A vibration isolation device

Abstract

This invention discloses a vibration isolation device, relating to the field of vibration isolation control. It comprises a first-level passive vibration isolation unit consisting of a lower plate and lower elastic supports, a middle plate, an inertial reaction force vibration suppression module, and an upper elastic supports, forming a second-level vibration isolation unit. The inertial reaction force vibration suppression module consists of an actuator, a mass block, and quasi-zero stiffness legs. Sensors for acquiring external vibrations and outputting feedback signals are installed on the middle plate. A controller receives the feedback signals and sends action commands to the actuator. The vibration isolation device provided by this invention employs a dual-layer dynamic architecture, deeply integrating a magnetic quasi-zero stiffness mechanism with electromagnetic active control. It aims to completely eliminate the dependence of traditional quasi-zero stiffness systems on the weight of specific equipment, achieve efficient blocking of excitation forces across the entire frequency band under broad loads, and fundamentally solve the problem of dynamic instability in the resonance region of the system.

Description

Technical Field

[0001] This invention relates to the field of vibration isolation control, and in particular to a vibration isolation device. Background Technology

[0002] With the continuous evolution of fields such as integrated circuit manufacturing, ultra-precision optical processing, and life science detection, high-end precision instruments have placed extremely high demands on the micro-vibration control indicators of their service environment. Traditional linear passive vibration isolation technology is constrained by the inherent physical contradiction between static load-bearing capacity and dynamic vibration isolation efficiency, making it difficult to achieve low-frequency vibration isolation while ensuring load-bearing capacity. Although pure active vibration isolation systems have the ability to suppress low-frequency resonance, they face limitations such as high energy consumption, complex control architecture, and lack of passive protection mechanisms in the event of power failure.

[0003] While quasi-zero stiffness vibration isolation technology developed in recent years has decoupled static and dynamic stiffness to some extent through parallel negative stiffness mechanisms, it has revealed significant limitations in practical engineering applications. Existing quasi-zero stiffness mechanisms typically directly bear the static load of external vibration source equipment. This force transmission configuration makes the nonlinear negative stiffness operating origin of the system extremely sensitive to the load mass. Even a slight increase or decrease in equipment weight will force the negative stiffness mechanism to deviate from its static equilibrium position, leading to complete failure of the quasi-zero stiffness characteristics. Therefore, traditional quasi-zero stiffness systems lack engineering versatility and adaptability to equipment of different masses. Furthermore, existing quasi-zero stiffness systems mostly exhibit single-layer dynamic characteristics, resulting in limited ability to block high-frequency mechanical noise and acoustic disturbances.

[0004] To further broaden the vibration isolation frequency band, double-layer vibration isolation architectures, thanks to the intermediate mass effect, exhibit excellent force transmissibility attenuation characteristics in the high-frequency band, and have become an important development trend in the field of micro-vibration control. However, existing double-layer vibration isolation platforms inevitably evolve with dual resonance peaks, which can easily lead to deterioration of dynamic stability in the low-frequency band; in addition, the spatial layout of sensors and actuators in traditional designs is often relatively discrete, which can easily induce control time delay and multi-axial motion coupling interference. Summary of the Invention

[0005] The purpose of this invention is to provide a vibration isolation device to solve the problems existing in the prior art. It adopts a dual-layer dynamic architecture, a magnetic quasi-zero stiffness mechanism and electromagnetic active control, which are deeply integrated to completely get rid of the dependence of traditional quasi-zero stiffness systems on the weight of specific equipment, achieve efficient blocking of full-band excitation force under a wide range of loads, and fundamentally solve the problem of dynamic instability of the system in the resonance zone.

[0006] To achieve the above objectives, the present invention provides the following solution: This invention provides a vibration isolation device, comprising a lower plate, a middle plate, and an upper plate arranged sequentially and parallel from bottom to top. A lower elastic support member is disposed on the lower plate and supports the middle plate. The elastic extension direction of the lower elastic support member is perpendicular to the middle plate. The lower plate and the lower elastic support member constitute a first-stage passive vibration isolation unit. An actuator is disposed on the middle plate. The line connecting the center of gravity of the actuator and the geometric center of the surface of the middle plate is perpendicular to the middle plate. The actuator includes an active resistance component. The resistance release direction of the active resistance component is perpendicular to the upper plate. A mass block that does not support the upper plate is disposed at the top of the active resistance component. The line connecting the center of gravity of the mass block and the center of gravity of the actuator is perpendicular to the middle plate. A quasi-zero stiffness support leg that does not support the upper plate is provided. On the middle layer plate, the quasi-zero stiffness outrigger includes a series of positive stiffness telescopic members and a passive resistance assembly. The resistance release directions of the positive stiffness telescopic members and the passive resistance assembly coincide and are parallel to the resistance release direction of the active resistance assembly. The telescopic end of the passive resistance assembly is connected to the top of the active resistance assembly. The actuator, the mass block, and the quasi-zero stiffness outrigger constitute an inertial reaction force vibration suppression module. An upper elastic support member is disposed on the middle layer plate and supports the upper layer plate. The elastic telescopic direction of the upper elastic support member is perpendicular to the middle layer plate. The middle layer plate, the inertial reaction force vibration suppression module, and the upper elastic support member constitute a second-level vibration isolation unit. A sensor for collecting external vibrations and outputting feedback signals is disposed on the middle layer plate. The controller receives the feedback signals and sends action commands to the actuator.

[0007] In one embodiment, the actuator includes an actuator base and an actuator top plate. The actuator base is fixedly connected to the middle plate. The active resistance assembly is disposed on the actuator base. The actuator top plate is fixed on the active resistance assembly. The mass block is fixedly disposed on the side of the actuator top plate away from the active resistance assembly.

[0008] In one embodiment, the active resistance assembly includes a permanent magnet assembly and a coil assembly. The permanent magnet assembly is a straight cylinder. The bottom of the permanent magnet assembly is fixed to the actuator base. An insertion cavity matching the coil assembly is provided inside the permanent magnet assembly. An insertion hole communicating with the insertion cavity is opened on the top of the permanent magnet assembly. A first end of the coil assembly is inserted into the permanent magnet assembly through the insertion hole. The second end of the coil assembly is fixedly connected to the top plate of the actuator.

[0009] In one embodiment, the permanent magnet assembly is one of a straight cylindrical cylinder, a straight elliptical cylinder, or a straight prism.

[0010] In one embodiment, the quasi-zero stiffness outrigger includes an outer sleeve, the bottom of which is fixed to the middle plate. A mounting cavity is provided inside the outer sleeve, and an opening communicating with the mounting cavity is formed at the top of the outer sleeve. The positive stiffness telescopic member and the passive resistance assembly are arranged from bottom to top inside the mounting cavity. The bottom end of the positive stiffness telescopic member is fixed to the bottom of the outer sleeve, and the positive stiffness telescopic member abuts against the bottom of the movable part of the passive resistance assembly. The top of the movable part of the passive resistance assembly extends out of the mounting cavity and connects to the actuator top plate.

[0011] In one embodiment, the passive resistance assembly includes an outer hollow magnetic column, an inner hollow magnetic column, and an inner sleeve that serves as a movable part of the passive resistance assembly. The axial orthographic projection shape of the outer hollow magnetic column is consistent with the axial orthographic projection shape of the inner hollow magnetic column. The outer hollow magnetic column is disposed inside the outer sleeve, and the inner hollow magnetic column is disposed on the inner sleeve. The outer sleeve, the outer hollow magnetic column, the inner hollow magnetic column, and the inner sleeve are coaxially arranged. Both the outer and inner hollow magnetic columns are axially magnetized. The inner polarity of the outer hollow magnetic column is the same as the outer polarity of the inner hollow magnetic column. The radial main view projection of the outer hollow magnetic column overlaps with the radial main view projection of the inner hollow magnetic column.

[0012] In one embodiment, the upper edge of the outer hollow magnetic column is flush with the inner edge of the opening, and an annular outer hollow magnetic column fixing member covers the outer hollow magnetic column and the outer sleeve. The inner sleeve passes through the outer hollow magnetic column fixing member. The inner sleeve is made of a magnetically permeable material, and a receiving cavity is provided inside the inner sleeve. An opening communicating with the receiving cavity is opened at the top of the inner sleeve, and the inner hollow magnetic column is disposed in the receiving cavity.

[0013] In one embodiment, the flange portion of the flange bearing is disposed within the actuator top plate. The lower end of the bearing portion of the flange bearing extends downward to abut against the upper surface of the inner hollow magnetic column. The positive stiffness telescopic member is a positive stiffness spring. The bottom of the mounting cavity is provided with a lower fixing boss for connecting the bottom of the positive stiffness spring. The bottom of the inner sleeve is provided with an upper fixing boss for connecting the top of the positive stiffness spring. A guide rod fixed to the bottom of the outer sleeve passes through the bearing portion of the flange bearing, the inner hollow magnetic column, the upper fixing boss, the positive stiffness spring, and the lower fixing boss sequentially from top to bottom. The top of the guide rod is located above the actuator top plate. A limiting member is provided at the top of the guide rod. The size of the limiting member is larger than the inner ring size of the bearing portion of the flange bearing. The bottom of the guide rod is fixed to the bottom of the outer sleeve. The guide rod and the outer sleeve are coaxially arranged.

[0014] In one embodiment, the axial orthographic projection of the outer hollow magnetic column is a circular ring or a regular polygonal ring. When the axial orthographic projection of the outer hollow magnetic column is a regular polygonal ring, the plane formed by any side edge of the outer hollow magnetic column and the side edge of the nearest inner hollow magnetic column passes through the axis of the outer sleeve. The shape of the axial orthographic projection of the outer sleeve is consistent with the shape of the axial orthographic projection of the outer hollow magnetic column, the shape of the axial orthographic projection of the inner sleeve is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column, and the shape of the axial orthographic projection of the guide rod is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column. The outer hollow magnetic column and the inner hollow magnetic column are an integral structure or a spliced ​​structure.

[0015] In one embodiment, the lower plate, the middle plate, and the upper plate are circular plates of the same size. The lower elastic support is arranged with equal curvature along the edge of the lower plate, and the upper elastic support is arranged with equal curvature along the edge of the middle plate. The number of lower and upper elastic supports is the same and they are arranged in a one-to-one correspondence. There are at least three lower elastic supports. The lower and upper elastic supports are one of the following: cylindrical helical springs, air springs, rubber damping blocks, metal rubber pads, or leaf springs. The quasi-zero stiffness support legs are arranged between adjacent upper elastic supports. There is at least one quasi-zero stiffness support leg. When there is more than one, the quasi-zero stiffness support leg is arranged with equal curvature along the edge of the middle plate.

[0016] The present invention achieves the following technical effects compared to the prior art: This invention alters the force transmission path of traditional quasi-zero stiffness mechanisms. The quasi-zero stiffness outriggers do not directly bear the static load of external vibration sources; instead, they independently bear the mass blocks configured within the system. This decoupling design offers two significant advantages: First, it frees the vibration isolation device from the limitation of specific load weights, enabling flexible adaptation and stable bearing of vibration sources of varying masses, greatly improving the device's engineering versatility. Second, through the precise parallel cancellation of the negative stiffness and positive mechanical stiffness of the passive resistance components within the quasi-zero stiffness outriggers, the natural frequency of the second-stage active-passive composite vibration isolation unit is significantly reduced without affecting the external load-bearing capacity. This mechanism breaks through the bottleneck of the traditional vibration isolator's load-bearing capacity and low-frequency performance mutually restricting each other, significantly broadening the effective blocking bandwidth of active vibration isolation in the extremely low-frequency range.

[0017] This invention employs a two-stage dynamic series architecture. The first-stage passive vibration isolation unit enables the system to exhibit significantly superior high-frequency force transmission rate attenuation characteristics compared to a single-layer system, effectively filtering out the leakage of high-frequency excitation energy. Simultaneously, addressing the inherent dual resonance amplification defect of the two-layer vibration isolation architecture, the active drag component in this invention provides real-time active cancellation and transient disturbance compensation for the dynamic excitation force generated by the vibration source. This deep synergy between the active and passive mechanisms not only completely suppresses the excitation force amplification phenomenon at the resonant frequency but also achieves a substantial reduction in the transmission of vibration energy to the foundation and external environment across the entire frequency band.

[0018] The physical architecture of this invention has extremely high compactness and integration. By adopting an integrated configuration with actuators arranged in the center and quasi-zero stiffness legs arranged in the periphery, the transmission path of active control force is significantly shortened, the control response time delay of the system is effectively reduced, and the non-axial motion and multi-degree-of-freedom coupling interference induced by the excitation source during operation are constrained to the maximum extent and avoided, thus significantly improving the overall dynamic stability and long-term reliability of the system under active vibration isolation conditions. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the overall structure of a vibration isolation device according to an embodiment of the present invention; Figure 2 This is a cross-sectional structural diagram of a vibration isolation device according to an embodiment of the present invention; Figure 3 This is a schematic diagram of a quasi-zero stiffness support leg in an embodiment of the present invention; Figure 4 This is a schematic cross-sectional view of a quasi-zero stiffness support leg in an embodiment of the present invention. Figure 5 This is a cross-sectional structural diagram of an actuator according to an embodiment of the present invention.

[0021] The components are as follows: 1. Lower layer plate; 2. Lower layer elastic support; 3. Middle layer plate; 4. Upper layer elastic support; 5. Upper layer plate; 6. Actuator; 61. Actuator base; 62. Permanent magnet assembly; 63. Coil assembly; 64. Actuator top plate; 7. Quasi-zero stiffness support leg; 71. Outer sleeve; 72. Guide rod; 73. Positive stiffness telescopic component; 74. Inner hollow magnetic column; 75. Outer hollow magnetic column; 76. Outer hollow magnetic column fixing component; 77. Inner sleeve; 78. Flange bearing; 79. Limiting component; 8. Mass block. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings of this specification are merely for illustrative purposes to aid those skilled in the art and are not intended to limit the implementation conditions of the invention. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and purpose of the invention, should still fall within the scope of the technical content disclosed in this invention. In the description of this invention, it should be understood that the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are merely for the convenience of describing the invention and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Thus, features defined with "first," "second," etc., may explicitly or implicitly include one or more of those features. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0024] It should also be noted that in the embodiments of this application, the same reference numerals are used to denote the same component or the same part.

[0025] The purpose of this invention is to provide a vibration isolation device to solve the problems existing in the prior art. It adopts a dual-layer dynamic architecture, a magnetic quasi-zero stiffness mechanism and electromagnetic active control, which are deeply integrated to completely get rid of the dependence of traditional quasi-zero stiffness systems on the weight of specific equipment, achieve efficient blocking of full-band excitation force under a wide range of loads, and fundamentally solve the problem of dynamic instability of the system in the resonance zone.

[0026] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0027] like Figures 1 to 5As shown, the present invention provides a vibration isolation device, comprising a lower plate 1, a middle plate 3 and an upper plate 5 arranged in a parallel and aligned manner from bottom to top, a lower elastic support member 2 disposed on the lower plate 1 and supporting the middle plate 3, the elastic extension direction of the lower elastic support member 2 being perpendicular to the middle plate 3, and the lower plate 1 and the lower elastic support member 2 constituting a first-stage passive vibration isolation unit. Actuator 6 is mounted on the middle plate 3. The line connecting the center of gravity of actuator 6 and the geometric center of the surface of the middle plate 3 is perpendicular to the middle plate 3. Actuator 6 includes an active resistance component. The resistance release direction of the active resistance component is perpendicular to the upper plate 5. A mass block 8 that does not support the upper plate 5 is mounted at the top of the active resistance component. The line connecting the center of gravity of mass block 8 and the center of gravity of actuator 6 is perpendicular to the middle plate 3. A quasi-zero stiffness support leg 7 that does not support the upper plate 5 is mounted on the middle plate 3. The quasi-zero stiffness support leg 7 includes a series of positive stiffness telescopic members 73 and a passive resistance component. The resistance release directions of the positive stiffness telescopic members 73 and the passive resistance component coincide and are parallel to the resistance release direction of the active resistance component. The telescopic end of the passive resistance component is connected to the top of the active resistance component. Actuator 6, mass block 8 and quasi-zero stiffness support leg 7 constitute an inertial reaction force vibration suppression module. The upper elastic support 4 is mounted on the middle plate 3 and supports the upper plate 5. The elastic extension and contraction direction of the upper elastic support 4 is perpendicular to the middle plate 3. The middle plate 3, the inertial reaction force vibration damping module, and the upper elastic support 4 constitute the second-level vibration isolation unit. Sensors for collecting external vibrations and outputting feedback signals are installed on the middle plate 3. The controller receives the feedback signals and sends action commands to the actuator 6.

[0028] Working process and principle: Excitation forces are characterized by a mixture of multiple frequencies. While mid-to-high frequency excitation forces have high energy density, they dissipate and decay rapidly, allowing for simple handling with high stiffness and single damping. Low-frequency excitation forces, on the other hand, have low energy density but high total energy, dissipate and decay slowly, requiring more complex absorption structures for proper handling. This invention employs a two-stage dynamic series architecture. The first-stage passive vibration isolation unit is used to initially filter out mid-to-high frequency excitation forces. Its structure is a combination of "grounding + single damping element," which can quickly conduct and absorb mid-to-high frequency excitation forces. The second-stage passive vibration isolation unit is used to eliminate low-frequency excitation forces. After the vibration source device is placed on the upper plate 5, the upper elastic support 4 is compressed and retracts, independently bearing the downward static thrust of the device and transferring this thrust to the middle plate 3, ultimately supported by the lower elastic support 2 and the lower plate 1. Meanwhile, the quasi-zero stiffness support leg 7 on the middle layer plate 3 is unaffected by external loads and only bears the weight of the mass block 8. By adjusting the weight of the mass block 8, the passive resistance component is brought into equilibrium under static load, making the branch supporting the mass block 8 exhibit quasi-zero stiffness characteristics with extremely low dynamic stiffness. When the equipment generates complex dynamic excitation forces during operation, this vibration energy is transmitted downward to the middle layer plate 3 through the upper elastic support 4. At this time, the sensor captures the vibration state of the middle layer plate 3 in real time, and the controller sends an action command to the actuator 6 accordingly. The active resistance component then drives the upper mass block 8 to generate precise dynamic acceleration motion. Utilizing the inertial effect of the mass block 8, a dynamic active control force of equal magnitude and opposite direction is applied to the middle layer plate 3. This active control force directly and precisely cancels the excitation force transmitted from the upper elastic support 4 to the middle layer plate 3, making the middle layer plate 3 tend to be stationary. Since the vibration of the middle layer plate 3 is greatly suppressed, the lower elastic support 2 is no longer subjected to significant dynamic excitation, thus fundamentally cutting off the path of vibration transmission to the lower layer plate 1. When subjected to residual excitation force, the passive resistance component provides a reaction resistance to further eliminate the influence. The negative stiffness of the internal passive resistance component of the quasi-zero stiffness outrigger 7 is precisely canceled out by the parallel connection of the mechanical positive stiffness. Without affecting the external load, it greatly reduces the natural frequency of the second-stage active-passive composite vibration isolation unit. At the same time, the extremely low stiffness characteristics greatly reduce the kinetic energy consumption required for the driving mass block 8, realizing wide-bandwidth, high-efficiency active isolation of micro-vibrations.

[0029] It should be noted that the sensors and controllers can utilize existing technologies.

[0030] It should be noted that, to ensure that only transmitted vibrations are received, the mass block and the quasi-zero stiffness support leg 7 in this invention do not serve as support components for the upper plate 5 and do not bear the vibration source equipment. To ensure that no mechanical interference occurs among the components when subjected to ultimate static loads or large-stroke dynamic displacements, a safety gap is reserved between the lower surface of the upper plate 5 and the upper surface of the mass block 8, and the top of the quasi-zero stiffness support leg 7. The height of this safety gap is greater than the sum of the maximum static compression of the upper plate 5 under full load conditions and the maximum dynamic amplitude of the system.

[0031] In one embodiment, the actuator 6 includes an actuator base 61 and an actuator top plate 64. The actuator base 61 is fixedly connected to the middle layer plate 3. The active resistance assembly is disposed on the actuator base 61, and the actuator top plate 64 is fixed on the active resistance assembly. The mass block 8 is fixedly disposed on the side of the actuator top plate 64 away from the active resistance assembly. By using the actuator base 61 and the actuator top plate 64 as independent support and load-bearing components, the active resistance assembly is avoided from being a structure directly connected to external functional components. This allows the function of the active resistance assembly to be more focused on providing reverse resistance that matches the excitation force.

[0032] In one embodiment, the active resistance component includes a permanent magnet assembly 62 and a coil assembly 63. The permanent magnet assembly 62 is a straight cylinder, and its bottom is fixed to the actuator base 61. An insertion cavity matching the coil assembly 63 is provided inside the permanent magnet assembly 62, and an insertion hole communicating with the insertion cavity is opened on the top of the permanent magnet assembly 62. The first end of the coil assembly 63 is inserted into the permanent magnet assembly 62 through the insertion hole, and the second end of the coil assembly 63 is fixedly connected to the actuator top plate 64. The permanent magnet assembly 62 and the coil assembly 63 actually form a voice coil motor, which is a direct-drive motor based on the Lorentz force principle that directly converts electrical energy into linear or finite-angle motion. In this application, only its linear motion function is used. When the permanent magnet assembly 62 and the coil assembly 63 are used, the controller directly outputs control current to the coil assembly 63. The coil assembly 63 is subjected to the Lorentz force in the magnetic field, driving the actuator top plate 64 and the mass block 8 to move axially at high frequency. It should be noted that, in the appendix... Figure 2 and attached Figure 5 It can be seen that there is a gap between the bottom of the coil assembly 63 and the bottom of the permanent magnet assembly 62. This gap is an air gap, which is a non-magnetic gap between the stator permanent magnet / yoke and the mover (coil or permanent magnet). It is the critical path of the magnetic circuit and the physical space for the movement of the mover. It determines the magnetic flux density, thrust linearity and stability, and is a necessary prior art.

[0033] In one embodiment, the permanent magnet assembly 62 is one of a straight cylindrical shape, a straight elliptical cylinder, or a right prism. It is understood that the above structures are all shapes that can be adopted in existing voice coil motors.

[0034] In one embodiment, the quasi-zero stiffness outrigger 7 includes an outer sleeve 71. The bottom of the outer sleeve 71 is fixed to the middle plate 3. A mounting cavity is provided inside the outer sleeve 71, and an opening communicating with the mounting cavity is formed at the top of the outer sleeve 71. A positive stiffness telescopic member 73 and a passive resistance assembly are arranged from bottom to top within the mounting cavity. The bottom end of the positive stiffness telescopic member 73 is fixed to the bottom of the outer sleeve 71, and the positive stiffness telescopic member 73 abuts against the bottom of the movable part of the passive resistance assembly. The top of the movable part of the passive resistance assembly extends out of the mounting cavity and connects to the actuator top plate 64. The outer sleeve 71 serves as an independent connecting structure, avoiding the positive stiffness telescopic member 73 and the passive resistance assembly from being structures that directly connect to external functional components. This allows the functions of the positive stiffness telescopic member 73 and the passive resistance assembly to be more focused on providing reverse resistance to match the excitation force. It also plays a regulating and guiding role, ensuring that the resistance release direction of the positive stiffness telescopic member 73 and the passive resistance assembly is correct and stable. The movable part of the passive resistance assembly supports the actuator top plate 64 and can directly receive and respond to the transmitted excitation force.

[0035] It should be noted that positive stiffness refers to the potential energy, supporting force, or resistance that an object can generate in the opposite direction after being compressed (or stretched).

[0036] In one embodiment, the passive resistance assembly includes an outer hollow magnetic column 75, an inner hollow magnetic column 74, and an inner sleeve 77, which is a movable part of the passive resistance assembly. The axial orthographic projection shape of the outer hollow magnetic column 75 is consistent with the axial orthographic projection shape of the inner hollow magnetic column 74. The outer hollow magnetic column 75 is disposed inside the outer sleeve 71, and the inner hollow magnetic column 74 is disposed on the inner sleeve 77. The outer sleeve 71, the outer hollow magnetic column 75, the inner hollow magnetic column 74, and the inner sleeve 77 are coaxially arranged. Both the outer hollow magnetic column 75 and the inner hollow magnetic column 74 are axially magnetized. The inner polarity of the outer hollow magnetic column 75 is the same as the outer polarity of the inner hollow magnetic column 74. The radial main view projection of the outer hollow magnetic column 75 and the radial main view projection of the inner hollow magnetic column 74 overlap. To ensure the uniformity of the magnetic field distribution and eliminate the radially eccentric lateral friction caused by the repulsive magnetic fields, the central axes of the inner hollow magnetic column 74 and the outer hollow magnetic column 75 are completely coincident and coaxially arranged with the axis of the guide rod 72. Regarding the "radial alignment" in the spatial relative position of the hollow magnetic columns, it specifically refers to the axial geometric center planes (i.e., equally divided tangents in the height direction) of the inner hollow magnetic column 74 and the outer hollow magnetic column 75 being on the same horizontal plane. In actual engineering design, the axial lengths of the inner hollow magnetic column 74 and the outer hollow magnetic column 75 can be the same (i.e., the upper and lower end faces are completely flush), or they can be designed differently depending on the specific requirements of the system for the negative stiffness nonlinear curve, but both use their geometric center planes as the physical reference for radial alignment. It should be noted that when the geometric center planes of the inner and outer hollow magnetic columns are completely aligned, the axial static magnetic force between them is zero, and the nonlinear magnetic negative stiffness reaches its peak value at this time. This alignment position is the static plateau point of the quasi-zero stiffness characteristic of this system. Both the inner hollow magnetic column 74 and the outer hollow magnetic column 75 are configured with axially repulsive magnetization. During the dynamic vibration isolation phase of the system, when the inner hollow magnetic column 74 and the outer hollow magnetic column 75 deviate from their equilibrium origin and undergo axial relative displacement, a nonlinear magnetic negative stiffness characteristic is generated between them. This nonlinear magnetic negative stiffness perfectly cancels out the mechanical positive stiffness of the positive stiffness telescopic component 73, causing the branch supporting the mass block 8 to exhibit quasi-zero stiffness characteristics with extremely low dynamic stiffness.

[0037] In one embodiment, the upper edge of the outer hollow magnetic column 75 is flush with the inner edge of the opening. An annular outer hollow magnetic column fixing member 76 covers the outer hollow magnetic column 75 and the outer sleeve 71. An inner sleeve 77 passes through the outer hollow magnetic column fixing member 76. The inner sleeve 77 is made of a magnetically permeable material and has a receiving cavity inside. The top of the inner sleeve 77 has an opening communicating with the receiving cavity. The inner hollow magnetic column 74 is disposed in the receiving cavity. When the outer hollow magnetic column 75 needs to be replaced, the outer hollow magnetic column fixing member 76 can be removed directly to take out the old outer hollow magnetic column 75. When the inner hollow magnetic column 74 needs to be replaced, the old inner hollow magnetic column 74 can be taken out directly from the cavity opening.

[0038] In one embodiment, the flange portion of the flange bearing 78 is disposed within the actuator top plate 64. The lower end of the bearing portion of the flange bearing 78 extends downward to abut against the upper surface of the inner hollow magnetic column 74. The positive stiffness telescopic member 73 is a positive stiffness spring. A lower fixing boss for connecting the bottom of the positive stiffness spring is provided at the bottom of the mounting cavity. An upper fixing boss for connecting the top of the positive stiffness spring is provided at the bottom of the inner sleeve 77. A guide rod 72 fixed to the bottom of the outer sleeve 71 passes through the bearing portion of the flange bearing 78, the inner hollow magnetic column 74, the upper fixing boss, the positive stiffness spring, and the lower fixing boss sequentially from top to bottom. The top of the guide rod 72 is located above the actuator top plate 64. A limiting member 79 is provided at the top of the guide rod 72. The size of the limiting member 79 is larger than the inner ring size of the bearing portion of the flange bearing 78. The bottom of the guide rod 72 is fixed to the bottom of the outer sleeve 71. The guide rod 72 and the outer sleeve 71 are coaxially arranged. The guide rod 72 serves as a further guiding auxiliary structure to further ensure the correct and stable direction of resistance release. The shape of the positive stiffness spring is adapted to the guide rod 72. The limiting member 79 serves two purposes: firstly, it determines the distance between the quasi-zero stiffness support leg 7 and the upper plate 5 at its highest position; secondly, it limits the upward movement stroke of the actuator base plate 64, preventing the mass block 8 from contacting the upper plate 5. The lower end of the bearing portion of the flange bearing 78 presses against the upper surface of the hollow magnetic column 74 to prevent the hollow magnetic column 74 from jumping during vibration elimination, thus ensuring stable linear movement.

[0039] In one embodiment, the axial orthographic projection of the outer hollow magnetic column 75 is a circular ring or a regular polygonal ring. When the axial orthographic projection of the outer hollow magnetic column 75 is a regular polygonal ring, the plane formed by any side edge of the outer hollow magnetic column 75 and the side edge of the nearest inner hollow magnetic column 74 passes through the axis of the outer sleeve 71. This arrangement ensures the alignment of the inner and outer magnetic poles. The shape of the axial orthographic projection of the outer sleeve 71 is consistent with the shape of the axial orthographic projection of the outer hollow magnetic column 75, the shape of the axial orthographic projection of the inner sleeve 77 is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column 74, and the shape of the axial orthographic projection of the guide rod 72 is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column 74.

[0040] In one embodiment, the outer hollow magnetic column 75 and the inner hollow magnetic column 74 are either an integral structure or a spliced ​​structure. It should be noted that when using a spliced ​​structure, it is necessary to ensure that the magnetic poles are intact and uniform.

[0041] In one embodiment, the lower plate 1, middle plate 3, and upper plate 5 are circular plates of the same size. The lower elastic support 2 is arranged with a uniform arc along the edge of the lower plate 1, and the upper elastic support 4 is arranged with a uniform arc along the edge of the middle plate 3. The number of lower elastic support 2 and upper elastic support 4 are the same and they are arranged in a one-to-one correspondence. There are at least three lower elastic support 2s. This one-to-one correspondence ensures a continuous force transmission path and achieves vertical transmission, preventing additional bending moments on the middle plate 3. Stable static support can only be achieved when there are at least three lower elastic support 2s and three upper elastic support 4s.

[0042] In one embodiment, the lower elastic support 2 and the upper elastic support 4 are one of a cylindrical helical spring, an air spring, a rubber damping block, a metal rubber pad, or a leaf spring. These elastic elements all have linear or weakly nonlinear positive stiffness characteristics.

[0043] The quasi-zero stiffness support leg 7 is set between adjacent upper elastic support members 4. There is at least one quasi-zero stiffness support leg 7. When there is more than one, the quasi-zero stiffness support leg 7 is set with equal curvature along the edge of the middle plate 3.

[0044] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0045] If this invention discloses or relates to components or structural parts that are fixedly connected to each other, then, unless otherwise stated, a fixed connection can be understood as: a fixed connection that can be detached (e.g., using bolts or screws), or a fixed connection that cannot be detached (e.g., riveting, welding). Of course, a fixed connection can also be replaced by an integral structure (e.g., manufactured in one piece using a casting process) (except where it is obviously impossible to use an integral molding process).

[0046] In addition, unless otherwise stated, the terms used in any of the technical solutions disclosed in this invention to indicate positional relationships or shapes include states or shapes that are similar to, close to, or approximate with those states or shapes.

[0047] Any component provided by this invention can be assembled from multiple individual components or can be a single component manufactured by a one-piece molding process.

[0048] Any adaptive changes made according to actual needs are within the scope of protection of this invention.

[0049] It should be noted that, for those skilled in the art, it is obvious that the present invention is not limited to the details of the exemplary embodiments described above, and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0050] Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this invention. Furthermore, those skilled in the art will recognize that, based on the ideas of this invention, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this invention.

Claims

1. A vibration isolation device, characterized in that: The system includes a lower plate (1), a middle plate (3), and an upper plate (5) arranged in a parallel and aligned manner from bottom to top. A lower elastic support member (2) is arranged on the lower plate (1) and supports the middle plate (3). The elastic extension direction of the lower elastic support member (2) is perpendicular to the middle plate (3). The lower plate (1) and the lower elastic support member (2) constitute a first-level passive vibration isolation unit. An actuator (6) is mounted on the middle layer plate (3). The line connecting the center of gravity of the actuator (6) and the geometric center of the surface of the middle layer plate (3) is perpendicular to the middle layer plate (3). The actuator (6) includes an active resistance component. The resistance release direction of the active resistance component is perpendicular to the upper layer plate (5). A mass block (8) that does not support the upper layer plate (5) is mounted at the top of the active resistance component. The line connecting the center of gravity of the mass block (8) and the center of gravity of the actuator (6) is perpendicular to the middle layer plate (3). The quasi-zero stiffness support leg (7) of the upper plate (5) is set on the middle plate (3). The quasi-zero stiffness support leg (7) includes a series of positive stiffness telescopic member (73) and passive resistance component. The resistance release direction of the positive stiffness telescopic member (73) and the passive resistance component coincides with and is parallel to the resistance release direction of the active resistance component. The telescopic end of the passive resistance component is connected to the top of the active resistance component. The actuator (6), the mass block (8) and the quasi-zero stiffness support leg (7) constitute an inertial reaction force vibration suppression module. The upper elastic support (4) is set on the middle plate (3) and supports the upper plate (5). The elastic extension direction of the upper elastic support (4) is perpendicular to the middle plate (3). The middle plate (3), the inertial reaction force vibration damping module and the upper elastic support (4) constitute the second-level vibration isolation unit. The middle plate (3) is equipped with a sensor for collecting external vibrations and outputting feedback signals. The controller receives the feedback signals and sends action commands to the actuator (6).

2. The vibration isolation device according to claim 1, characterized in that: The actuator (6) includes an actuator base (61) and an actuator top plate (64). The actuator base (61) is fixedly connected to the middle plate (3). The active resistance component is disposed on the actuator base (61). The actuator top plate (64) is fixed on the active resistance component. The mass block (8) is fixedly disposed on the side of the actuator top plate (64) away from the active resistance component.

3. The vibration isolation device according to claim 2, characterized in that: The active resistance assembly includes a permanent magnet assembly (62) and a coil assembly (63). The permanent magnet assembly (62) is a straight column. The bottom of the permanent magnet assembly (62) is fixed on the actuator base (61). An insertion cavity matching the coil assembly (63) is provided inside the permanent magnet assembly (62). An insertion hole communicating with the insertion cavity is opened on the top of the permanent magnet assembly (62). The first end of the coil assembly (63) is inserted into the permanent magnet assembly (62) through the insertion hole. The actuator top plate (64) is fixedly connected to the second end of the coil assembly (63).

4. The vibration isolation device according to claim 3, characterized in that: The permanent magnet assembly (62) is one of a straight cylindrical cylinder, a straight elliptical cylinder, or a straight prism.

5. The vibration isolation device according to claim 2, characterized in that: The quasi-zero stiffness outrigger (7) includes an outer sleeve (71), the bottom of which is fixed to the middle plate (3). An installation cavity is provided inside the outer sleeve (71), and an opening communicating with the installation cavity is opened at the top of the outer sleeve (71). The positive stiffness telescopic member (73) and the passive resistance assembly are arranged from bottom to top inside the installation cavity. The bottom end of the positive stiffness telescopic member (73) is fixed to the bottom of the outer sleeve (71), and the positive stiffness telescopic member (73) abuts against the bottom of the movable part of the passive resistance assembly. The top of the movable part of the passive resistance assembly extends out of the installation cavity and connects to the actuator top plate (64).

6. The vibration isolation device according to claim 5, characterized in that: The passive resistance assembly includes an outer hollow magnetic column (75), an inner hollow magnetic column (74), and an inner sleeve (77) that is the movable part of the passive resistance assembly. The shape of the axial orthographic projection of the outer hollow magnetic column (75) is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column (74). The outer hollow magnetic column (75) is disposed inside the outer sleeve (71), and the inner hollow magnetic column (74) is disposed on the inner sleeve (77). The outer sleeve (71), the outer hollow magnetic column (75), the inner hollow magnetic column (74), and the inner sleeve (77) are coaxially arranged. Both the outer hollow magnetic column (75) and the inner hollow magnetic column (74) are axially magnetized. The inner polarity of the outer hollow magnetic column (75) is the same as the outer polarity of the inner hollow magnetic column (74). The radial main view projection of the outer hollow magnetic column (75) and the radial main view projection of the inner hollow magnetic column (74) overlap.

7. The vibration isolation device according to claim 6, characterized in that: The upper edge of the outer hollow magnetic column (75) is flush with the inner edge of the opening. The annular outer hollow magnetic column fixing member (76) covers the outer hollow magnetic column (75) and the outer sleeve (71). The inner sleeve (77) passes through the outer hollow magnetic column fixing member (76). The inner sleeve (77) is made of magnetically permeable material. The inner sleeve (77) has a cavity inside. The top of the inner sleeve (77) has an opening that communicates with the cavity. The hollow magnetic column (74) is placed inside the cavity.

8. The vibration isolation device according to claim 7, characterized in that: The flange portion of the flange bearing (78) is disposed inside the actuator top plate (64). The lower end of the bearing portion of the flange bearing (78) extends downward to abut against the upper surface of the inner hollow magnetic column (74). The positive stiffness telescopic member (73) is a positive stiffness spring. The bottom of the mounting cavity is provided with a lower fixing boss for connecting the bottom of the positive stiffness spring. The bottom of the inner sleeve (77) is provided with an upper fixing boss for connecting the top of the positive stiffness spring. The guide rod (72) fixed to the bottom of the outer sleeve (71) passes through the flange bearing (74) from top to bottom. The flange bearing (78) has a bearing portion, an inner hollow magnetic column (74), an upper fixed boss, a positive stiffness spring, and a lower fixed boss. The top of the guide rod (72) is located above the actuator top plate (64). A limiting member (79) is provided on the top of the guide rod (72). The size of the limiting member (79) is larger than the inner ring size of the bearing portion of the flange bearing (78). The bottom of the guide rod (72) is fixed to the bottom of the outer sleeve (71). The guide rod (72) and the outer sleeve (71) are coaxially arranged.

9. The vibration isolation device according to claim 8, characterized in that: The axial orthographic projection of the outer hollow magnetic column (75) is a circular ring or a regular polygonal ring. When the axial orthographic projection of the outer hollow magnetic column (75) is a regular polygonal ring, the plane formed by any side edge of the outer hollow magnetic column (75) and the side edge of the nearest inner hollow magnetic column (74) passes through the axis of the outer sleeve (71). The shape of the axial orthographic projection of the outer sleeve (71) is consistent with the shape of the axial orthographic projection of the outer hollow magnetic column (75), the shape of the axial orthographic projection of the inner sleeve (77) is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column (74), and the shape of the axial orthographic projection of the guide rod (72) is consistent with the shape of the axial orthographic projection of the inner hollow magnetic column (74). The outer hollow magnetic column (75) and the inner hollow magnetic column (74) are integral structures or spliced ​​structures.

10. The vibration isolation device according to claim 1, characterized in that: The lower plate (1), the middle plate (3) and the upper plate (5) are circular plates of the same size. The lower elastic support (2) is set with equal arc along the edge of the lower plate (1), and the upper elastic support (4) is set with equal arc along the edge of the middle plate (3). The number of lower elastic support (2) and upper elastic support (4) are the same and they are set one-to-one. There are at least three lower elastic support (2). The lower elastic support (2) and the upper elastic support (4) are one of the following: cylindrical helical spring, air spring, rubber damping block, metal rubber pad or leaf spring; The quasi-zero stiffness support leg (7) is arranged between adjacent upper elastic support members (4). There is at least one quasi-zero stiffness support leg (7). When there is more than one, the quasi-zero stiffness support leg (7) is arranged with equal arc along the edge of the middle plate (3).

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