Electromagnetic self-adjusting dynamic anti-resonance vibration isolation system

Abstract

An electromagnetic self-regulating dynamic anti-resonance vibration isolation system comprises a load platform and a base platform arranged relative to each other. Several elastic elements and lever-type inertia amplification mechanisms are positioned between the load platform and the base platform. The lever-type inertia amplification mechanisms are connected to a controller system to receive control signals. The system utilizes the amplifying effect of lever coupling to amplify the output of a relatively small added mass and an electromagnetically controllable device. This system achieves an output comparable to the greater system stiffness with minimal mass loss and energy consumption, thereby achieving a wideband, adjustable anti-resonance vibration reduction stopband and enabling low-frequency vibration reduction under varying operating conditions.

Description

Technical Field

[0001] The present invention relates to a technology in the field of low-frequency engineering vibration reduction, in particular to an electromagnetic self-regulating dynamic anti-resonance vibration isolation system. Background Art

[0002] The impact of low-frequency vibration is widespread in engineering practice. Without vibration reduction design, excessive vibration can trigger a series of engineering problems. Current vibration reduction technologies can be divided into three main categories: passive, semi-active, and active. Traditional passive vibration reduction technology is widely used due to its simple structure and high reliability. However, its structural parameters require pre-design and it cannot provide effective vibration reduction when the external excitation frequency changes. Compared to passive vibration reduction, active vibration reduction technology achieves vibration reduction by controlling the actuator's output of active force through a controller, thus achieving better vibration reduction under varying operating conditions. However, active vibration reduction generally consumes a lot of external energy and has relatively high design, manufacturing, and maintenance costs. Semi-active vibration reduction technology lies between passive and active vibration reduction. It generally achieves better vibration reduction by changing the stiffness or damping characteristics of the vibration reduction device, thus being able to adapt to changing operating conditions and consuming less energy than active control. Semi-active control generally involves adjusting the stiffness or damping parameters of a vibration isolation system. Depending on the isolation principle, semi-active vibration reduction technologies can be divided into two categories: the first directly controls the stiffness or damping of a spring-damper vibration isolation system; the second, based on the anti-resonance principle, uses semi-active vibration absorbers to control the stiffness, damping, or inertia of an attached vibration reduction device. The actuators for both types of semi-active vibration reduction technologies are largely similar, employing controllable devices such as electromagnetics, magnetorheological devices, memory alloys, or mechanical adjustment devices. The first type of semi-active vibration reduction technology controls the stiffness or damping of the system. Controlling damping reduces the amplitude of the system's resonant peak without affecting the vibration reduction effect at high frequencies; controlling stiffness shifts the position of the system's resonant frequency, shifting the resonant peak away from the excitation frequency. The second type of semi-active vibration reduction technology utilizes an attached vibration reduction device to generate an anti-resonance stopband at a specific frequency. By modifying the characteristics of the attached device, the anti-resonance stopband is widened and position-adjustable, thereby achieving broadband vibration reduction. The first type of semi-active vibration reduction technology requires the resonant frequency to be significantly lower than the excitation frequency to achieve excellent vibration reduction, thus having limitations in low-frequency vibration reduction. Semi-active vibration absorbers can achieve satisfactory vibration reduction at low frequencies, but they also suffer from issues such as excessive added mass and a narrow anti-resonance vibration reduction stopband, which can lead to control instability.

[0003] Existing vibration reduction actuator technology couples a controllable damping actuator with a controllable negative stiffness actuator, using the controllable damping actuator to control the resonance peak amplitude, and the controllable negative stiffness actuator to control the position of the system's resonance frequency, moving it away from the excitation frequency. However, for low-frequency excitation, the controllable negative stiffness actuator needs to output a large negative stiffness to compensate for the system's positive stiffness, reducing the system's resonance frequency to a lower position and achieving an excellent vibration reduction effect. A larger negative stiffness means a larger control energy consumption, and for situations where the positive stiffness is large, the controllable negative stiffness actuator is required to provide an output negative stiffness of the same magnitude. The resulting weight, size, and input energy consumption of the controllable negative stiffness actuator are unacceptable in some engineering applications. Summary of the Invention

[0004] In response to the above-mentioned defects in the prior art, the present invention proposes an electromagnetic self-regulating dynamic anti-resonance vibration isolation system, which utilizes the amplifying effect of lever coupling to amplify the smaller additional mass and the output of the electromagnetic controllable device, so that the output of the electromagnetic controllable device reaches an order of magnitude equivalent to the larger system stiffness at a lower mass cost and energy consumption, thereby obtaining a wide-band adjustable anti-resonance vibration reduction stopband and realizing low-frequency vibration reduction under variable working conditions.

[0005] The present invention is achieved through the following technical solutions:

[0006] The present invention relates to an electromagnetic self-regulating dynamic anti-resonance vibration isolation system, comprising: a load platform and a base platform arranged opposite to each other, wherein: a plurality of elastic elements and a plurality of lever-type inertia amplification mechanisms are arranged between the load platform and the base platform, and the lever-type inertia amplification mechanisms are connected to a controller system to receive control signals.

[0007] The lever-type inertia amplification mechanism includes: a first connecting seat and a second connecting seat respectively arranged on the load platform and the base platform, and a vibration-damping lever with one end rotatably connected to the second connecting seat, wherein: a permanent magnet is provided on the other end of the vibration-damping lever, and a plurality of electromagnetic controllable units are provided at positions corresponding to the permanent magnets on the base platform.

[0008] The electromagnetic controllable unit includes: a connecting base and a pair of coil windings arranged inside it, wherein: the first and second coil windings are respectively arranged at the top and bottom of the inner side of the connecting base and the centers of the two are facing the permanent magnet, and the first and second coil windings are respectively connected to the controller system.

[0009] The vibration-damping lever, the first connecting seat, the second connecting seat and the connecting base are all made of low-density, high-strength materials, which include but are not limited to titanium alloys, so as to further reduce the mass cost of the additional vibration isolation device.

[0010] The elastic element and the load platform, as well as the base platform and the elastic element are all fixedly connected to ensure that the load platform does not rotate.

[0011] The first connecting seat is preferably arranged at the center of the load platform, and the corresponding elastic elements are distributed in a centrally symmetrical manner.

[0012] The lever-type inertia amplification mechanism and the electromagnetic controllable unit are preferably symmetrically distributed between the load platform and the base platform. By superimposing the forces of multiple lever-type inertia amplification mechanisms, the force acting on the load platform is the sum of multiple coupled electromagnetic lever-type inertia amplification mechanisms, which can effectively reduce the size of a single lever-type inertia amplification mechanism.

[0013] Technical Effects

[0014] The present invention achieves adjustable anti-resonance vibration reduction stopband by coupling an electromagnetic lever inertia amplification mechanism. By coupling an electromagnetic controllable unit with the lever inertia amplification mechanism, the output of the relatively small added mass and electromagnetic controllable device is amplified, enabling the output of the electromagnetic controllable device to reach a level comparable to a larger system stiffness at a reduced mass cost and energy consumption. By varying the input current of the electromagnetic controllable unit, the force acting between the permanent magnet and the electromagnetic controllable unit can be varied. After amplification by the lever inertia amplification mechanism, the force acting on the load platform is amplified, thereby enabling low-frequency vibration control of large equipment using a relatively small electromagnetic controllable device. Furthermore, the lever inertia amplification mechanism also increases the adjustable bandwidth. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is a schematic diagram of the present invention;

[0016] Figure 2 It is a schematic diagram of the structure of the present invention;

[0017] Figure 3 Schematic diagram of electromagnetic controllable unit;

[0018] Figure 4 is the displacement transfer rate under different excitation amplitudes of the embodiment;

[0019] Figure 5 This is a diagram showing the vibration control effect under different input currents in the embodiment;

[0020] Figure 6 is the relationship between the adjustable bandwidth and the lever length ratio α of the embodiment;

[0021] In the figure: 1 load platform, 2 base platform, 3 elastic element, 4 lever-type inertia amplification mechanism, 5 permanent magnet, 6 electromagnetic controllable unit, 7 controller system, 8 sensor, 9 damping lever, 10 first connecting base, 11 second connecting base, 12 first coil winding, 13 second coil winding, 14 connecting base. DETAILED DESCRIPTION

[0022] like Figure 1-Figure 3 As shown, this embodiment relates to an electromagnetic self-regulating dynamic anti-resonance vibration isolation system, including: a load platform 1 and a base platform 2 arranged relatively to each other, wherein: an elastic element 3 and a lever-type inertia amplification mechanism 4 are provided between the load platform 1 and the base platform 2, and the lever-type inertia amplification mechanism 4 is connected to a controller system 7 to receive a control signal.

[0023] The lever-type inertia amplification mechanism 4 includes: a first connecting seat 10 and a second connecting seat 11 respectively arranged on the load platform 1 and the base platform 2, and a damping lever 9 with one end rotatably connected to the second connecting seat 11, wherein: a permanent magnet 5 is provided on the other end of the damping lever 9, and an electromagnetic controllable unit 6 is provided at the position corresponding to the permanent magnet 5 on the load platform 1 and the base platform 2.

[0024] The electromagnetic controllable unit 6 includes: a connecting base 14 and a pair of coil windings 12 and 13 arranged inside it, wherein: the first and second coil windings 12 and 13 are respectively arranged at the top and bottom of the inner side of the connecting base 14 and the centers of the two are facing the permanent magnet 5, and the first and second coil windings 12 and 13 are respectively connected to the controller system 7.

[0025] The load platform 1 and / or the base platform 2 are further provided with a plurality of sensors 8 connected to the controller system 7 for collecting excitation signals.

[0026] The controller system 7 collects the vibration signal of the sensor 8 and performs analysis and processing to obtain the excitation frequency of the base platform 2 , and then outputs the control signal to the first and second coil windings 12 , 13 .

[0027] The load platform 1 is connected to the vibration-damped equipment. When the base platform 2 is subjected to vibration excitation, the sensor 8 transmits the collected signal to the controller system 7. The controller system 7 outputs the control signal to the electromagnetic controllable unit 6 after processing by a specific algorithm, thereby changing the magnitude of the input current of the electromagnetic controllable unit 6. The first coil winding 12 and the second coil winding 13 generate an induced magnetic field, which interacts with the magnetic field of the permanent magnet 5, thereby changing the equivalent stiffness between the permanent magnet 5 and the electromagnetic controllable unit 6. Through the action of the lever-type inertia amplification mechanism 4, the equivalent stiffness of the entire system is changed, thereby achieving a self-adjusting vibration reduction effect.

[0028] The working principle of the present invention is as follows: When the load platform 1 is connected to the vibration-damped device with a mass of m, the base platform 2 is connected to the excitation source, the stiffness of the elastic element is k, L1 is the length between the hinge point of the lever and the first connecting seat 10 and the hinge point of the second connecting seat 11, L2 is the length between the free end of the lever and the hinge point of the lever and the second connecting seat 11, m1 is the mass of the permanent magnet 5, and x1, x2 and x3 are the absolute displacements of the excitation source, the vibration-damped device and the permanent magnet, respectively. The force between the first and second coil windings 12 and 13 and the permanent magnet 5 generates a nonlinear equivalent stiffness k that is related to the input current i. eq =β0(i)+β2(i)(x2-x1) 2 +β4(i)(x2-x1) 4 The lever-type inertia amplification mechanism 4 will introduce an amplification ratio When the lever moves at a small angle and does not bend, the kinetic energy of the system is obtained. and potential energy

[0029] The dynamic equation of the system is obtained from the Lagrange equation: Then we can get the resonant frequency of the system and antiresonance frequency

[0030] When the amplification ratio α of the lever-type inertia amplification mechanism 4 is greater than 1, the effective mass m1 of the permanent magnet 5 and the equivalent stiffness k caused by the lever-type inertia amplification mechanism 4 are eq At the same time, it plays an amplifying role. When α>>1, the smaller equivalent stiffness k eq The stiffness k of the elastic element can be compensated.

[0031] According to the anti-resonance frequency, the generalized adjustable bandwidth under different currents i1 and i2 is obtained That is, increasing the amplification ratio α also has the effect of widening the generalized adjustable bandwidth in the present invention.

[0032] Compared to existing technologies, the present invention simultaneously amplifies the effective mass of the permanent magnet 5 and the electromagnetically controllable unit 6 by placing them simultaneously at the free end of the lever-type inertial amplification mechanism 4. This amplifies both the effective mass of the permanent magnet 5 and the electromagnetic force of the electromagnetically controllable unit 6, thereby achieving an adjustable low-frequency anti-resonance vibration reduction stopband with minimal mass penalty and low energy consumption. Simultaneously, the lever-type inertial amplification mechanism 4 amplifies the relative displacement between the electromagnetically controllable unit 6 and the permanent magnet 5, allowing the nonlinear electromagnetic force between the electromagnetically controllable unit 6 and the permanent magnet 5 to reduce the amplitude at the system's resonant frequency.

[0033] The above-mentioned specific implementation can be partially adjusted in different ways by those skilled in the art without departing from the principles and purpose of the present invention. The scope of protection of the present invention shall be based on the claims and shall not be limited by the above-mentioned specific implementation. All implementation schemes within its scope shall be subject to the constraints of the present invention.

Claims

1. An electromagnetic self-regulating dynamic anti-resonance vibration isolation system, characterized in that: include: A load platform and a base platform are arranged opposite to each other, wherein: a plurality of elastic elements and a plurality of lever-type inertia amplification mechanisms are arranged between the load platform and the base platform, and the lever-type inertia amplification mechanisms are connected to a controller system to receive control signals; The lever-type inertia amplification mechanism includes: a first connecting seat and a second connecting seat respectively arranged on the load platform and the base platform; and a vibration-damping lever having one end rotatably connected to the second connecting seat. A permanent magnet is provided on the other end of the vibration-damping lever, and a plurality of electromagnetically controllable units are provided at positions corresponding to the permanent magnets on the base platform. The lever-type inertia amplification mechanism compensates for the stiffness of the elastic element by generating an equivalent stiffness of the effective mass of the permanent magnet and the electromagnetically controllable units. The electromagnetic controllable unit includes: a connection base and a pair of coil windings arranged inside the connection base, wherein: the first and second coil windings are respectively arranged at the top and bottom of the inner side of the connection base and the centers of the two are facing the permanent magnet, and the first and second coil windings are respectively connected to the controller system; The vibration-damping lever, the first connecting seat, the second connecting seat and the connecting base are all made of low-density, high-strength materials; The first connecting seat is arranged at the center of the load platform, and the corresponding elastic elements are distributed in a centrally symmetrical manner; The lever-type inertia amplification mechanism and the electromagnetic controllable unit are symmetrically distributed between the load platform and the base platform. By superimposing the forces of multiple lever-type inertia amplification mechanisms, the force acting on the load platform is the sum of the multiple coupled electromagnetic lever-type inertia amplification mechanisms, which can effectively reduce the size of a single lever-type inertia amplification mechanism. The compensation mentioned above specifically refers to: when the load platform and the mass are The vibration-damped device is connected to the base platform, the excitation source is connected to the base platform, and the force between the first and second coil windings and the permanent magnet produces a nonlinear equivalent stiffness related to the input current i. , where: the stiffness of the elastic element is , is the length between the lever and the hinge point of the first connecting seat and the hinge point of the second connecting seat, is the length between the free end of the lever and the hinge point between the lever and the second connecting seat, is the mass of the permanent magnet, 、 and are the absolute displacements of the excitation source, the device to be damped, and the permanent magnet respectively; The amplification ratio of the lever-type inertia amplification mechanism is When the lever moves at a small angle and does not bend, the kinetic energy of the system is obtained. and potential energy ; The dynamic equation of the anti-resonance vibration isolation system is: , , and then the resonant frequency of the system is obtained and antiresonance frequency ; When the load platform and mass are The damped equipment is connected to the base platform, the excitation source is connected to the base platform, and the stiffness of the elastic element is , is the length between the lever and the hinge point of the first connecting seat and the hinge point of the second connecting seat, is the length between the free end of the lever and the hinge point between the lever and the second connecting seat, is the mass of the permanent magnet, 、 and are the absolute displacements of the excitation source, the damped device, and the permanent magnet respectively; the force between the first and second coil windings and the permanent magnet produces a nonlinear equivalent stiffness related to the input current i ; The lever-type inertia amplification mechanism will introduce an amplification ratio When the lever moves at a small angle and does not bend, the kinetic energy of the system is obtained. and potential energy .

Images