Rolling pendulum type active and passive composite tuned mass damper driven in two-way electromagnetic mode

Abstract

The invention relates to a bidirectional electromagnetically-driven rolling pendulum type active and passive composite tuned mass damper. The bidirectional electromagnetically-driven rolling pendulum type active and passive composite tuned mass damper comprises a sliding support and an inertia body. The sliding support is provided with a top side. A recess is formed on the top side of the sliding support. And the shape of the inner wall surface of the concave position corresponds to the whole or part of the spherical crown shape. The inertia body is at least partially contained in the concave position in a sliding mode, and the inertia body is provided with a bottom face. And the shape of the bottom surface of the inertia body corresponds to the whole or part of the spherical crown shape. And the bottom surface of the inertia body is opposite to the inner wall surface of the concave position. One of the sliding support and the inertia body is connected with a plurality of magnets, and the other one is connected with a plurality of electromagnetic windings. And when the sliding support and the inertia body slide relatively, the plurality of electromagnetic windings and the magnet form electromagnetic induction coupling. The electromagnetic control force generated by the electromagnetic winding on the magnet can increase the offset amplitude of the inertia body relative to the balance position, so that the inertia body has larger reset force relative to the sliding support, the bandwidth of the vibration reduction frequency is widened, and the vibration reduction device can adapt to the state of large load or shutdown.

Description

Technical Field

[0001] The present application relates to the technical field of ocean engineering and structural vibration reduction control, and particularly to a bidirectional electromagnetic-driven rolling pendulum type main-passive composite tuned mass damper. Background Art

[0002] Offshore wind power is of great significance in optimizing the energy structure, coping with climate change and implementing sustainable development. After more than a decade of development, the single-unit capacity and tower height of offshore wind turbines have been continuously increasing. In addition, the operating environment of offshore wind power equipment is complex, and the structural safety and fatigue problems are becoming increasingly prominent. By installing a vibration control system on offshore wind power equipment, the dynamic response of the equipment can be effectively reduced, the damage of its components can be alleviated, and the disaster resistance ability can be enhanced.

[0003] TMD (tuned mass damper) is a kind of vibration control system. Research shows that TMD has a significant vibration reduction effect on structural wind vibration and earthquakes. TMD operates without relying on external energy, and through the synergistic action of mass, stiffness and damping elements, it absorbs and transfers vibration energy from the structure.

[0004] However, the traditional TMD dissipates energy through friction damping, and its energy dissipation capacity is limited in a large-load environment. At the same time, the traditional TMD often can only adapt to a single working state of offshore wind power equipment and is difficult to produce a vibration control effect under different working states of offshore wind power equipment. Summary of the Invention

[0005] Based on this, the present invention provides a bidirectional electromagnetic-driven rolling pendulum type main-passive composite tuned mass damper that can solve or at least alleviate the above technical problems.

[0006] The present invention provides a bidirectional electromagnetic-driven rolling pendulum type main-passive composite tuned mass damper, comprising:

[0007] A sliding support provided with a top side; a concave position is formed on the top side of the sliding support; the shape of the inner wall surface of the concave position corresponds to all or part of a spherical crown shape; and

[0008] An inertial body is at least partially slidably received in the concave position; the inertial body is provided with a bottom surface; the shape of the bottom surface of the inertial body corresponds to all or part of a spherical crown shape; the bottom surface of the inertial body is disposed opposite to the inner wall surface of the concave position; one of the sliding supports and the inertial body is connected with a plurality of magnets, and the other is connected with a plurality of electromagnetic windings; when the sliding support and the inertial body slide relative to each other, the plurality of electromagnetic windings and the magnets form an electromagnetic induction coupling; several of the plurality of electromagnetic windings are distributed along a first predetermined arc, and several other electromagnetic windings are distributed along a second predetermined arc; one of the sliding support and the inertial body is provided with a rolling bearing assembly, and the other is in rolling contact with the rolling bearing assembly.

[0009] For the tuned mass damper of the present application, since the inner wall surface of the concave position is generally in a spherical crown shape and the bottom surface of the inertial body is also generally in a spherical crown shape, the inertial body can slide along an arc path in any direction in the concave position under the support of the rolling bearing assembly. The lowest point of the inertial body relative to the sliding support serves as the equilibrium position during the sliding process. Considering the shapes of the inner wall surface of the concave position and the bottom surface of the inertial body, the inertial body can automatically return to the equilibrium position under the action of its own gravity, thus avoiding the need to additionally provide a stiffness element. The tuned mass damper can generate a vibration control effect under different working conditions of the offshore wind power equipment, which is beneficial to improving the safety of the offshore wind power equipment. With the combination of the two damping dissipation mechanisms, the energy dissipation capacity of the tuned mass damper is improved, effectively solving the problem that the energy dissipation capacity of the friction damping is limited under large load disturbances. The electromagnetic control force generated by the electromagnetic windings on the magnets can increase the offset amplitude of the inertial body relative to the equilibrium position, enabling the inertial body to have a greater restoring force relative to the sliding support and broadening the bandwidth of the vibration damping frequency, so as to adapt to the states of large loads or shutdowns. By controlling the input current in the two groups of electromagnetic windings, electromagnetic control forces in different directions and magnitudes can be formed between the electromagnetic windings and the inertial body, which is beneficial to achieving vibration suppression effects in different directions on the offshore wind power equipment.

[0010] In one embodiment, a receiving groove is formed on the inner wall surface of the concave position; the electromagnetic winding and at least one of the rolling bearing assemblies are received in the receiving groove.

[0011] In one embodiment, the receiving groove houses the electromagnetic winding and the rolling bearing assembly; the electromagnetic winding surrounds the outer periphery of the rolling bearing assembly.

[0012] In one embodiment, the magnets are in a ring shape; several magnets are respectively arranged around a predetermined axis; among the several magnets, the radii of the respective magnets are in a matching relationship of gradually increasing one by one; one of the bottom surface of the inertial body and the inner wall surface of the concave position cooperates with the several magnets to form all or part of a spherical crown shape.

[0013] In one embodiment, a plurality of magnets are connected to one of the sliding support and the inertial body, and the other is made of ferromagnetic material in whole or in part.

[0014] In one embodiment, a limiting member is further included; the limiting member is arranged along the circumferential direction of the concave position.

[0015] In one embodiment, a base is further included; the base is connected between the limiting member and the sliding support.

[0016] In one embodiment, the inertial body includes at least two inertial blocks; one of the inertial blocks is provided with the bottom surface, and the other inertial blocks are arranged on the side of the one inertial block facing away from the sliding support; two adjacent inertial blocks are arranged at intervals.

[0017] In one embodiment, the rolling bearing assembly includes a guide rail and a plurality of balls installed on the guide rail; one of the sliding support and the inertial body is connected to the guide rail, and the other is in contact with the plurality of balls.

[0018] In one embodiment, the inertial body has an equilibrium position relative to the sliding support; one of the sliding support and the inertial body is provided with a central region; the magnet is arranged on the outer peripheral side of the central region; in the equilibrium position, the central region abuts against the rolling bearing assembly. Description of the Drawings

[0019] Figure 1 Is a three-dimensional schematic diagram of a two-way electromagnetic-driven rolling pendulum type main and passive composite tuned mass damper according to an embodiment of the present application.

[0020] Figure 2 Is Figure 1 The exploded schematic diagram of the two-way electromagnetic-driven rolling pendulum type main and passive composite tuned mass damper shown in.

[0021] Figure 3 Is Figure 1 The three-dimensional cross-sectional view of the two-way electromagnetic-driven rolling pendulum type main and passive composite tuned mass damper shown in. The inertial body is in the equilibrium position.

[0022] Figure 4 Is Figure 1 The three-dimensional schematic diagram of the sliding support, the base, the electromagnetic winding and the rolling bearing assembly in the two-way electromagnetic-driven rolling pendulum type main and passive composite tuned mass damper shown in.

[0023] Figure 5 Is Figure 1 The three-dimensional schematic diagram of the inertial body and the magnet in the two-way electromagnetic-driven rolling pendulum type main and passive composite tuned mass damper shown in.

[0024] Reference numerals: 100, tuned mass damper; 20, sliding support; 201, top side; 21, recess; 22, receiving groove; 30, inertial body; 301, bottom surface; 31, inertial block; 32, positioning rod; 33, nut member; 40, magnet; 401, predetermined axis line; 50, electromagnetic winding; 501, first predetermined arc; 502, second predetermined arc; 60, rolling bearing assembly; 61, guide rail; 62, ball; 70, limiting member; 80, base; 81, bottom plate portion; 811, mounting groove; 82, support ear portion; 83, fixing hole position. Detailed implementation manners

[0025] The technical solutions of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some, but not all, of the embodiments of the present application. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present application without creative efforts shall fall within the protection scope of the present application.

[0026] In the description of the present application, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present application. In addition, the terms "first", "second", and "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance.

[0027] In the description of the present application, it should be noted that unless otherwise clearly defined and limited, the terms "mounted", "connected", and "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, an integral connection, a mechanical connection, an electrical connection, a direct connection, an indirect connection through an intermediate medium, or a communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific situations.

[0028] The technical solutions provided by the embodiments of the present application will be introduced below with reference to the accompanying drawings.

[0029] Combined with Figure 1 As shown, the present application provides a bidirectional electromagnetic-driven rolling pendulum type main-passive composite tuned mass damper 100, which is applied to offshore wind power equipment to reduce the vibration of offshore wind power equipment. Exemplarily, the offshore wind power equipment is used to convert wind energy into electrical energy.

[0030] Exemplarily, an offshore wind power device includes a tower barrel, a nacelle installed on the tower barrel, and a wind turbine rotatably arranged relative to the nacelle. Optionally, a rolling pendulum type main and passive composite tuned mass damper 100 driven by bidirectional electromagnetic force is connected to the top of the tower barrel. Optionally, a rolling pendulum type main and passive composite tuned mass damper 100 driven by bidirectional electromagnetic force is connected to the interior of the nacelle. Optionally, a rolling pendulum type main and passive composite tuned mass damper 100 driven by bidirectional electromagnetic force is connected to the top of the nacelle.

[0031] For the sake of simplicity in description, hereinafter, the rolling pendulum type main and passive composite tuned mass damper 100 driven by bidirectional electromagnetic force will be briefly referred to as the tuned mass damper 100.

[0032] Specifically, as shown in Figure 2 and Figure 3 , the tuned mass damper 100 includes a sliding support 20 and an inertial body 30. The sliding support 20 is provided with a top side 201. The sliding support 20 forms a concave position 21 on the top side 201. The inner wall surface shape of the concave position 21 corresponds to all or part of a spherical crown shape. The inertial body 30 is at least partially slidably received in the concave position 21, and the inertial body 30 is provided with a bottom surface 301. The shape of the bottom surface 301 of the inertial body 30 corresponds to all or part of a spherical crown shape. The bottom surface 301 of the inertial body 30 is disposed opposite to the inner wall surface of the concave position 21. One of the sliding support 20 and the inertial body 30 is connected with a plurality of magnets 40, and the other is connected with a plurality of electromagnetic windings 50. When the sliding support 20 and the inertial body 30 slide relative to each other, the plurality of electromagnetic windings 50 and the magnets 40 form electromagnetic induction coupling. A plurality of the electromagnetic windings 50 among the plurality of electromagnetic windings 50 are distributed along a first predetermined arc 501, and a plurality of the other electromagnetic windings 50 are distributed along a second predetermined arc 502. One of the sliding support 20 and the inertial body 30 is provided with a rolling bearing assembly 60, and the other is in rolling contact with the rolling bearing assembly 60.

[0033] For the tuned mass damper 100 of the present application, since the inner wall surface of the concave position 21 is generally in a spherical crown shape and the bottom surface 301 of the inertial body 30 is also generally in a spherical crown shape, under the support of the rolling bearing assembly 60, the inertial body 30 can slide along an arc path in any direction within the concave position 21. The lowest point of the inertial body 30 relative to the sliding support 20 serves as the equilibrium position during the sliding process. Combining the shape of the inner wall surface of the concave position 21 and the bottom surface 301 of the inertial body 30, the inertial body 30 can automatically return to the equilibrium position under the action of its own gravity, thus avoiding the need to additionally provide a stiffness element.

[0034] Understandably, the magnetic fields provided by a number of magnets 40 form a magnetic coupling with the electromagnetic windings 50. When the tuned mass damper 100 is applied to an offshore wind power device, the operating modes of the tuned mass damper 100 include a passive mode and an active mode. The passive mode is used to achieve vibration damping control in the daily operating state of the offshore wind power device. The active mode is used to achieve vibration damping control in the state where the offshore wind power device is subjected to large loads or shut down. Therefore, the tuned mass damper 100 can produce a vibration control effect in different operating states of the offshore wind power device, which is beneficial to improving the safety of the offshore wind power device.

[0035] In the passive mode, the tuned mass damper 100 has two damping dissipation mechanisms. The first damping dissipation mechanism is that when the inertial body 30 slides relative to the sliding support 20, a rolling friction is formed between one of the sliding support 20 and the inertial body 30 and the rolling bearing assembly 60, thereby forming a frictional damping that can consume the relative sliding energy between the inertial body 30 and the sliding support 20. The second damping dissipation mechanism is that when the electromagnetic windings 50 are connected but no current is input, when the inertial body 30 slides relative to the sliding support 20, a relative movement also occurs synchronously between the magnets 40 and the electromagnetic windings 50. There is an electromagnetic induction effect between the magnets 40 and the electromagnetic windings 50. The electromagnetic windings 50 cut the magnetic field generated by the magnets 40, and eddy currents are formed in the electromagnetic windings 50. Since the eddy currents can be consumed in the form of heat or other forms, an eddy current damping that can consume the relative sliding energy between the inertial body 30 and the sliding support 20 is formed. With the combination of the two damping dissipation mechanisms, the energy dissipation capacity of the tuned mass damper 100 is improved, effectively solving the problem that the energy dissipation capacity of the frictional damping is limited under large load disturbances.

[0036] In the active mode, the electromagnetic windings 50 are input with current and generate a magnetic field, and the electromagnetic windings 50 form a magnetic coupling with the magnets 40. The electromagnetic control force generated by the electromagnetic windings 50 on the magnets 40 can increase the offset amplitude of the inertial body 30 relative to the equilibrium position, make the inertial body 30 have a greater restoring force relative to the sliding support 20, and broaden the bandwidth of the vibration damping frequency, so as to adapt to the state of large loads. The electromagnetic control force in any direction can be decoupled into two substantially perpendicular unidirectional control forces. One unidirectional control force is applied between a number of electromagnetic windings 50 and the corresponding magnets 40, and the other unidirectional control force is applied between another number of electromagnetic windings 50 and the other corresponding magnets 40. By controlling the input current in the two groups of electromagnetic windings 50, electromagnetic control forces in different directions and magnitudes can be formed between the electromagnetic windings 50 and the inertial body 30, which is beneficial to achieving vibration suppression in different directions for the offshore wind power device.

[0037] Exemplarily, for the large loads borne by the offshore wind power device, the large loads can be understood as relatively large wind loads and wave loads.

[0038] Understandably, supported by the rolling bearing assembly 60, the bottom surface 301 of the inertial body 30 is spaced from the inner wall surface of the concave portion 21, so as to reduce the resistance suffered by the inertial body 30 when sliding relative to the sliding support 20. Understandably, since the bottom surface 301 of the inertial body 30 is spaced from the inner wall surface of the concave portion 21, a certain air flow space is formed, which is beneficial to improving the heat dissipation of the bottom surface 301 of the inertial body 30.

[0039] In some embodiments, one of the sliding support 20 and the inertial body 30 is connected with a plurality of magnets 40, and the other is made of ferromagnetic material in whole or in part. Specifically, in the passive mode, a magneto-induced attractive force is formed between the sliding support 20 and the other of the inertial body 30 and the plurality of magnets 40. The magneto-induced attractive force is perpendicular to the tangent plane of the bottom surface 301 of the inertial body 30, or the magneto-induced attractive force is perpendicular to the tangent plane of the inner wall surface of the concave portion 21. Since the magneto-induced attractive force is ultimately applied between the inertial body 30 and the sliding support 20, and the rolling bearing assembly 60 rolls and abuts between the inertial body 30 and the sliding support 20, the magneto-induced attractive force can increase the frictional damping between the inertial body 30 and the sliding support 20.

[0040] Exemplarily, when the inertial body 30 is connected with a plurality of magnets 40, the sliding support 20 is made of ferromagnetic material in whole or in part, so as to form a magneto-induced attractive force between the plurality of magnets 40 and the sliding support 20. Exemplarily, when the sliding support 20 is connected with a plurality of magnets 40, the inertial body 30 is made of ferromagnetic material in whole or in part, so as to form a magneto-induced attractive force between the plurality of magnets 40 and the inertial body 30.

[0041] In some embodiments, in combination with Figure 3 and Figure 5 as shown, the inertial body 30 has a balanced position relative to the sliding support 20. One of the sliding support 20 and the inertial body 30 is provided with a middle region. The magnet 40 is disposed on the outer peripheral side of the middle region. When the inertial body 30 is in the balanced position, the middle region abuts against the rolling bearing assembly 60, so that when the inertial body 30 is in the balanced position, it can avoid the lower end of the inertial body 30 from being suspended relative to the sliding support 20, prevent most of the gravity of the inertial body 30 from being applied to the magnet 40, and reduce the loss of the magnet 40.

[0042] Exemplarily, in combination with Figure 5 as shown, the middle region 302 is the region near the center of the bottom surface 301 of the inertial body 30. Since the magnet 40 is installed on the inertial body 30 at the same time and the magnet 40 is disposed on the outer peripheral side of the middle region 302, the magnet 40 bypasses the region near the center of the bottom surface 301 of the inertial body 30. When the inertial body 30 is in the balanced position, the middle region 302 of the inertial body 30 abuts against the rolling bearing assembly 60, so as to bear a part of the gravity of the inertial body 30.

[0043] Exemplarily, the middle region is the region near the center of the inner wall surface of the concave portion 21. Understandably, the magnet 40 is mounted on the sliding support 20, and the magnet 40 is disposed on the outer peripheral side of the middle region. At the equilibrium position, the rolling bearing assembly 60 abuts between the region near the center of the bottom surface 301 of the inertial body 30 and the region near the center of the inner wall surface of the concave portion 21.

[0044] In some embodiments, in combination with Figure 1 as shown, the tuned mass damper 100 further includes a limiting member 70. The limiting member 70 is disposed along the circumferential direction of the concave portion 21. When the movement amplitude of the inertial body 30 is too large, the limiting member 70 can limit the inertial body 30 to prevent the inertial body 30 from completely leaving the concave portion 21 due to excessive relative speed. Understandably, when the swing amplitude of the inertial body 30 exceeds a preset limit value, an impact will occur between the inertial body 30 and the limiting member 70.

[0045] Optionally, the limiting member 70 is elastic to avoid a violent collision when the limiting member 70 contacts the inertial body 30. Exemplarily, the limiting member 70 is a rubber pad. Optionally, an elastic material is connected to the outer periphery of the inertial body 30. When the swing amplitude of the inertial body 30 exceeds the preset limit value, a collision contact occurs between the limiting member 70 and the elastic material on the outer periphery of the inertial body 30.

[0046] Optionally, a single limiting member 70 is annular, and the limiting member 70 is disposed along the circumferential direction of the concave portion 21, thereby defining the sliding range of the inertial body 30. Further, the limiting member 70 surrounds the outer peripheral side of the concave portion 21.

[0047] Optionally, a plurality of limiting members 70 are distributed along the circumferential direction of the concave portion 21, thereby defining the sliding range of the inertial body 30.

[0048] In some embodiments, in combination with Figure 1 and Figure 2 as shown, the tuned mass damper 100 further includes a base 80. The base 80 is connected between the limiting member 70 and the sliding support 20 to position the limiting member 70 relative to the sliding support 20.

[0049] Optionally, in combination with Figure 2 as shown, the base 80 is provided with a mounting groove 811. The sliding support 20 is received in the mounting groove 811, and the mounting groove 811 limits the sliding support 20. Exemplarily, the mounting groove 811 is disposed at the middle position of the base 80. Exemplarily, the sliding support 20 is received in the mounting groove 811 by interference fit.

[0050] Exemplarily, in combination with Figure 4As shown, the base 80 includes a bottom plate portion 81 and a plurality of ear portions 82 connected to the bottom plate portion 81. An installation groove 811 is provided on the bottom plate. The plurality of ear portions 82 are arranged around the outer periphery of the installation groove 811. One side of the ear portion 82 is close to the installation groove 811, and the limiting member 70 is connected to this side of the ear portion 82.

[0051] Optionally, in combination with Figure 4 As shown, the base 80 is provided with fixing holes 83 for fixedly connecting the base 80 to the vibrating structure in the offshore wind power equipment. Exemplarily, a fastener passes through the fixing holes 83 and the tower barrel. Exemplarily, the fixing holes 83 penetrate through the bottom plate portion 81 and the ear portions 82. Exemplarily, the base 80 is fixed inside the tower barrel. Exemplarily, the base 80 is fixed at the top of the tower barrel. Exemplarily, the base 80 is installed inside the nacelle or at the top of the nacelle. Exemplarily, the vibrating structure in the offshore wind power equipment is the tower barrel.

[0052] Optionally, the base 80 is made of steel material.

[0053] It can be understood that when the space in the recess 21 is relatively large, when the inertial body 30 slides relative to the sliding support 20 to different positions, the inertial body 30 can be kept accommodated in the recess 21.

[0054] It can be understood that in combination with Figure 3 As shown, when the space in the recess 21 is relatively small, the inertial body 30 may always be partially accommodated in the recess 21. Exemplarily, when the inertial body 30 deviates from the equilibrium position, a part of the inertial body 30 is outside the recess 21.

[0055] In some embodiments, in combination with Figure 2 and Figure 4 As shown, a receiving groove 22 is formed on the inner wall surface of the recess 21. At least one of the electromagnetic winding 50 and the rolling bearing assembly 60 is accommodated in the receiving groove 22, which is beneficial to controlling the spacing distance between the bottom surface 301 of the inertial body 30 and the inner wall surface of the recess 21 and improving the compactness of the tuned mass damper 100.

[0056] Exemplarily, when the thickness of the rolling bearing assembly 60 is greater than the thickness of the electromagnetic winding 50, the rolling bearing assembly 60 is partially accommodated in the receiving groove 22, and the electromagnetic winding 50 can be arranged outside the receiving groove 22. When the spacing distance between the bottom surface 301 of the inertial body 30 and the inner wall surface of the recess 21 is greater than the thickness of the electromagnetic winding 50, the electromagnetic winding 50 will not be worn due to the relative sliding of the inertial body 30.

[0057] Exemplarily, the electromagnetic winding 50 is received in the receiving groove 22, and the rolling bearing assembly 60 is disposed outside the receiving groove 22. Exemplarily, a part of the receiving groove 22 houses the electromagnetic winding 50, and another part of the receiving groove 22 houses the rolling bearing assembly 60.

[0058] In another embodiment, the receiving groove 22 may also be provided on the bottom surface 301 of the inertial body 30.

[0059] In some embodiments, in combination with Figure 4 As shown, the electromagnetic winding 50 and the rolling bearing assembly 60 are received in the receiving groove 22. The electromagnetic winding 50 surrounds the outer periphery of the rolling bearing assembly 60. It can be understood that since the electromagnetic winding 50 and the rolling bearing assembly 60 are received in the same receiving groove 22 at the same time, the compactness of the tuned mass damper 100 can be further improved, and the opening area of the receiving groove 22 can be reduced, ensuring the structural stability of the sliding support 20 or the inertial body 30. It can be understood that the height of the rolling bearing assembly 60 is greater than the depth of the receiving groove 22, so that a gap is maintained between the bottom surface 301 of the inertial body 30 and the inner wall surface of the recess 21.

[0060] Exemplarily, the curvature of the bottom surface 301 of the inertial body 30 is the same as or substantially the same as the curvature of the inner wall surface of the recess 21, so as to maintain a uniform gap between the bottom surface 301 of the inertial body 30 and the inner wall surface of the recess 21.

[0061] Optionally, the tuned mass damper 100 can be simplified to a simple pendulum model, and the frequency of the tuned mass damper 100 is as shown in Equation (1):

[0062]

[0063] In Equation (1), g is the acceleration due to gravity, and R is the radius of curvature of the inner wall surface of the recess 21, which can also be understood as the radius of the sliding trajectory of the inertial body 30. It can be understood that the curvature of the bottom surface 301 of the inertial body 30 and the curvature of the inner wall surface of the recess 21 can be determined according to Equation (1).

[0064] Exemplarily, in the active mode, the electromagnetic winding 50 passes a current and generates a magnetic field. This magnetic field forms a coupling with the magnetic field generated by the magnet 40, and the inertial body 30 slides relative to the sliding support 20 under the action of the electromagnetic control force, and the electromagnetic winding 50 affects the position or speed of the inertial body 30 through the electromagnetic control force. Specifically, when it is necessary to control the position of the inertial body 30 relative to the sliding support 20, by inputting a specified current to the electromagnetic winding 50, the electromagnetic control force can be separated from the gravity of the inertial body 30 and balanced at a specified position point, so that the inertial body 30 can be maintained at a specified position relative to the sliding support 20.

[0065] It is understandable that when the direction of the electromagnetic control force is substantially the same as the direction of movement of the inertial body 30, the deviation amplitude of the inertial body 30 relative to the equilibrium position can be increased. It is understandable that by periodically adjusting the direction of the current passing through the electromagnetic winding 50, the electromagnetic control force can be periodically changed, so that the inertial body 30 can maintain a larger deviation amplitude.

[0066] Optionally, in the active mode, based on the principle of a linear motor, the electromagnetic winding 50 is input with a three-phase current, and a traveling wave magnetic field with a sinusoidal distribution is formed. The magnetic field interacts with the constant magnetic field provided by the plurality of magnets 40 to form an electromagnetic force. The electromagnetic force can drive the plurality of magnets 40 to generate a position, thereby adjusting the relative position between the inertial body 30 and the sliding support 20.

[0067] Exemplarily, a plurality of electromagnetic windings 50 are distributed along the first predetermined arc 501 to form a three-phase structure. Specifically, the plurality of electromagnetic windings 50 are arranged linearly in sequence, and the front and rear electromagnetic windings 50 are staggered by a certain distance, which is smaller than the size of a single electromagnetic winding 50 along the distribution direction.

[0068] Exemplarily, a plurality of electromagnetic windings 50 are distributed along the second predetermined arc line 502 to form a three-phase structure.

[0069] It can be understood that one of the two unidirectional control forces is tangent to the first predetermined arc 501, and the other is tangent to the second predetermined arc 502. By adjusting the magnitude and positive and negative directions of the two unidirectional control forces, an electromagnetic control force in any direction can be formed between the sliding support 20 and the inertial body 30. Optionally, the second predetermined arc 502 is orthogonal to the first predetermined arc 501, and the electromagnetic control force in any direction can be easily decoupled into two perpendicular or substantially perpendicular unidirectional control forces.

[0070] Understandably, in the active mode, the tuned mass damper 100 provides an excellent bidirectional vibration reduction and energy dissipation effect for the offshore wind power equipment, and horizontal vibrations in any direction can be efficiently controlled by a single inertial body 30 .

[0071] Exemplarily, in the plurality of electromagnetic windings 50 along the second predetermined arc 502 or the first predetermined arc 501, when the phase relationship of the current in each electromagnetic winding 50 changes, the plurality of electromagnetic windings 50 can generate a magnetic field that changes in motion, and more specifically, the strong magnetic region in the magnetic field changes in motion relative to the plurality of electromagnetic windings 50. After the magnetic field of the magnet 40 is coupled with the magnetic field, the position of the inertial body 30 changes with the magnetic field, thereby being able to adjust the position of the inertial body 30 relative to the sliding support 20. More specifically, the position of the magnet 40 coincides with the strong magnetic region in the magnetic field.

[0072] Understandably, since the electromagnetic winding 50 can not only induce eddy currents and consume electrical energy in the passive mode, but also generate a non-contact electromagnetic control force on the magnet 40 in the active mode, it is beneficial to simplify the overall structure of the tuned mass damper 100 and make the tuned mass damper 100 more economical and efficient.

[0073] Understandably, the number of turns and the size of the electromagnetic winding 50 are designed according to the actual electromagnetic drive power requirements.

[0074] Optionally, the magnet 40 is made of a permanent magnetic material. Optionally, the magnet 40 has an electromagnet structure.

[0075] In some embodiments, in combination Figure 2 and Figure 5 as shown, the magnet 40 is annular. Specifically, since the magnet 40 is annular, it is beneficial to keep the magnetic field distribution of the magnet 40 consistent in the circumferential direction. Understandably, when the magnetic field distribution of the magnet 40 is consistent in the circumferential direction, when in the equilibrium position, the inertial body 30 can maintain a relative relationship with the electromagnetic winding 50 at any circumferential angle, thereby reducing the assembly difficulty and maintenance requirements of the inertial body 30.

[0076] In some embodiments, in combination Figure 2 as shown, a plurality of magnets 40 are arranged around a predetermined axis line 401. Among the plurality of magnets 40, the radii of the respective magnets 40 are in a cooperative relationship of increasing one by one. Therefore, along from the predetermined axis line 401 to the outer periphery, the direction of the magnetic field formed by the plurality of magnets 40 changes sinusoidally, which is beneficial to adjusting the magnitude and direction of the electromagnetic control force in the active module and beneficial to ensuring the damping effect. Specifically, when the plurality of magnets 40 are connected to the inertial body 30, the position distribution of the respective magnets 40 is set according to the shape change of the bottom surface 301 of the inertial body 30. Exemplarily, the plurality of magnets 40 are arranged in a tower shape. Understandably, the magnet 40 with a smaller radius is relatively closer to the center of the bottom surface 301 of the inertial body 30, and the magnet 40 with a larger radius is relatively farther from the center of the bottom surface 301 of the inertial body 30.

[0077] Optionally, by controlling the magnitude relationship between the magnetic field intensity of the magnet 40 with a smaller radius and the magnetic field intensity of the magnet 40 with a larger radius, the magnetic field intensity formed by the plurality of magnets 40 can be kept consistent from the center to the outer periphery.

[0078] In some embodiments, one of the bottom surface 301 of the inertial body 30 and the inner wall surface of the concave portion 21 cooperates with the plurality of magnets 40 to form all or part of a spherical crown shape. Optionally, in combination Figure 5As shown, when a plurality of magnets 40 are connected to the inertial body 30, the outer peripheral surface of each magnet 40 cooperates with the bottom surface 301 of the inertial body 30 to form a complete spherical crown shape. Understandably, the outer peripheral surface of the magnet 40 is tangentially arranged with the bottom surface 301 of the inertial body 30. Understandably, the curvature of the outer peripheral surface of the magnet 40 is correspondingly arranged with the curvature of the outer periphery of the inertial body 30.

[0079] Optionally, when a plurality of magnets 40 are connected to the sliding support 20, the inner peripheral surface of each magnet 40 cooperates with the inner wall surface of the concave portion 21 to form a complete spherical crown shape. Understandably, the inner peripheral surface of the magnet 40 is tangentially arranged with the inner wall surface of the concave portion 21.

[0080] Understandably, the performance parameters and geometric dimensions of the magnet 40 can be designed according to actual damping requirements.

[0081] Optionally, in combination with Figure 3 As shown, the distance between the upper end and the lower end of the inertial body 30 is less than the diameter of the inertial body 30, which is beneficial to ensuring that the inertial body 30 can return to the equilibrium position by gravity.

[0082] In some embodiments, in combination with Figure 5 As shown, the inertial body 30 includes at least two inertial blocks 31. One of the inertial blocks 31 is provided with a bottom surface 301, and the other inertial blocks 31 are arranged on the side of the one inertial block 31 facing away from the sliding support 20. Two adjacent inertial blocks 31 are spaced apart, so that the inertial body 30 can have a larger heat dissipation area, avoiding affecting the passive energy dissipation efficiency of the tuned mass damper 100 or the accuracy of the active control force due to temperature change, which is beneficial to ensuring the performance of the tuned mass damper 100.

[0083] Exemplarily, in combination with Figure 5 As shown, for the sake of simplified description and easy understanding, the inertial block 31 provided with the bottom surface 301 is briefly described as the first inertial block 31. At least one positioning rod 32 is fixedly connected to the first inertial block 31. The positioning rod 32 is inserted into the other inertial blocks 31. Optionally, a spacer ring is also sleeved on the positioning rod 32. The spacer ring is arranged between two adjacent inertial blocks 31, so as to keep the adjacent inertial blocks 31 spaced apart. Optionally, a nut member 33 is threadedly sleeved on the end of the positioning rod 32 away from the first inertial block 31, and the nut member 33 can limit the other inertial blocks 31 from detaching from the positioning rod 32.

[0084] Optionally, to effectively reduce the acceleration response of the structure, the optimal tuning parameters of the tuned mass damper 100 can be calculated through the classical Den-Hartog formula derived based on the fixed-point theory, namely Equation (2) and Equation (3):

[0085]

[0086] In Equation (2), ωn is the natural vibration frequency of the tuned mass damper 100. Ω n is the natural vibration frequency of the vibrating structure in the offshore wind power equipment. In Equation (3), μ is the ratio between the mass of the tuned mass damper 100 and the mass of the vibrating structure in the offshore wind power equipment.

[0087] In some embodiments, in combination with Figure 4 As shown, the rolling bearing assembly 60 includes a guide rail 61 and a plurality of balls 62 mounted on the guide rail 61. One of the sliding support 20 and the inertial body 30 is connected to the guide rail 61, and the other is in contact with the plurality of balls 62. Understandably, the guide rail 61 is used to define the position of the balls 62, and there is a certain gap between the surface of the guide rail 61 and the balls 62, allowing the balls 62 to roll in any direction.

[0088] Exemplarily, the balls 62 protrude out of the guide rail 61 in two opposite directions. One end of the protruding balls 62 abuts against the inertial body 30, and the other end of the protruding balls 62 abuts against the sliding support 20.

[0089] Exemplarily, the guide rail 61 is received in the receiving groove 22. The electromagnetic winding 50 is wound around the outer peripheral side of the guide rail 61.

[0090] Exemplarily, the sliding surface of the guide rail 61 and the surface of the balls 62 are respectively coated with a low-friction lubricating material. Exemplarily, the balls 62 are made of a steel material with high hardness and wear resistance, and the specific quantity is designed according to actual requirements. The bearing capacity of a single ball 62 can be calculated by Equation (4):

[0091]

[0092] In Equation (4), P is the bearing capacity of the balls 62, and E, r, σ HP are respectively the elastic modulus, radius and allowable contact stress of the balls 62.

[0093] In some embodiments, the tuned mass damper 100 further includes a vibration detection component and a control unit. The vibration detection component is used to detect the vibration condition of the vibrating structure in the offshore wind power equipment and generate a vibration detection signal. The control unit is electrically connected to the vibration detection component and the electromagnetic winding 50. The control unit is at least used to adjust the magnitude and direction of the electromagnetic control force according to the vibration detection signal.

[0094] Specifically, for the type or quantity of the vibration detection component, it can be selected according to specific anti-vibration requirements and monitoring needs. Optionally, the vibration detection component is a vibration sensor. Optionally, the vibration detection component is an acceleration sensor.

[0095] Specifically, the control unit can adjust the magnitude and direction of the current passing through the electromagnetic winding 50, so as to change the magnitude and direction of the electromagnetic control force between the control unit and the magnet 40, and control the movement of the inertial body 30. Exemplarily, the control unit calculates the required magnitude of the electromagnetic control force according to the vibration detection signal.

[0096] Optionally, the control unit is integrated inside the offshore wind power equipment. Exemplarily, the control unit is integrated inside the nacelle.

[0097] The above embodiments are only descriptions of the preferred embodiments of the present application, and do not limit the scope of the present application. Without departing from the design spirit of the present application, various deformations and improvements made by those of ordinary skill in the art to the technical solutions of the present application shall fall within the protection scope determined by the claims of the present application.

Claims

1. A bidirectional electromagnetically driven rolling pendulum active and passive composite tuned mass damper, characterized in that: include: The sliding support is provided with a top side; the sliding support is formed with a concave position on the top side; the inner wall surface shape of the concave position corresponds to the whole or part of the spherical crown; and The inertial body is at least partially slidably accommodated in the concave position; the inertial body is provided with a bottom surface; the bottom surface shape of the inertial body corresponds to the whole or part of the spherical crown; the bottom surface of the inertial body is arranged opposite to the inner wall surface of the concave position; one of the sliding support and the inertial body is connected with a plurality of magnets, and the other is connected with a plurality of electromagnetic windings; when the sliding support and the inertial body slide relative to each other, the plurality of electromagnetic windings and the magnets form electromagnetic induction coupling; a plurality of electromagnetic windings among the plurality of electromagnetic windings are distributed along a first predetermined arc, and another plurality of electromagnetic windings are distributed along a second predetermined arc; one of the sliding support and the inertial body is installed with a rolling bearing assembly, and the other is in rolling contact with the rolling bearing assembly.

2. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: An accommodating groove is formed on the inner wall surface of the concave position; at least one of the electromagnetic winding and the rolling bearing assembly is accommodated in the accommodating groove.

3. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 2 is characterized in that: The containing groove contains an electromagnetic winding and a rolling bearing assembly; the electromagnetic winding surrounds the outer circumference of the rolling bearing assembly.

4. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: The magnet is annular; a plurality of magnets are respectively arranged around a predetermined axis; among the plurality of magnets, the radius of each magnet is in a matching relationship of increasing and changing one by one; the bottom surface of the inertial body and one of the inner wall surfaces of the concave position cooperate with the plurality of magnets to form all or part of a spherical crown.

5. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: One of the sliding support and the inertial body is connected with a plurality of magnets, and the other one is entirely or partially made of ferromagnetic material.

6. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: It also includes a limiting member; the limiting member is arranged along the circumference of the concave position.

7. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 6 is characterized in that: It also includes a base; the base is connected between the limiting member and the sliding support.

8. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: The inertia body comprises at least two inertia blocks; one of the inertia blocks is provided with the bottom surface, and the other inertia block is arranged on a side of the one of the inertia blocks facing away from the sliding support; two adjacent inertia blocks are arranged at intervals.

9. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1 is characterized in that: The rolling bearing assembly comprises a guide rail and a plurality of balls mounted on the guide rail; one of the sliding support and the inertial body is connected to the guide rail, and the other is in contact with the plurality of balls.

10. The bidirectional electromagnetically driven rolling pendulum active-passive composite tuned mass damper according to claim 1, characterized in that: The inertial body has a balanced position relative to the sliding support; one of the sliding support and the inertial body is provided with a middle area; the magnet is arranged on the outer peripheral side of the middle area; in the balanced position, the middle area abuts against the rolling bearing assembly.

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