. 12 illustrates the connection of the universal ball joint at the end of the tension rod to the first bracket in the damping system of FIG. 11.

Fig. 13 shows the mounting position of one embodiment of the damping system.

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

Fig. 15 shows the distributed positions of two sets of spring systems in the displacement tuned mass damper of fig. 1.

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

Fig. 17 shows the distributed positions of the limit bumper system in the displacement tuned mass damper of fig. 1.

Fig. 18 shows the structure of one embodiment of the limit bumper system.

Fig. 19 and 20 show specific connection relationships between the limit bumper system and the mass system of fig. 18.

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

Fig. 22 shows the structure of another embodiment of the limit bumper system.

Fig. 23 schematically shows the position on the tower of a wind park where a displacement tuned mass damper is mounted according to the application.

In the present application, all of the figures are schematic drawings which are intended to illustrate the principles of the application only and are not to scale.

Detailed Description

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

In the present application, the direction indicated by X in fig. 1 is defined as a lateral direction, the direction indicated by Y is defined as a longitudinal direction, and the direction indicated by Z is defined as a vertical direction. The directional terms or qualifiers "upper", "lower", and the like used in the present application are used with reference to fig. 1. They are not intended to limit the absolute position of the parts involved, but may vary according to the specific circumstances.

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

Fig. 1 shows the structure of a displacement tuned mass damper 100 for a wind park tower according to the present application. As shown in fig. 1, the displacement tuning mass damper 100 includes a load bearing support base 1, a guide system 2 fixedly mounted on the load bearing support base 1, a mass system 3 mounted on the guide system 2, damping systems 4 distributed in a longitudinal direction, two sets of spring systems 5 symmetrically disposed on both lateral sides of the mass system 3, and a plurality of limit cushioning systems 6. The load bearing support base 1 is adapted to be fixedly connected to a tower 200 (see fig. 23) of a wind power plant, thereby fixedly mounting the displacement tuned mass damper 100 to the tower 200. The guiding system 2 enables the mass system 3 to slide in a fixed direction. Damping system 4 is used for energy absorption, reducing vibrations, and providing damping for displacement tuned mass damper 100. The spring systems 5 arranged on the two sides are matched with increasing and decreasing the weight of the top mass block system 3, so that the natural frequency of the displacement tuning mass damper 100 can be adjusted, and the natural frequency of the displacement tuning mass damper 100 is completely matched with the natural frequency of the tower of the wind generating set. The limit buffer system 6 is used for enabling the displacement tuning mass damper 100 to have a limit buffer function under a limit working condition, so as to provide operation limiting capability for the displacement tuning mass damper 100. The displacement tuned mass damper 100 is capable of providing effective damping of the tower of a wind turbine.

As shown in fig. 2, the mass system includes a frequency modulation mass module 31 and a fixed mass module 32, and the fixed mass module 32 is disposed at an upper end of the frequency modulation mass module 31. In the embodiment shown in fig. 2, the lateral length of the fixed mass module 32 is equal to the lateral length of the tuning mass module 31, and the longitudinal length of the fixed mass module 32 is smaller than the longitudinal length of the tuning mass module 31, and the fixed mass module 32 is disposed in the longitudinal middle of the tuning mass module 31. The tuning mass module 31 is formed by overlapping a plurality of tuning mass blocks, and the fixed mass module 32 is formed by overlapping a plurality of fixed mass blocks. The mass block system 3 enables a plurality of frequency modulation mass blocks and a plurality of fixed mass blocks to be fixedly connected 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 tuning mass in the tuning mass module 31.

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

As shown in fig. 4, the guiding system 2 comprises a rail 21 distributed in the longitudinal direction, a plurality of sliders 22 fitting the rail 21, and a bottom plate 23. The rail 21 is fixed to the bottom 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 guiding system 2 is fixedly connected with the upper support plate 12 of the bearing support seat 1 through the bottom plate 23, so that the guiding system 2 is fixedly mounted on the bearing support seat 1. The slide 22 is adapted 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 track 21 under the influence of the slide 22.

As shown in fig. 5 and 6, a mounting groove 231 for mounting the rail 21 is provided on the bottom plate 23. One side (right side in fig. 6) of the rail 21 is abutted against the side wall of the mounting groove 231, and the other side is abutted against a thin round steel bar 26, and the round steel bar 26 is gradually compressed by the tapered cap of the taper head screw 25. Thereby, a press fit is formed to the rail 21 by the side wall of the mounting groove 231 and the round bar 26. The rails 21 can ensure the mounting accuracy of the two rails 21 by the processing accuracy of the mounting groove 231 in such a fixing manner, and the straightness between the linear guide rails of the rails 21 is ensured. So that an increase in sliding friction force of the slider 22 due to an error in mounting non-parallelism of the rail 21 at the time of sliding can be avoided. Meanwhile, the conical head screw 25 is used for pressing the round steel rod 26, so that the transverse shearing capacity of the track 21 can be increased, and the transverse bearing capacity of the displacement tuning mass damper 100 is increased.

According to the application, the mass system 3 is fixedly connected to the slide 22. As shown in fig. 7, the bottom frequency-modulated mass 310 of the guiding system 2 is fastened to the slide 22 by means of a press 313. As shown in fig. 8 and 9, the two lateral ends of the bottom tuning mass 310 of the tuning mass module 31, which is close to the guiding system 2, are respectively provided with a first step 311 and a second step 312, wherein the first step 311 is located at the lower end surface of the bottom tuning mass 310, and the second step 312 is located at the upper end surface of the bottom tuning mass 310. The step surface of the first step 311 is in contact fit with the outer side surface of the slider 22 on one lateral side, and a pressing block 313 is arranged on the lateral outer side of the second step 312, and the pressing block 313 laterally presses the slider 22 on the other lateral side. The pressing block 313 is fastened to the bottom frequency modulation mass 310 by a fastening screw 314, and by tightening the fastening screw 314, a lateral pressure can be applied to the pressing block 313 to press the corresponding slider 22, and at the same time, 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 connected to the guiding system 2. This mounting of the mass system 3 ensures lateral shear capability of the slider 22, further increasing the lateral load carrying capability of the displacement tuned mass damper 100. For convenience of description herein, a bottom block of the proof mass 31 will be referred to as a bottom proof 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 seat 1 through a first bracket 71, the other end (left end in fig. 10) is fixedly connected with the mass system 3 through a second bracket 72, and the damping system 4 can slide along with the mass system 3 to be deformed in a pulling and pressing manner, so that damping is provided. In the embodiment shown in fig. 10, the second bracket 72 is fixedly connected to a bottom frequency modulation mass 310 in the mass system 3.

According to one embodiment of the application, the damping system 4 may employ an electromagnetic damper. As shown in fig. 11, the damping system 4 includes a housing 41, a magnetic pole 42 provided in the housing 41, and a tension rod 43. A copper sleeve 47 is provided on the inner wall of the housing 41, the magnetic poles 42 are in contact with the copper sleeve 47, and a wear-resistant sleeve 48 is provided between the end plate and the tension rod. The housing 41 is provided at both ends 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 tension rod 43 are respectively configured with a universal ball joint 46, the end of the housing 41 is connected with the second bracket 72 through the universal ball joint 46, and the second end of the tension rod 43 is connected with the first bracket 71 through the universal ball joint 46. The connector and stretching rod 43 can slide with the mass system 3, pulling the magnetic pole 42 to move axially relative to the housing 41 to provide damping. The damping system 4 has stable damping coefficient in the operation process of the displacement tuning mass damper 100, and can effectively avoid the problem of damping coefficient change caused by oil leakage. The damping system 4 is capable of providing damping as the mass system 3 slides to absorb energy and to cushion the mass system 3, thereby effectively reducing the impact force on the tower due to collisions.

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

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

According to one embodiment of the application, as shown in fig. 13, the fm mass module 31 is provided with longitudinally inwardly extending grooves 33 at both longitudinal ends (see fig. 2), and the first and second brackets 71 and 72 are respectively arranged in the corresponding grooves 33. The middle part of the lower end of the frequency modulation mass module 31 is reserved with a longitudinally extending installation space 34, the installation space 34 longitudinally penetrates through the frequency modulation mass module 31, and the installation space 34 is positioned above the bottom frequency modulation mass block 310. The damping system 4 is installed in the installation space 34, and both ends of the damping system 4 extend into the grooves 33 to be connected with the first bracket 71 and the second bracket 72, respectively. Thereby, the damping system 4 is arranged in the mass system 3 through the tuned mass module 31. This construction of the mass system 3 not only facilitates the installation of the first bracket 71 and the second bracket 72, but also facilitates the maintenance and replacement of the damping system 4.

According to another embodiment of the application, as shown in fig. 14, the fm mass module 31 is provided with longitudinally inwardly extending grooves 33 at both longitudinal ends (see fig. 2), and the first and second brackets 71 and 72 are respectively arranged in the corresponding grooves 33. And, the upper end portions of the first bracket 71 and the second bracket 72 each extend to an upper region of the mass system 3. Both ends of the damping system 4 are connected to 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 application, 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 lower end of the tuning mass module 31 is provided with right angle areas 35 recessed inward on both lateral sides. The spring system 5 is correspondingly arranged in the right-angled region 35 (see fig. 1).

As shown in fig. 15, both 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, for example, a steel spring. The spring system 5 is capable of deforming in tension and compression as the mass system 3 slides. The two first springs 51 of each set of spring systems 5 are laterally arranged side by side. One end (left end in fig. 15) of the first spring 51 on the lateral outside in each group of spring systems 5 is fixedly connected with the load-bearing support base 1 through a spring bracket 52 and kept stationary, and the other end (right end in fig. 15) is fixedly connected with the mass system 3 through the spring bracket 52. While one end (left end in fig. 15) of the first spring 51 on the inner side in the lateral direction in each group of spring systems 5 is fixedly connected to the mass system 3 via a spring bracket 52 and kept stationary, and the other end (right end in fig. 15) is fixedly connected to the load-bearing support base 1 via a spring bracket 52. Fig. 16 schematically shows the principle of installation of the first springs 51 in a set of spring systems 5. The first springs 51 do not affect each other in the stretching process, and the arrangement mode of the first springs 51 can ensure that each first spring 51 realizes the maximum deformation, so that the structure of the displacement tuning mass damper 100 is compact enough, and the operation displacement of the displacement tuning mass damper is ensured to be large. This mutual staggering of the spring system 5, the arrangement of the independent deformations effectively ensures that the first springs 51 can achieve a very large deformation displacement in a limited space.

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

According to the present application, the first springs 51 are all tension springs. In the initial pressing state, the first springs 51 are each in a pretensioned mounting state, the pretensioning amount 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 a stretched state and can automatically return to the balance position, so that the motion stability of the mass system 3 is effectively ensured. The two ends of the first spring 51 are connected with the corresponding spring brackets 52 by adopting threaded joints, nuts are respectively arranged on the two sides of the spring brackets 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 balance position of the mass system 3 on the rail 21 of the guide system 2 can also be fine-tuned by adjusting the inner nuts, so that the final balance position of the mass system 3 on the guide system 2 is adjusted. The spring system 5 can be stretched or compressed as the mass system 3 slides, thereby absorbing energy, cushioning the mass system 3, further reducing the impact force on the tower due to the collision.

According to the application, a plurality of limit buffer systems 6 are symmetrically distributed on two lateral sides of the guide system 2, and the limit buffer systems 6 are fixedly connected to the lower end of the mass block system 3, and the limit buffer systems 6 are positioned right above the spring system 5. As shown in fig. 17, two limit buffer systems 6 are respectively provided on both lateral sides of the guide system 2, and each limit buffer system 6 corresponds to a corresponding spring bracket 52, so that the two-way limit buffer function is provided in both directions, and two-way limit can be realized. The limit buffer system 6 is capable of colliding with the corresponding spring support 52 when the movement displacement of the mass system 3 reaches the limit position, thereby forming limit buffer for the mass system 3.

According to one embodiment of the application, the limit buffer system 6 adopts an oil pressure type buffer to absorb energy, so that collision energy is more stable, and impact on a tower can be effectively reduced. As shown in fig. 18, the limit bumper system 6 includes a hydraulic cylinder 61, a striker rod 62, and a second spring 63 sleeved on the striker rod 62. The second spring 63 may be, for example, a steel spring. The impact rod 62 is disposed within the hydraulic cylinder 61, and a free end (left end in fig. 18) of the impact rod 62 protrudes out of the hydraulic cylinder 61, and the impact rod 62 is movable in the axial direction of the hydraulic cylinder 61. At the free end of the impact rod 62, an impact head 64 is provided, the diameter of the impact head 64 being larger than the diameter of the impact rod 62, and a second spring 63 abuts against the axially inner end face 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 limit bumper system 6, thereby improving the vibration damping capability of the limit bumper system 6. The limit bumper system 6 is capable of absorbing energy when the impact head 64 collides with the corresponding spring bracket 52 to perform the function of limit bumper.

As shown in fig. 19 and 20, the limit buffer systems 6 are fixedly connected with the fm mass module 31 of the mass system 3 through limit brackets 66, and the collision heads 64 of the limit buffer systems 6 face the spring brackets 52 of the respective ends. The limit bracket 66 is fixedly connected to the lower end surface of the frequency modulation mass module 31. The outer surface of the hydraulic cylinder 61 is provided with an external thread so as to be constructed in a screw shape and is fitted with a limit bracket 66, and the rotational limit buffer system 6 is capable of fine-tuning the initial distance between the impact head 64 and the corresponding spring bracket 52.

As shown in fig. 20, two protruding mounting portions 313 are arranged on the lower end face of the frequency modulation mass module 31, which is correspondingly provided with the limit buffer system 6, and the bottoms of the protruding mounting portions 313 are provided with clamping grooves 314. The limiting bracket 66 is plate-shaped, and the limiting bracket 66 is adaptively installed in the clamping groove 314 and is fixedly connected with the protruding installation part 313 through the fastening screw 663. As shown in fig. 21, a threaded hole 662 is provided in the middle of the limit bracket 66 for the fit-on of the limit bumper system 6. The stopper bracket 66 is provided with a slot 661 extending radially along the screw hole 662, so that the screw hole 662 of the stopper bracket 66 forms a slotted structure. In the mounting, the limit buffer system 6 is first sequentially passed through the screw holes 662 of the limit bracket 66, and the external screw threads of the hydraulic cylinder 61 are engaged with the screw holes 662. After that, the limit bracket 66 is fitted into the clamping groove 314, and the limit bracket 66 is fixedly connected with the boss mounting portion 313 by the fastening screw 663. Thereafter, the initial distance between the impact head 64 and the corresponding spring bracket 52 is fine-tuned by rotating the limit bumper system 6. After the distance adjustment is completed, the fastening screw 663 is further tightened to fix the limit bracket 66 to the mass system 3, and at the same time, the fastening screw 663 compresses the clamping groove 314 to tighten the screw hole 662 to fasten the limit bumper 61.

In the working process, the limit buffer system 6 moves along with the mass block system 3, the spring bracket 52 is used as a collision point, after the collision head 64 contacts with the corresponding spring bracket 52, the second spring 63 and the hydraulic cylinder 61 work simultaneously and begin to absorb energy, and the limit buffer system 6 can reduce instant collision energy by compressing the second spring 63 and the hydraulic cylinder to absorb energy steadily, so that the impact force caused by collision to the tower can be effectively reduced. The second spring 63 ensures that the impact head 64 returns to the initial position quickly after leaving the spring bracket 52.

According to another embodiment of the present application, as shown in fig. 22, the limit bumper system 6 is configured to include a damper block 261 provided on the spring bracket 52, and a collision block 262 fixed to the lower end of the tuned mass module 31, the collision block 262 being forward-facing the damper block 261 on the corresponding spring bracket 52. The damping block 261 can be made of a polymer material, for example. The damping mass 261 can significantly increase the crash damping. The limit bumper system 6 is capable of absorbing energy when the impact mass 262 collides 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 contacts and collides with the damping block 261 on the corresponding spring bracket 52, the collision block 262 and the damping block 261 absorb energy and buffer, so that the limiting and buffering functions are realized, and the impact force caused by collision to the tower can be effectively reduced.

The displacement tuned mass damper 100 according to the present application can provide damping and buffering, thereby effectively reducing the impact force to the tower due to the collision. The guiding 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 vibrations and providing damping for the displacement tuned mass damper 100. The spring systems 5 arranged on the two sides are matched with increasing and decreasing the weight of the top mass block system 3, so that the natural frequency of the displacement tuning mass damper 100 can be adjusted, the natural frequency of the displacement tuning mass damper 100 is completely matched with the natural frequency of the tower of the wind generating set, and the vibration reduction and buffering performances of the displacement tuning mass damper 100 are improved. The first springs 51 in the spring system 5 do not affect each other in the stretching process, and the arrangement mode of each first spring 51 can ensure that each first spring 51 realizes the maximum deformation, so that the structure of the displacement tuning mass damper 100 is compact enough, and can realize large deformation displacement in a limited space. The limit buffer system 6 can play a role in limit buffer for the displacement tuning mass damper 100 under the limit working condition, thereby providing operation limit capability and further improving the vibration reduction capability of the displacement tuning mass damper 100. The displacement tuning mass damper 100 can effectively damp vibration of the tower of the wind generating set, effectively reduce impact force on the tower caused by collision, and is very beneficial to enhancing the stability of the tower and improving the safety performance.

Finally, it should be noted that the above description is only of a preferred embodiment of the application and is not to be construed as limiting the application in any way. Although the application 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 techniques described in the foregoing examples, or equivalents may be substituted for elements thereof. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (13)

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

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

a guiding system (2) fixedly mounted on the load-bearing support, comprising a track (21) distributed in the longitudinal direction and a slider (22) adapted to the track, the slider being slidable along the track;

the mass block system (3) is arranged 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, wherein the frequency modulation mass module is formed by superposing a plurality of frequency modulation mass blocks, the fixed mass module is formed by superposing 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 tuning mass damper can be adjusted by increasing or decreasing the frequency modulation mass blocks;

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

two groups of spring systems (5) symmetrically arranged on two lateral sides of the mass block system, wherein the spring systems are configured to be capable of being pulled, pressed and deformed along with the sliding of the mass block system so as to buffer the mass block system, each group of spring systems comprises two first springs (51) which are distributed side by side, a first end of each first spring on the lateral outer side is fixedly connected with the mass block system through a spring bracket (52), a second end of each first spring on the lateral inner side is fixedly connected with the bearing support seat, and a first end of each first spring on the lateral inner side is fixedly connected with the bearing support seat through a spring bracket (52), and a second end of each first spring is fixedly connected with the mass block system;

and 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 absorb energy when the movement displacement of the mass block system reaches the limit position, so that buffer limit is formed for the mass block system.

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

3. Displacement tuned mass damper according to claim 1 or 2, characterized in that the lateral ends of the bottom tuning mass (310) against the guiding system are provided with a first step (311) and a second step (312), respectively, said first step being at the lower end face and said second step being at the upper end face,

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

4. The displacement tuned mass damper according to claim 1, wherein the damping system comprises a housing (41), a pole (42) arranged in the housing, and a tension rod (43) provided at both ends with a front end plate (44) and a rear end plate (45), respectively, a first end of the tension rod being fixedly connected to the pole and a second end extending out of the housing through the front end plate,

the end of the shell, which is 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 being connected with the first bracket and the second bracket, and the stretching rod can pull the magnetic pole to move axially relative to the shell.

5. The displacement tuned mass damper according to claim 4, wherein the inner wall of the housing is provided with a copper sleeve (47) with which the magnetic poles are in contact.

6. Displacement tuned mass damper according to claim 4 or 5, wherein a wear sleeve (48) is provided between the end plate and the tension rod.

7. The displacement tuned mass damper according to claim 1, wherein the limit buffer system is configured to include a hydraulic cylinder (61), a collision rod (62) provided in the hydraulic cylinder and movable in an axial direction of the hydraulic cylinder, a collision head (64) provided at a free end of the collision rod and having a diameter larger than that of the collision rod, and a second spring (63) fitted over the collision rod and an elastic pad (65) provided at an axially outer end of the collision head,

the second spring abuts against the collision head, and the limit buffer system can absorb energy when the collision head collides with the corresponding spring support.

8. The displacement tuned mass damper according to claim 7, wherein the limit buffer system is fixedly connected to the tuned mass module by a limit bracket (66), the outer surface of the hydraulic cylinder is configured in a screw shape and is mounted in a fitting manner to the limit bracket, and the initial distance between the limit buffer system and the corresponding spring bracket can be adjusted by rotating the limit buffer system.

9. The displacement tuned mass damper of claim 1, wherein the limit bumper system is configured to include a damper mass (261) disposed on the spring support and a crash mass (262) secured to a lower end of the tuned mass module, the limit bumper system being capable of absorbing energy upon impact of the crash mass with the damper mass.

10. Displacement tuned mass damper according to claim 1, characterized in that on both lateral sides of the lower end of the tuned mass module are provided laterally inwardly concave right-angled areas (35), in which two sets of the spring systems are arranged, respectively.

11. Displacement tuning mass damper according to claim 1, characterized in that at the longitudinal ends of the tuning mass module there are provided longitudinally inwardly extending grooves (33), the first and second brackets being arranged in the respective grooves.

12. The displacement tuned mass damper of claim 11, wherein a longitudinally extending mounting space (34) is reserved in the middle of the lower end of the tuned mass module, the damping system being mounted in the mounting space.

13. The displacement tuned mass damper of claim 11, wherein the damping system is mounted at an upper end of the mass system.