A three - element adaptive nonlinear tuned vibration absorber system with a displacement - steering efficiency - enhancing mechanism

Abstract

The present invention relates to a displacement steering and efficiency-enhancing mechanism type three-element adaptive non-linear tuned vibration absorption system. The control box is connected to the controlled structure through a tuning unit. A liquid, a first fixed semi-magnetic disk, a semi-magnetic piston disk, and a second fixed semi-magnetic disk are arranged in the control box. One side of the displacement steering and efficiency-enhancing mechanism is connected to the semi-magnetic piston disk through a transmission rod, and the other side is connected to the controlled structure through an inertance container. Compared with the prior art, the present invention utilizes the convective component of the liquid to generate a hydrodynamic mass, utilizes the pulsed component of the liquid to generate a non-linear hydrodynamic damping, provides a non-linear electromagnetic negative stiffness for the vibration control of the structure, realizes the non-linear inertance behavior through the non-linear motion conversion of the displacement steering and efficiency-enhancing mechanism, establishes a parallel mechanism of the efficiency-enhancing hydrodynamic mass unit and the non-linear hydrodynamic damping unit, establishes a parallel mechanism of the electromagnetic negative stiffness unit and the non-linear inertance unit, and realizes the collaborative adaptive vibration damping effect based on the displacement amplitude enhancement.

Description

Technical Field

[0001] The present invention belongs to the technical field of civil engineering and relates to a ternary adaptive non-linear tuned vibration absorption system with a displacement steering and efficiency enhancement mechanism type. Background Art

[0002] In the aspect of using the inertial mass of liquid to control the vibration reduction of structures, the current main technologies (products) are tuned liquid dampers (TLD) and their combined control systems. In these technologies (products), most utilize the sloshing of liquid to generate inertial mass. However, this sloshing is generated by the convective components in the liquid, and the pulse components in the liquid still cannot provide additional liquid inertial mass or hydrodynamic damping during the sloshing process. Therefore, the existing technologies (products) still need to further explore the utilization methods of the pulse components of the liquid.

[0003] In addition, the current utilization of liquid mainly focuses on generating inertial mass, and the utilization of the enhanced hydrodynamic damping effect generated by liquid friction and shear is insufficient, and the utilization rate of the vibration reduction control potential of the liquid is low. Moreover, the current technology is difficult to achieve the coordinated control of liquid mass units and other high-performance control units, such as inertance units, electromagnetic negative stiffness units, etc., and the overall vibration reduction efficiency of the control system still needs to be further improved.

[0004] Patent CN117758880A discloses a tuned liquid mass-damping non-linear system based on orthogonal conversion and efficiency enhancement. The system includes a tuned liquid enhanced damping tank, a main structure, and an orthogonal motion conversion mechanism. The lower part and the interior of the tuned liquid enhanced damping tank are respectively provided with an orthogonal motion conversion mechanism. The orthogonal motion conversion mechanism at the lower part of the tuned liquid enhanced damping tank is respectively connected to the tuned liquid enhanced damping tank and the main structure. The orthogonal motion conversion mechanism inside the tuned liquid enhanced damping tank is connected to the orthogonal motion conversion mechanism at the lower part of the tuned liquid enhanced damping tank. The orthogonal motion conversion mechanism inside the tuned liquid enhanced damping tank is connected to the tank body of the tuned liquid enhanced damping tank and is connected to the grid plate. The orthogonal motion conversion mechanism includes rigid rods connected to each other, and the connection ends of the rigid rods are hinged. Although this patent utilizes the orthogonal motion conversion mechanism to amplify the horizontal displacement, utilizes the pulse components of the liquid in the liquid damping tank to generate a damping effect, and forms an enhanced liquid mass, it does not have a non-linear negative stiffness effect. Therefore, it limits the tuning ability of the device for the low-frequency vibration of the structure. And the formed enhanced liquid mass is limited by the liquid in the tank (that is, the upper limit of the enhanced mass is only the pulse component of the total liquid mass), and it is difficult to achieve free regulation.

[0005] Patent CN107268824A discloses a multi-dimensional tuned electromagnetic energy dissipation vibration damping device, which includes an outer box body and an inner box body. A plurality of small balls are arranged inside the outer box body, and the inner box body is arranged on the small balls to ensure that it can move freely in the horizontal direction. The two sides of the inner box body are connected to the inner side wall of the outer box body through electromagnetic dampers. A magnet is provided at each of the inner top and inner bottom of the inner box body, and a spring pendulum is suspended at the top of the inner box. The spring pendulum is located in the magnetic space formed by the magnets, and its swing can cut the magnetic induction lines. The outer side wall of the outer box body can move along the guide rail under the action of an external force through a slider, and the slider is connected to a translational rack. The translational rack moves with the slider, driving the rotating gear meshed with it to rotate. The rotating gear drives an inner core to rotate. The inner core is installed in an outer cylinder with magnetic poles on its inner wall, and a coil is wound around the inner core. The inner core rotates to cut the magnetic induction lines, thereby forming an eddy current damper. Although this patent forms an eddy current damper by using the device structure and electromagnetic principles, it only has a damping effect and does not have a negative stiffness effect. Although it uses a gear-rack mechanism, it only serves as a part of the structure to realize the eddy current damper, and its rotation angle is too small to produce an inertance behavior. The device described in this patent only includes a mass unit, a damping unit, and a spring unit, and its working principle is similar to that of a tuned mass damper. Summary of the Invention

[0006] The purpose of the present invention is to overcome at least one defect of the above-mentioned existing technologies and provide a displacement steering and efficiency-enhancing mechanism type ternary adaptive non-linear tuned vibration absorber system. The present invention uses the liquid convection component to generate a liquid dynamic mass, uses the liquid pulse component to generate a non-linear liquid dynamic damping, provides a non-linear electromagnetic negative stiffness for the vibration control of the structure, realizes the non-linear inertance behavior through the non-linear motion conversion of the displacement steering and efficiency-enhancing mechanism, establishes a parallel mechanism of the efficiency-enhancing liquid dynamic mass unit and the non-linear liquid dynamic damping unit, establishes a parallel mechanism of the electromagnetic negative stiffness unit and the non-linear inertance unit, and realizes the collaborative adaptive vibration damping effect based on the displacement amplitude enhancement.

[0007] The purpose of the present invention can be achieved through the following technical solutions:

[0008] One of the technical solutions of the present invention is to provide a displacement steering and efficiency-enhancing mechanism type ternary adaptive non-linear tuned vibration absorber system, which includes a dynamic vibration absorption unit, a tuning unit, and a displacement steering and efficiency-enhancing mechanism. The dynamic vibration absorption unit includes a control box and an inertance container. The control box is connected to the inertance container through the displacement steering and efficiency-enhancing mechanism. The inertance container is connected to the controlled structure. The control box is connected to the controlled structure through the tuning unit;

[0009] The control box is provided with liquid, a first fixed semi-magnetic disk, a semi-magnetic piston disk, and a second fixed semi-magnetic disk. One side of the displacement steering and efficiency enhancement mechanism is connected to the semi-magnetic piston disk through a transmission rod, and the other side is connected to the controlled structure through an inertance container. The semi-magnetic piston disk is arranged between the first fixed semi-magnetic disk and the second fixed semi-magnetic disk. An annular piston disk is arranged on the periphery of the semi-magnetic piston disk. The semi-magnetic piston disk and the annular piston disk move vertically between the first fixed semi-magnetic disk and the second fixed semi-magnetic disk. When the control box moves horizontally relative to the controlled structure, the liquid in the control box sloshes to generate liquid convection mass.

[0010] Further, the displacement steering and efficiency enhancement mechanism includes four rhombus structures and hinged rods connected to each other. The connection ends of the hinged rods are hinged. The displacement steering and efficiency enhancement mechanism is used to turn the horizontal movement of the control box relative to the controlled structure and amplify it into the vertical movement of the hinge points at both ends of one pair of sides of the displacement steering and efficiency enhancement mechanism.

[0011] Further, one of the hinge points at both ends of one pair of sides of the displacement steering and efficiency enhancement mechanism is connected to the transmission rod through a slide rail, and the other hinge point is connected to the inertance container through a slide rail;

[0012] One of the hinge points at both ends of the other pair of sides is connected to the controlled structure through a first connecting rod, and the other hinge point is connected to the control box through a first connecting rod.

[0013] As a preferred technical solution, the connection end of the first connecting rod to the controlled structure is rigidly connected, and the connection end to the displacement steering and efficiency enhancement mechanism is hinged.

[0014] Further, a certain gap is left between the annular piston disk and the control box.

[0015] As a preferred technical solution, holes are provided in the annular piston disk.

[0016] As a preferred technical solution, the liquid damping generated by the annular piston disk shearing the liquid is adjusted by changing the size of the gap or opening holes in the annular piston disk.

[0017] Further, the first fixed semi-magnetic disk, the semi-magnetic piston disk, and the second fixed semi-magnetic disk all include two permanent magnets with different magnetic poles up and down.

[0018] Further, the fixed semi-magnetic disk is connected to the control box through a fixed rod to ensure its relative position with the control box remains unchanged.

[0019] As a preferred technical solution, a fixed semi-magnetic disk is fixed in the middle of the control box, and the fixed semi-magnetic disk is connected to the side wall of the control box through a fixed rod.

[0020] Further, the inertance container includes a rack and pinion type inertance or a ball screw type inertance.

[0021] Further, the rack and pinion type inertance includes a rack, a first gear, a second gear and a disc. The hinge point at the other end of one side of the displacement steering and efficiency increasing mechanism is connected to the rack through a slide rail. The rack meshes with the first gear. The first gear meshes with the second gear. The second gear is rigidly connected to the disc and rotates coaxially.

[0022] As a preferred technical solution, the axis of the first gear is connected to the controlled structure through a second connecting rod. The axes of the second gear and the disc are connected to the controlled structure through a second connecting rod.

[0023] As a preferred technical solution, the diameter of the first gear is larger than that of the second gear.

[0024] Further, the ball screw type inertance includes a screw rod, a nut and a flywheel. The hinge point at the other end of one side of the displacement steering and efficiency increasing mechanism is connected to the screw rod through a slide rail. The screw rod extends into the nut. The nut is rigidly connected to the flywheel and rotates coaxially. The nut passes through a restraint ring. The translational degree of freedom of the nut relative to the restraint ring is constrained, and the rotational degree of freedom is not constrained.

[0025] As a preferred technical solution, the restraint ring is connected to the controlled structure through a third connecting rod.

[0026] As a preferred technical solution, the restraint ring includes a pair of thrust bearings arranged vertically and a rigid outer sleeve. A step is provided on the outer surface of the nut, and this step is constrained in the middle of the thrust bearings arranged vertically. The thrust bearings are used to ensure that the nut does not undergo vertical displacement during operation and can only rotate. The thrust bearings arranged vertically are wrapped by the rigid outer sleeve. The rigid outer sleeve is connected to the controlled structure through a third connecting rod to constrain the horizontal displacement and vertical displacement of the thrust bearings and the nut.

[0027] As a preferred technical solution, the slide rail includes a semi-enclosed plate member. The transmission rod or the inertance container extends out of the semi-enclosed plate member. A slide plate is arranged inside the semi-enclosed plate member. The upper and lower sides of the slide plate are respectively in contact sliding connection with the plate member through rollers.

[0028] The vertical movement of the hinge point at one end of one side of the displacement steering and efficiency increasing mechanism causes the synchronous vertical movement of the semi-magnetic piston disc inside the control box to generate a non-linear electromagnetic negative stiffness. The vertical movement of the semi-magnetic piston disc drives the pulsed liquid mass in the control box to shake and generates a non-linear hydrodynamic damping;

[0029] The vertical movement of the hinge point at the other end causes the internal rotation of the inertor, thereby generating a significant inertance coefficient and non-linear inertial control force.

[0030] Further, the tuning unit includes a vibration isolation support, and the control box is connected to the controlled structure through the vibration isolation support; the vibration isolation support is used to support the control box and can realize the adjustment of the tuning stiffness and additional damping in the tuning unit for the connection between the control box and the controlled structure.

[0031] As a preferred technical solution, the vibration isolation support is connected to the controlled structure through a vibration isolation pier; the vibration isolation pier is a non-essential component and can be not used if the height is sufficient.

[0032] As a preferred technical solution, the vibration isolation support includes a friction pendulum support, a rubber support or a flat sliding support.

[0033] As a preferred technical solution, the cross-section of the control box includes a circle or a rectangle.

[0034] As a preferred technical solution, the liquid can be selected according to actual needs and includes water or silicone oil.

[0035] As a preferred technical solution, the non-linear electromagnetic negative stiffness generated by the interaction between the semi-magnet piston disk and the fixed semi-magnet disk is adjusted by changing the magnetism of the magnet and the distance between the magnets.

[0036] As a preferred technical solution, the amplification effect of the displacement on the displacement by the displacement steering and amplification mechanism is adjusted by adjusting the initial angle of the hinge rod.

[0037] As a preferred technical solution, the inertance coefficient (apparent mass) of the inertor on the other side of the displacement steering and amplification mechanism is adjusted by adjusting the radii of the first gear, the second gear and the disk.

[0038] As a preferred technical solution, the inertance coefficient (apparent mass) of the inertor on the other side of the displacement steering and amplification mechanism is adjusted by adjusting the pitch of the lead screw and the radius of the flywheel.

[0039] One of the technical solutions of the present invention is to provide a method for using the displacement steering and amplification mechanism type three-element adaptive non-linear tuning vibration absorber system, and the method includes the following steps:

[0040] When the system is working, the control box and the controlled structure have a relative horizontal displacement, and the liquid in the control box sloshes to generate a hydrodynamic mass;

[0041] The displacement steering and efficiency - increasing mechanism on one side of the control box steers this relative horizontal displacement and increases it to an amplified vertical displacement, and transfers the amplified vertical displacement to the semi - magnetic piston disk through the slide rail and the transmission rod. At the same time, the amplified vertical displacement is transferred to the first gear through the slide rail and the rack, causing the first gear to rotate, or the amplified vertical displacement is transferred to the nut through the slide rail and the lead screw, causing the nut to rotate;

[0042] In the control box, the semi - magnetic piston disk moves vertically between the second fixed semi - magnetic disk and the first fixed semi - magnetic disk inside the control box, and according to the principle of electromagnetism, a non - linear electromagnetic negative stiffness will be generated;

[0043] At the same time, when the semi - magnetic piston disk moves vertically, the liquid continuously flows through the gap between the annular piston disk and the control box, and the semi - magnetic piston disk shears the liquid inside the control box to generate non - linear hydrodynamic damping;

[0044] On the other side of the displacement steering and efficiency - increasing mechanism, the rack drives the first gear to rotate, and then transfers it to the second gear to achieve amplification of the rotational motion;

[0045] At this time, the disk will rotate coaxially with the second gear to generate an inertance coefficient;

[0046] Or, the lead screw drives the nut to rotate and achieves amplification of the vertical displacement to the rotational motion;

[0047] At this time, the flywheel will rotate coaxially with the nut to generate an inertance coefficient.

[0048] Compared with the prior art, the present invention has the following beneficial effects:

[0049] (1) In the system proposed by the present invention, the displacement steering and efficiency - increasing mechanism is used to realize the steering and amplification of the hydrodynamic mass - electromagnetic negative stiffness - hydrodynamic damping multi - control box horizontal motion, so that the semi - magnetic piston disk in the box generates an amplified vertical motion, providing the possibility of structural vertical vibration control;

[0050] (2) While the present invention utilizes the convective component of the liquid in the control box to generate hydrodynamic mass, the vertical motion of the semi - magnetic piston disk can also shear the liquid pulse component at the bottom of the box, enabling the liquid pulse component that is originally difficult to play a role in vibration control to generate non - linear hydrodynamic damping, providing a mechanism scheme for utilizing the total mass of the tuned liquid. In addition, the interaction between the moving semi - magnetic piston disk and the fixed semi - magnetic disks at the bottom and in the box can also provide non - linear electromagnetic negative stiffness for the vibration control of the structure using the principle of electromagnetism, equivalently extending the convective period of the vertical hydrodynamic mass and broadening the low - frequency tuning control effect of the present invention;

[0051] (3) The displacement steering and efficiency - increasing mechanism of the present invention can not only convert the horizontal movement of the hydraulic mass - electromagnetic negative stiffness - hydraulic damping multi - control box into the vertical movement of the semi - magnetic piston disc, but also convert it into the vertical movement of the rack (or lead screw), and then drive the gear and disc (or nut and flywheel) below the displacement steering and efficiency - increasing mechanism. The inertance container providing the efficiency - increasing mass is independent of the liquid in the box and can be freely adjusted, providing a considerable non - linear inertial control force for structural control, achieving the tuned deformation control of the control box relative to the controlled structure. The combination of the non - linear inertial control force and the non - linear electromagnetic negative stiffness control force broadens the low - frequency vibration reduction control frequency band of the present invention;

[0052] (4) The system of the present invention realizes a non - linear mass unit based on liquid mass and inertance container; realizes a non - linear damping unit in the form of shearing liquid mass and the damping provided by the vibration isolation support; realizes a non - linear tuning unit with electromagnetic negative stiffness and the stiffness provided by the vibration isolation support; through the coordinated control of the non - linear three - vibration - reduction units (realizing non - linear inertance behavior by using the non - linear motion conversion of the displacement steering and efficiency - increasing mechanism, establishing the parallel mechanism of the efficiency - increasing hydraulic mass unit and the non - linear hydraulic damping unit, and establishing the parallel mechanism of the electromagnetic negative stiffness unit and the non - linear inertance unit), it realizes the adaptive non - linear vibration reduction effect based on displacement - amplitude efficiency increase, can achieve multi - level tuning, has a wider control frequency band and more flexible tuning ability, which is conducive to realizing the adaptive control of engineering structures under multi - level and multi - source excitations. Brief Description of the Drawings

[0053] Figure 1 It is a schematic structural diagram of the displacement steering and efficiency - increasing mechanism - type three - element adaptive non - linear tuned vibration absorber system in Embodiment 1 of the present invention;

[0054] Figure 2 It is a schematic structural diagram of the displacement steering and efficiency - increasing mechanism - type three - element adaptive non - linear tuned vibration absorber system in Embodiment 2 of the present invention.

[0055] Description of the Marks in the Figures:

[0056] 1 - control box, 2 - liquid, 3 - first fixed semi - magnetic disc, 4 - fixed rod, 5 - semi - magnetic piston disc, 6 - annular piston disc, 7 - second fixed semi - magnetic disc, 8 - transmission rod, 9 - articulated rod, 10 - articulated point, 11 - rack, 12 - first connecting rod, 13 - first gear, 14 - second gear, 15 - disc, 16 - second connecting rod, 17 - vibration isolation support, 18 - vibration isolation pier, 19 - controlled structure, 20 - slide rail, 21 - lead screw, 22 - nut, 23 - flywheel, 24 - restraint ring, 25 - third connecting rod. Detailed Description of the Invention

[0057] The present invention will be described in detail below in conjunction with specific embodiments. These embodiments are implemented on the premise of the technical solution of the present invention, and provide detailed implementation manners and specific operation processes. However, the protection scope of the present invention is not limited to the following embodiments.

[0058] In the description of the present invention, 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 drawings. It is only for the convenience of describing the present invention 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 of the present invention. In addition, the terms "first", "second", "third", etc. are used to describe common objects, and only represent different instances referring to the same object, rather than implying that the objects described in this way must be in a given order, whether in terms of time, space, sorting, or any other way.

[0059] In the description of the present invention, it should be noted that unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0060] Embodiment 1:

[0061] A three - element adaptive non - linear tuned vibration absorber system of a displacement - steering and efficiency - enhancing mechanism type, as Figure 1 shown, includes a dynamic vibration absorption unit, a tuning unit, and a displacement - steering and efficiency - enhancing mechanism. The dynamic vibration absorption unit includes a control box 1 and an inertance container. The control box 1 is connected to the inertance container through the displacement - steering and efficiency - enhancing mechanism. The inertance container is connected to the controlled structure 19. The control box 1 is connected to the controlled structure 19 through the tuning unit;

[0062] Inside the control box 1, there is a liquid 2, as well as a first fixed semi - magnetic disk 3, a semi - magnetic piston disk 5, and a second fixed semi - magnetic disk 7. One side of the displacement - steering and efficiency - enhancing mechanism is connected to the semi - magnetic piston disk 5 through a transmission rod 8, and the other side is connected to the controlled structure 19 through the inertance container. The semi - magnetic piston disk 5 is arranged between the first fixed semi - magnetic disk 3 and the second fixed semi - magnetic disk 7. An annular piston disk 6 is arranged on the periphery of the semi - magnetic piston disk 5. The semi - magnetic piston disk 5 and the annular piston disk 6 move vertically between the first fixed semi - magnetic disk 3 and the second fixed semi - magnetic disk 7. When the control box 1 moves horizontally relative to the controlled structure 19, the liquid 2 inside the control box 1 sloshes to generate liquid - motion convection mass;

[0063] The displacement steering and efficiency enhancement mechanism includes four rhombus structures and articulated rods 9 connected to each other. The connection ends of the articulated rods 9 are articulated; the displacement steering and efficiency enhancement mechanism is used to steer the horizontal movement of the control box 1 relative to the controlled structure 19 and amplify it into the vertical movement of the articulated points 10 at the upper and lower ends of the displacement steering and efficiency enhancement mechanism.

[0064] The articulated point 10 at the left end of the displacement steering and efficiency enhancement mechanism is connected to the controlled structure 19 through the first connecting rod 12, and the articulated point 10 at the right end is connected to the control box 1 through the first connecting rod 12.

[0065] The connection end of the first connecting rod 12 with the controlled structure 19 is rigidly connected, and the connection end with the displacement steering and efficiency enhancement mechanism is articulated.

[0066] The articulated point 10 at the upper end of the displacement steering and efficiency enhancement mechanism is connected to the transmission rod 8 through the slide rail 20. The transmission rod 8 is connected to the semi-magnetic piston disk 5. The semi-magnetic piston disk 5 is composed of two permanent magnets with different magnetic poles up and down. The upper part is the S (N) pole, and the lower part is the N (S) pole.

[0067] An annular piston disk 6 is arranged on the periphery of the semi-magnetic piston disk 5, and there is a certain gap between the annular piston disk 6 and the control box 1.

[0068] A second fixed semi-magnetic disk 7 is fixed at the bottom of the control box 1. The second fixed semi-magnetic disk 7 is composed of two permanent magnets with different magnetic poles up and down. The upper part is the S (N) pole, and the lower part is the N (S) pole.

[0069] A first fixed semi-magnetic disk 3 is also fixed in the middle of the control box 1. The first fixed semi-magnetic disk 3 is composed of two permanent magnets with different magnetic poles up and down. The upper part is the S (N) pole, and the lower part is the N (S) pole.

[0070] The first fixed semi-magnetic disk 3 is connected to the side wall of the control box 1 through the fixing rod 4 to ensure its relative position with the control box 1 remains unchanged.

[0071] The vertical movement of the articulated point 10 at the upper end causes the synchronous vertical movement of the semi-magnetic piston disk 5 inside the control box 1 to generate non-linear electromagnetic negative stiffness. The vertical movement of the semi-magnetic piston disk 5 drives the pulsed liquid mass in the control box 1 to shake and generates non-linear hydrodynamic damping.

[0072] The articulated point 10 at the lower end of the displacement steering and efficiency enhancement mechanism is connected to the inertance through the slide rail 20. In this embodiment, the inertance is preferably a gear-rack type inertance.

[0073] The rack and pinion type inertance includes a rack 11, a first gear 13, a second gear 14 and a disc 15. The hinge point at the lower end of the displacement steering and efficiency increasing mechanism is connected to the rack 11 through a slide rail 20. The rack 11 meshes with the first gear 13, the first gear 13 meshes with the second gear 14, the second gear 14 is rigidly connected to the disc 15 and rotates coaxially. The axis of the first gear 13 is connected to the controlled structure 19 through a second connecting rod 16, and the axes of the second gear 14 and the disc 15 are connected to the controlled structure 19 through a second connecting rod 16;

[0074] In this embodiment, the diameter of the first gear 13 is larger than that of the second gear 14;

[0075] The slide rail 20 includes a semi-enclosed structural plate member. The transmission rod 8 or the inertance container extends out of the semi-enclosed structural plate member. A slide plate is arranged inside the semi-enclosed structural plate member. The upper and lower sides of the slide plate are respectively in contact and sliding connection with the plate member through two pairs of rollers;

[0076] The vertical movement of the hinge point 10 at the lower end causes the internal rotation of the inertance container, thereby generating a significant inertance coefficient and a non-linear inertial control force;

[0077] The tuning unit includes a vibration isolation support 17. The control box 1 is connected to the controlled structure 19 through the vibration isolation support 17; The vibration isolation support 17 is used to support the control box 1 and can realize the adjustment of the tuning stiffness and additional damping in the tuning unit for the connection between the control box 1 and the controlled structure 19;

[0078] The vibration isolation support 17 is connected to the controlled structure 19 through a vibration isolation pier 18; The vibration isolation pier 18 is a non-essential component and can be not used if the height is sufficient.

[0079] It should be noted that the device of the present invention is not limited to the form in the figure;

[0080] Among them, the vibration isolation support 17 can adopt a friction pendulum support, a rubber support, a flat sliding support, etc., and is preferably a friction pendulum support in this embodiment;

[0081] The cross-section of the control box 1 can be circular or rectangular, and is preferably rectangular in this embodiment;

[0082] The liquid 2 can be selected according to actual needs, such as water, silicone oil, etc., and is preferably water in this embodiment;

[0083] The non-linear electromagnetic negative stiffness generated by the interaction between the semi-magnet piston disc 5 and the fixed semi-magnet disc can be adjusted by changing the magnetism of the magnet and the distance between the magnets;

[0084] The hydrodynamic damping generated by the annular piston disc 6 shearing the liquid can be adjusted by changing the size of the gap or opening holes on the annular piston disc 6;

[0085] The amplification effect of the displacement steering and boosting mechanism on displacement can be adjusted by adjusting the initial angle of the articulated rod 9;

[0086] The inertance coefficient (apparent mass) of the inertor at the lower part of the displacement steering and boosting mechanism can be adjusted by adjusting the radii of the first gear 13, the second gear 14, and the disk 15;

[0087] The gear-rack type inertor can also be replaced with other types of inertors, such as ball screw type inertors, etc.

[0088] The usage method of the above displacement steering and boosting mechanism type three-element adaptive nonlinear tuned vibration absorber system is as follows:

[0089] When the system is working, the control box 1 and the controlled structure 19 have a relative horizontal displacement, and the liquid 2 inside the control box 1 sloshes to generate a hydrodynamic mass;

[0090] The displacement steering and boosting mechanism at the lower part of the control box 1 steers and boosts this relative horizontal displacement into an amplified vertical displacement, and transmits the amplified vertical displacement to the semi-magnetic piston disk 5 through the slide rail 20 and the transmission rod 8. At the same time, the amplified vertical displacement is transmitted to the first gear 13 through the slide rail 20 and the rack 11, causing the first gear 13 to rotate;

[0091] In the control box 1, the semi-magnetic piston disk 5 moves vertically between the second fixed semi-magnetic disk 7 at the bottom of the control box 1 and the first fixed semi-magnetic disk 3 in the middle of the control box 1, and according to the principle of electromagnetism, a non-linear electromagnetic negative stiffness will be generated;

[0092] At the same time, when the semi-magnetic piston disk 5 moves vertically, the liquid 2 continuously flows through the gap between the annular piston disk 6 and the control box 1, and the semi-magnetic piston disk 5 shears the liquid 2 inside the control box 1 to generate a non-linear hydrodynamic damping;

[0093] At the lower part of the displacement steering and boosting mechanism, the rack 11 drives the first gear 13 to rotate, and then transmits it to the second gear 14 to achieve amplification of the rotational motion;

[0094] At this time, the disk 15 will rotate coaxially with the second gear 14 to generate an inertance coefficient.

[0095] Embodiment 2:

[0096] A displacement steering and boosting mechanism type three-element adaptive nonlinear tuned vibration absorber system, as Figure 2As shown, it is basically the same as Embodiment 1, except that the gear-rack type inertance is replaced with a ball screw type inertance. The ball screw type inertance includes a screw rod 21, a nut 22, and a flywheel 23. The hinge point at the lower end of the displacement steering and efficiency increasing mechanism is connected to the screw rod 21 through a slide rail 20. The screw rod 21 extends into the nut 22. The nut 22 is rigidly connected to the flywheel 23 and rotates coaxially. The nut 22 passes through a restraint ring 24. The translational degree of freedom of the nut 22 relative to the restraint ring 24 is constrained, and the rotational degree of freedom is not constrained. The restraint ring 24 is connected to the controlled structure 19 through a third connecting rod 25;

[0097] The restraint ring 24 includes a pair of thrust bearings arranged up and down and a rigid outer sleeve. A metal step is provided on the outer surface of the nut 22. The metal step is constrained in the middle of the thrust bearings arranged up and down. The thrust bearings are used to ensure that the nut 22 does not undergo vertical displacement during operation and can only rotate. The thrust bearings arranged up and down are wrapped by the rigid outer sleeve. The rigid outer sleeve is connected to the controlled structure 19 through a third connecting rod 25 and is used to constrain the horizontal and vertical displacements of the thrust bearings and the nut 22.

[0098] The inertance coefficient (apparent mass) of the inertance in the lower part of the displacement steering and efficiency increasing mechanism can be adjusted by adjusting the pitch of the screw rod 21 and the radius of the flywheel 23.

[0099] The usage method of the above displacement steering and efficiency increasing mechanism type three-element adaptive nonlinear tuned vibration absorber is basically the same as that of Embodiment 1, except that:

[0100] The displacement steering and efficiency increasing mechanism at the lower part of the control box 1 steers and increases the relative horizontal displacement into an amplified vertical displacement, and transmits the amplified vertical displacement to the semi-magnetic piston disc 5 through the slide rail 20 and the transmission rod 8. At the same time, the amplified vertical displacement is transmitted to the nut 22 through the slide rail 20 and the screw rod 21, causing the nut 22 to rotate;

[0101] At the lower part of the displacement steering and efficiency increasing mechanism, the screw rod 21 drives the nut 22 to rotate and realizes the amplification of the vertical displacement to the rotational motion;

[0102] At this time, the flywheel 23 will rotate coaxially with the nut 22 to generate an inertance coefficient.

[0103] The present invention innovates the implementation form of the mechanism in which the additional pulse mass in the non-linear liquid mass unit is connected in parallel with the inertance unit, forming a mass unit based on liquid mass and inertance coefficient, a tuning unit based on non-linear electromagnetic negative stiffness unit and vibration isolation support, and a damping unit based on additional non-linear hydrodynamic damping unit and vibration isolation support damping. By innovating the collaborative working mode of the three-element unit, a mechanism solution for utilizing the total mass of the tuned liquid is provided, achieving an adaptive vibration damping effect depending on the deformation amplitude of the non-linear tuned vibration absorption system, that is, providing enhanced hydrodynamic damping, electromagnetic negative stiffness and inertance parallel control force under the control requirements of large displacement and high acceleration, and realizing the adaptive vibration control of engineering structures under multi-level and multi-source excitations.

[0104] The above description of the embodiments is to enable those of ordinary skill in the art to understand and use the invention. It is obvious that those skilled in the art can easily make various modifications to these embodiments and apply the general principles described herein to other embodiments without creative efforts. Therefore, the present invention is not limited to the above embodiments, and the improvements and modifications made by those skilled in the art without departing from the scope of the present invention according to the disclosure of the present invention should be within the protection scope of the present invention.

Claims

1. A displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system, characterized in that: The system comprises a power vibration absorption unit, a tuning unit and a displacement steering enhancement mechanism, the power vibration absorption unit comprises a control box (1) and an inertia container, the control box (1) is connected to the inertia container via the displacement steering enhancement mechanism, the inertia container is connected to a controlled structure (19), and the control box (1) is connected to the controlled structure (19) via the tuning unit; The control box (1) is provided with a liquid (2), a first fixed semi-magnetic disk (3), a semi-magnetic piston disk (5), and a second fixed semi-magnetic disk (7); one side of the displacement steering enhancement mechanism is connected to the semi-magnetic piston disk (5) via a transmission rod (8), and the other side is connected to the controlled structure (19) via an inertial container; the semi-magnetic piston disk (5) is arranged between the first fixed semi-magnetic disk (3) and the second fixed semi-magnetic disk (7); an annular piston disk (6) is arranged on the periphery of the semi-magnetic piston disk (5); the semi-magnetic piston disk (5) and the annular piston disk (6) move vertically between the first fixed semi-magnetic disk (3) and the second fixed semi-magnetic disk (7); The displacement steering enhancement mechanism comprises four rhombus-shaped hinged rods (9) connected to each other, wherein the connecting ends of the hinged rods (9) are hinged; The inertia container includes a gear rack type inertia container or a ball screw type inertia container; The tuning unit comprises a vibration isolation support (17), and the control box (1) is connected to the controlled structure (19) via the vibration isolation support (17).

2. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: The hinge point (10) at one end of a pair of ends of the displacement steering enhancement mechanism is connected to the transmission rod (8) via a slide rail (20), and the hinge point (10) at the other end is connected to the inertia container via the slide rail (20); The hinge point (10) at one of the two ends of the other opposite side is connected to the controlled structure (19) via a first connecting rod (12), and the hinge point (10) at the other end is connected to the control box (1) via the first connecting rod (12).

3. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: A certain gap is left between the annular piston disc (6) and the control box (1).

4. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: The first fixed half-magnetic disk (3), the half-magnetic piston disk (5) and the second fixed half-magnetic disk (7) all comprise two upper and lower permanent magnets with different magnetic poles.

5. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: The fixed half-magnetic disk is connected to the control box (1) via a fixed rod (4).

6. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: The rack and pinion type inertia capacity comprises a rack (11), a first gear (13), a second gear (14) and a disc (15); a hinge point at the other end of a pair of ends of the displacement steering enhancement mechanism is connected to the rack (11) via a slide rail (20); the rack (11) meshes with the first gear (13); the first gear (13) meshes with the second gear (14); and the second gear (14) and the disc (15) are rigidly connected and coaxially rotate.

7. The displacement steering enhancement mechanism type three-dimensional adaptive nonlinear tuning vibration absorption system according to claim 1 is characterized in that: The ball screw type inertia capacity comprises a screw (21), a nut (22) and a flywheel (23); a hinge point at the other end of a pair of ends of the displacement steering enhancement mechanism is connected to the screw (21) via a slide rail (20); the screw (21) extends into the nut (22); the nut (22) and the flywheel (23) are rigidly connected and coaxially rotated; the nut (22) passes through a restraining ring (24).

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