WO2015120683A1 - 单自由度磁力隔振装置 - Google Patents

单自由度磁力隔振装置 Download PDF

Info

Publication number
WO2015120683A1
WO2015120683A1 PCT/CN2014/080357 CN2014080357W WO2015120683A1 WO 2015120683 A1 WO2015120683 A1 WO 2015120683A1 CN 2014080357 W CN2014080357 W CN 2014080357W WO 2015120683 A1 WO2015120683 A1 WO 2015120683A1
Authority
WO
WIPO (PCT)
Prior art keywords
permanent magnet
annular permanent
lower annular
connecting rod
central
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2014/080357
Other languages
English (en)
French (fr)
Inventor
陈学东
李子龙
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Huazhong University of Science and Technology
Original Assignee
Huazhong University of Science and Technology
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Huazhong University of Science and Technology filed Critical Huazhong University of Science and Technology
Priority to JP2016551172A priority Critical patent/JP6317822B2/ja
Priority to US15/118,776 priority patent/US9829059B2/en
Publication of WO2015120683A1 publication Critical patent/WO2015120683A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F6/00Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid
    • F16F6/005Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid using permanent magnets only
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00Special physical effects, e.g. nature of damping effects
    • F16F2222/06Magnetic or electromagnetic
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2228/00Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/06Stiffness
    • F16F2228/063Negative stiffness
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00Nature of movement
    • F16F2232/08Linear
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F6/00Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid

Definitions

  • the invention belongs to a vibration isolating device, and particularly relates to a single degree of freedom magnetic vibration isolating device, which can be used to improve the performance of a passive vibration isolating system.
  • the vibration isolation device can isolate the influence of ground and environmental vibration on precision equipment, and provide a "quiet" working environment for vibration-sensitive equipment to ensure the normal operation of precision equipment.
  • the traditional passive vibration isolation structure is generally a rigid coil spring or an air spring. As a rigid component, they cannot attenuate the vibration at the natural frequency of the vibration isolation system. When the external excitation frequency is equal to the natural frequency of the vibration isolation system, the vibration isolation system resonates. , so that the vibration amplitude of the load is amplified, causing the equipment to not work properly or even the adverse effects of damage.
  • the additional damper can reduce the amplitude amplification at the natural frequency of the vibration isolation system, but it will deteriorate the high frequency attenuation performance of the vibration isolation system. Therefore, the general passive vibration isolator can only balance the transfer rate and the high frequency transmission rate at the natural frequency by selecting the optimum damping value. The performance of passive vibration isolation systems often does not meet the requirements of precision vibration isolation.
  • U.S. Patent No. 5,844,664 discloses a damper system including an air spring, a pendulum mechanism, and a voice coil motor.
  • the sensor in the damper system detects and transmits a vibration signal to the controller, which is calculated by the controller.
  • the control command is sent to the voice coil motor, and the voice coil motor outputs the force according to the control command. Because it is the output force realized by the control algorithm, the output force is only attenuated for the vibration near the fixed frequency, and does not affect the attenuation performance of the high frequency.
  • the active vibration isolation performance of the vibration damping system meets the requirements, the structure is complicated, energy needs to be supplied, reliability is not as good as passive vibration isolation system, and the cost is huge.
  • the permanent magnet material has a wide hysteresis loop, high coercivity, high remanence, and can be kept constant after magnetization.
  • a magnetically determinable material also known as a hard magnetic material.
  • the permanent magnet material has high maximum magnetic energy product, high coercive force, high residual magnetic flux density, high residual magnetization and high stability, and is widely used in various actuators such as motors, valves, horns, and steering gears. , aviation equipment and other occasions.
  • the permanent magnet material has the following advantages compared with the electromagnet: The permanent magnet material does not need to supply energy, the structure is very simple, the maintenance is simple, the cost is low, and the user is more acceptable.
  • the permanent magnet material has a high residual magnetic flux density, and a large magnetic force can be generated in a small volume, and the electromagnet is limited by the power limitation of the driver, and at a large current, the electromagnet generates a large heat, so it takes a long time. It is not advisable to use an electromagnet in the magnetic mechanism of the output force. Therefore, permanent magnet materials have great application potential in precision machinery.
  • the invention provides a kind of single-degree-of-freedom magnetic vibration isolation device, which solves the problems that the existing active and passive combined vibration damping system has complex structure, needs energy supply and low reliability, and can be effectively improved by paralleling with the traditional passive vibration isolation system.
  • the performance of passive vibration isolation systems The invention provides a single-degree-of-freedom magnetic vibration isolation device, which comprises a base, an upper annular permanent magnet, a lower annular permanent magnet, a connecting rod and a central permanent magnet, and is characterized in that:
  • a metal conductor tube is connected to the upper surface of the base, the metal conductor tube is a hollow metal cylinder, and the base closes the lower end surface of the metal conductor tube;
  • the upper annular permanent magnet and the lower annular permanent magnet have the same shape, each of which is a hollow circular ring; the upper annular permanent magnet and the lower annular permanent magnet are respectively embedded in the upper annular bushing and the lower annular bushing, and the upper annular bushing And a lower annular bushing respectively connected to the upper end and the lower end of the inner wall of the metal conductor barrel such that the upper annular permanent magnet, the lower annular permanent magnet and the metal conductor cylinder are axially concentric, and the upper annular permanent magnet and The polarities of the opposing magnetic poles of the lower annular permanent magnets are opposite;
  • the axis of the connecting rod is coaxial with the central axis of the metal conductor barrel, the central permanent magnet is a hollow ring, concentrically sleeved on the connecting rod and fixed; the upper end of the connecting rod passes through the upper ring a central hole of the permanent magnet, the central permanent magnet being located between the upper annular permanent magnet and the lower annular permanent magnet, capable of axially moving between the upper annular permanent magnet and the lower annular permanent magnet together with the connecting rod;
  • the polarities of the opposing magnetic poles of the magnet and the upper annular permanent magnet are opposite, and the polarities of the opposing magnetic poles of the central permanent magnet and the lower annular permanent magnet are opposite.
  • the single-degree-of-freedom magnetic vibration isolation device is characterized by:
  • An inner wall of the metal conductor barrel has an internal thread, and an outer side surface of the upper annular bushing and an outer side surface of the lower annular bushing respectively have external threads, so that the upper annular bushing and the lower annular bushing are respectively screwed to the metal
  • the upper and lower ends of the inner wall of the conductor barrel 1.
  • the single-degree-of-freedom magnetic vibration isolation device is characterized by:
  • the base, the connecting rod, the upper annular bushing and the lower annular bushing are made of a non-magnetic material; the metal conductor tube is made of a metal material with high electrical conductivity.
  • the second single-degree-of-freedom magnetic vibration isolation device provided by the invention comprises a base, an upper annular permanent magnet, a lower annular permanent magnet, a connecting rod and a central permanent magnet, and is characterized in that:
  • the upper surface of the base is connected to the mounting cylinder, the mounting cylinder is a hollow cylinder, and the base closes the lower end surface of the mounting cylinder;
  • the upper annular permanent magnet and the lower annular permanent magnet have the same shape, each of which is a hollow circular ring; the upper annular permanent magnet and the lower annular permanent magnet are respectively embedded in the upper annular bushing and the lower annular bushing, and the upper annular bushing And a lower annular bushing respectively connected to the upper end and the lower end of the inner wall of the mounting cylinder such that the upper annular permanent magnet, the lower annular permanent magnet and the mounting cylinder are concentric in the axial direction, and the upper annular permanent magnet and the lower annular ring
  • the opposite poles of the permanent magnets have opposite polarities;
  • the upper conductor plate and the lower conductor plate have the same shape, and are all circular plates having a central threaded hole, and the outer diameter of the circular plate is smaller than the inner diameter of the mounting cylinder to slide in the inner hole of the mounting cylinder;
  • the axis of the connecting rod is coaxial with the central axis of the mounting cylinder, and the central permanent magnet is empty a ring of hearts, concentrically fitted to the shaft of the connecting rod and fixed; the upper end and the lower end of the connecting rod respectively pass through the central hole of the upper annular permanent magnet and the lower annular permanent magnet, and pass through the upper annular permanent magnet;
  • the upper end of the connecting rod of the center hole has an external thread and is screwed with the central threaded hole of the upper conductor plate;
  • the lower end of the connecting rod passing through the center hole of the lower annular permanent magnet has an external thread and is threaded with the center threaded hole of the lower conductor plate connection;
  • the central permanent magnet is located between the upper annular permanent magnet and the lower annular permanent magnet, and is axially movable between the upper annular permanent magnet and the lower annular permanent magnet together with the connecting rod; the central permanent magnet and the upper annular permanent magnet
  • the polarities of the opposing magnetic poles are opposite, and the polarities of the opposing magnetic poles of the central permanent magnet and the lower annular permanent magnet are opposite.
  • the single-degree-of-freedom magnetic vibration isolation device is characterized by:
  • the inner wall of the mounting cylinder has an internal thread, and the outer side surface of the upper annular bushing and the outer side surface of the lower annular bushing respectively have external threads, so that the upper annular bushing and the lower annular bushing are respectively screwed to the mounting cylinder The upper and lower ends of the inner wall.
  • the single-degree-of-freedom magnetic vibration isolation device is characterized by:
  • the base, the connecting rod, the upper annular bushing and the lower annular bushing are made of a non-magnetic material;
  • the mounting cylinder is made of a non-metallic material;
  • the upper conductor plate and the lower conductor plate are made of a metal having high conductivity Made of materials.
  • the invention has the advantages of simple structure, no need of energy supply and high reliability, and can generate static magnetic force and dynamic magnetic force, and the static magnetic force is realized by the permanent magnet mutual attraction, and the dynamic magnetic force is generated by the relative movement of the metal conductor tube and the permanent magnet to generate eddy current damping;
  • the magnitude of the static magnetic force is only related to the displacement.
  • the magnetic force also exists, which can be regarded as a kind of stiffness force.
  • the eddy current damping is only related to the relative motion speed, and exists only when the magnetic mechanism moves, and can be regarded as A viscous damping force.
  • the invention is connected in parallel with a passive vibration isolation system such as a rigid coil spring, an air spring, etc., without affecting the vibration isolation system
  • the high-frequency attenuation performance reduces the amplitude amplification at the natural frequency, which can effectively improve the passive vibration isolation performance of the original system.
  • Embodiment 1 is a schematic structural view of Embodiment 1 of the present invention.
  • Embodiment 2 is an application schematic diagram of Embodiment 1;
  • Figure 3 is a schematic diagram of the effect of the system shown in Figure 2;
  • FIG. 4 is a schematic structural view of a third embodiment of the present invention.
  • a first embodiment of the present invention includes a metal conductor barrel 1, a base 2, an upper annular permanent magnet 3a, a lower annular permanent magnet 3b, a connecting rod 5 and a central permanent magnet 6;
  • the upper surface of the base 2 is connected to the metal conductor tube 1.
  • the metal conductor tube 1 is a hollow metal cylinder, and the base 2 closes the lower end surface of the metal conductor tube 1;
  • the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are identical in shape, each being a hollow annular ring; the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are respectively embedded in the upper annular bushing 4a and the lower annular bushing 4b Inner, upper annular bushing 4a and lower annular bushing 4b are respectively connected to upper and lower ends of the inner wall of the metal conductor cylinder 1, such that the upper annular permanent magnet 3a, the lower annular permanent magnet 3b and the metal conductor cylinder 1 are The axes are concentric, and the polarities of the opposing magnetic poles of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are opposite, respectively, N pole and S pole ⁇ '
  • the axis of the connecting rod 5 is coaxial with the central axis of the metal conductor tube 1.
  • the central permanent magnet 6 is a hollow ring, concentrically sleeved on the connecting rod 5 and fixed; the upper end of the connecting rod 5 passes through a central hole of the upper annular permanent magnet 3a, the central permanent magnet 6 being located between the upper annular permanent magnet 3a and the lower annular permanent magnet 3b, together with the connecting rod 5 in the upper annular permanent magnet 3a and
  • the axial movement between the lower annular permanent magnets 3b; the polarities of the opposing magnetic poles of the central permanent magnet 6 and the upper annular permanent magnet 3a are opposite, respectively S and N; the central permanent magnet 6 and the lower annular permanent magnet 3b are opposite to each other The opposite polarity is N and S poles.
  • the base 2, the connecting rod 5, the upper annular bushing 4a and the lower annular bushing 4b are made of a polymer composite material such as polyurethane or plexiglass; the metal conductor cylinder 1 is electrically conductive. Made of high-quality metal copper.
  • the central permanent magnet 6 is simultaneously attracted by the magnetic force of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b.
  • the center permanent magnet 6 is located just in the middle of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b, the upper and lower magnetic attraction forces are the same in magnitude and opposite in direction, and the central permanent magnet 6 is subjected to force balance.
  • the center permanent magnet 6 is biased to the upper annular permanent magnet 3a or the lower annular permanent magnet 3b on one side, the upper annular permanent magnet 3a or the lower annular permanent magnet 3b on this side attracts the central permanent magnet 6.
  • This displacement-dependent static magnetism can be seen as a negative stiffness.
  • FIG. 2 is a schematic diagram of the application of the first embodiment.
  • the load 10 is supported by a passive spring element 9 for isolating the vibration of the foundation 11 from being transmitted to the load 10.
  • the single-degree-of-freedom magnetic vibration isolating device 12 of the first embodiment is connected in parallel with the passive spring element 9, wherein the connecting rod 5 of the first embodiment is connected to the load 10, and the base 2 is connected to the foundation 11.
  • the central permanent magnet 6 is located just in the middle of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b.
  • the central permanent magnet 6 is subjected to a force of zero, and does not change the equilibrium position of the passive vibration isolation system.
  • the passive spring element 9 is in a stretched state, creating a downward spring force.
  • the intermediate permanent magnet 6 will be close to the upper ring.
  • the magnet 3a is subjected to the resultant force of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b upward, counteracting a part of the passive spring element 9 to generate a downward spring force.
  • the passive spring element 9 is under pressure In the contracted state, an upward spring force is generated.
  • the intermediate permanent magnet 6 is adjacent to the lower annular permanent magnet 3b, and is subjected to the upper annular permanent magnet 3a and the lower annular permanent magnet 3b.
  • the resultant force is downward, offsetting a portion of the passive spring element 9 to produce an upward spring force.
  • the spring force experienced by the load 10 is reduced, that is, the stiffness of the vibration isolation system is reduced.
  • Figure 3 is a schematic diagram of the effect of the system shown in Figure 2.
  • the vertical axis is the system's transfer rate and the horizontal axis is the frequency.
  • Conventional passive vibration isolation systems can effectively isolate ground vibrations in the high frequency range, but there is a large amplitude amplification at the natural frequency.
  • the transmission rate at the natural frequency is greatly reduced, and the high frequency performance is not deteriorated.
  • the magnitude of the static magnetic force mainly affects the peak frequency of the system. Excessive static magnetic force will make the peak frequency of the system too small or even close to OHz, which makes the system lose stability.
  • the dynamic magnetic force is determined by the magnetic field strength and size of the intermediate permanent magnet 6 and the size and conductivity of the metal conductor tube 1, which mainly affects the magnitude of the peak value of the system. The larger the dynamic magnetic force, the smaller the amplitude of the system peak, and the user needs to The magnitude of the dynamic magnetic force is designed for the resonance peak requirement.
  • the second embodiment of the present invention has the same structural composition as that of the first embodiment. As shown in FIG. 1, the difference is only that: the inner wall of the metal conductor cylinder 1 has an internal thread, and the outer side surface and the lower ring of the upper annular bushing 4a The outer sides of the bushings 4b are respectively externally threaded so that the upper annular bushing 4a and the lower annular bushing 4b are screwed to the upper and lower ends of the inner wall of the metal conductor cylinder 1, respectively.
  • the second embodiment has an advantage in that the upper annular permanent magnet 3a and the upper annular permanent magnet 3a can be adjusted by changing the fitting positions of the upper annular bushing 4a and the lower annular bushing 4b at the upper end and the lower end of the inner wall of the metal conductor cylinder 1.
  • the distance between the lower annular permanent magnets 3b changes the negative stiffness value to avoid the system losing stability because the negative stiffness value exceeds the positive stiffness value of the passive vibration isolation system. Sex.
  • a third embodiment of the present invention includes a base 2, an upper annular permanent magnet 3a, a lower annular permanent magnet 3b, a connecting rod 5 and a central permanent magnet 6;
  • the upper surface of the base 2 is connected to the mounting cylinder 8, and the mounting cylinder 8 is a hollow cylinder, and the base 2 closes the lower end surface of the mounting cylinder 8;
  • the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are identical in shape, each being a hollow annular ring; the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are respectively embedded in the upper annular bushing 4a and the lower annular bushing 4b Inner, upper annular bushing 4a and lower annular bushing 4b are respectively connected to upper and lower ends of the inner wall of the mounting cylinder 8, such that the upper annular permanent magnet 3a, the lower annular permanent magnet 3b and the mounting cylinder 8 are axially Concentric, and the polarities of the opposing magnetic poles of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b are opposite;
  • the inner wall of the mounting cylinder 8 has an internal thread, and the outer side surface of the upper annular bushing 4a and the outer side surface of the lower annular bushing 4b have external threads, respectively, so that the upper annular bushing 4a and the lower annular bushing 4b are respectively screwed.
  • the upper conductor plate 7a and the lower conductor plate 7b are identical in shape, and each is a circular plate having a central threaded hole, and the outer diameter of the circular plate is smaller than the inner diameter of the mounting cylinder 8 so as to slide in the inner hole of the mounting cylinder 8;
  • the axis of the rod 5 is coaxial with the central axis of the mounting barrel 8
  • the central permanent magnet 6 is a hollow ring that is concentrically fitted to the shaft of the connecting rod 5 and fixed; the upper end and the lower end of the connecting rod 5 are respectively Through the central hole of the upper annular permanent magnet 3a and the lower annular permanent magnet 3b, the upper end of the connecting rod 5 passing through the central hole of the upper annular permanent magnet 3a has an external thread and is threaded with the central threaded hole of the upper conductor plate 7a.
  • Connecting; the lower end of the connecting rod 5 passing through the central hole of the lower annular permanent magnet 3b has an external thread and is screwed with the central threaded hole of the
  • the central permanent magnet 6 is located between the upper annular permanent magnet 3a and the lower annular permanent magnet 3b, and is axially movable between the upper annular permanent magnet 3a and the lower annular permanent magnet 3b together with the connecting rod 5;
  • the polarities of the opposing magnetic poles of the magnet 6 and the upper annular permanent magnet 3a are opposite, and the polarities of the opposing magnetic poles of the central permanent magnet 6 and the lower annular permanent magnet 3b are opposite.
  • the base 2, the connecting rod 5, the upper annular bushing 4a and the lower annular bushing 4b are made of a polymer composite material such as polyurethane or plexiglass; in order not to affect the size of the eddy current damping, the mounting cylinder 8 is made of a polymer composite material such as polyurethane or plexiglass; the upper conductor plate 7a and the lower conductor plate 7b are made of metal copper having high electrical conductivity.
  • the relative movement between the central permanent magnet and the metal conductor cylinder is changed to the relative movement between the upper annular permanent magnet 3a and the lower annular permanent magnet 3b and the upper conductor plate 7a and the lower conductor plate 7b.
  • the movement of the central permanent magnet 6 drives the movement of the upper conductor plate 7a and the lower conductor plate 7b, causing the upper conductor plate 7a and the lower conductor plate 7b to move relative to the upper annular permanent magnet 3a and the lower annular permanent magnet 3b to generate eddy current damping.
  • the distance between the upper conductor plate 7a and the lower conductor plate 7b and the upper annular permanent magnet 3a and the lower annular permanent magnet 3b can be changed on the connecting rod 5, and the dynamic magnetic force can be adjusted according to different applications, and the magnetic mechanism is increased. applicability.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

单自由度磁力隔振装置,属于隔振装置,解决现有主动和被动结合减振系统结构复杂、需要供给能源且可靠性不高的问题。该单自由度磁力隔振装置包括金属导体筒(1)、底座(2)、上环形永磁体(3a)、下环形永磁体(3b),连接杆(5)和中心永磁体(6);上、下环形永磁体相向面磁极的极性相反,分别连接于金属导体筒(1)内壁的上端和下端;中心永磁体(6)同心套于连接杆(5)并固接,中心永磁体(6)位于上、下环形永磁体之间,能够连同连接杆(5)在上、下环形永磁体之间轴向运动;中心永磁体(6)和上、下环形永磁体相向面磁极的极性相反。该单自由度磁力隔振装置结构简单、不需供给能源且可靠性高,可产生静磁力和动磁力,将该单自由度磁力隔振装置与被动隔振系统并联可以有效的改善原系统的被动隔振性能。

Description

单自由度磁力隔振装置
【技术领域】
本发明属于隔振装置, 特别涉及单自由度磁力隔振装置, 能够用于改 善被动隔振系统的性能。
【背景技术】
随着科学技术的不断发展, 以 IC制造装备、 高分辨率电子显微镜、 表 面粗糙度测试仪和精密光学设备等为代表的精密制造设备、 精密测量设备 得到了越来越广泛的应用, 其对精度的要求越来越高。 作为实现高精度的 重要基础设备, 隔振装置能隔离地基和环境振动对精密设备的影响, 给振 动敏感的设备提供 "安静" 的工作环境, 保证精密设备的正常运行。
传统的被动隔振结构一般为刚性螺旋弹簧或者空气弹簧, 它们作为刚 性元件, 不能衰减隔振系统固有频率处的振动, 在外界激励频率等于隔振 系统固有频率的情况下, 隔振系统发生共振, 使得负载的振动幅值被放大, 造成设备不能正常工作甚至损坏的不利影响。 通过附加阻尼器可以减小隔 振系统固有频率处的幅值放大, 但却会恶化隔振系统的高频衰减性能。 因 此, 一般的被动隔振器只能通过选择最佳阻尼值, 来兼顾固有频率处的传 递率和高频传递率。 被动隔振系统的性能往往不能达到精密隔振的要求。
采用主动和被动结合的方式, 可以解决被动隔振性能不足的问题。 美 国专利 US5844664 (公开号) 公开了一种减振系统, 该减振系统包括空气 弹簧、 摆机构和音圈电机, 减振系统中的传感器将振动信号检测并发送给 控制器, 由控制器计算出控制指令并发送给音圈电机, 音圈电机根据控制 指令输出力。 因为是通过控制算法实现的输出力, 因此该输出力只针对固 有频率附近的振动进行衰减, 并不影响高频的衰减性能。 虽然该减振系统 的主动隔振性能满足要求, 但结构复杂, 需要供给能源, 可靠性不如被动 隔振系统, 且成本巨大。
永磁材料具有宽磁滞回线、 高娇顽力、 高剩磁, 一经磁化即能保持恒 定磁性的材料, 又称硬磁材料。 永磁材料具有高的最大磁能积、 高的娇顽 力, 高的剩余磁通密度和高的剩余磁化强度及高的稳定性, 广泛应用在各 种执行机构如电机、 阀、 喇叭、 舵机、 航空设备等场合。 在磁力机构中, 永磁材料与电磁铁相比, 存在以下优点: 永磁材料不需要供给能源, 结构 十分精简, 维护简便, 成本低廉, 更容易被用户接受。 永磁材料具有很高 的剩余磁通密度, 小体积下便可产生较大的磁力, 而电磁铁受限于驱动器 功率限制, 且在大电流下, 电磁铁发热较大, 因此在需要长时间输出力的 磁力机构中不宜选用电磁铁。 因此, 永磁材料在精密机械中有着巨大的应 用潜力。
【发明内容】
本发明提供一类单自由度磁力隔振装置, 解决现有主动和被动结合减 振系统结构复杂、 需要供给能源且可靠性不高的问题, 通过其与传统被动 隔振系统并联, 可以有效提高被动隔振系统的性能。 本发明所提供的一种单自由度磁力隔振装置, 包括底座、 上环形永磁 体、 下环形永磁体, 连接杆和中心永磁体, 其特征在于:
所述底座上表面连接金属导体筒, 所述金属导体筒为空心金属圆筒, 所述底座将金属导体筒的下端面封闭;
所述上环形永磁体和下环形永磁体形状相同, 各自均为空心圆环; 所 述上环形永磁体和下环形永磁体分别嵌于上环形衬套和下环形衬套内, 上 环形衬套和下环形衬套分别连接于所述金属导体筒内壁的上端和下端, 使 得所述上环形永磁体、 下环形永磁体和所述金属导体筒在轴向同心, 且所 述上环形永磁体和下环形永磁体相向面磁极的极性相反;
所述连接杆的轴线与所述金属导体筒的中轴线同轴, 所述中心永磁体 为空心圆环, 同心套于连接杆并固接; 所述连接杆的上端穿过所述上环形 永磁体的中心孔, 所述中心永磁体位于所述上环形永磁体和下环形永磁体 之间, 能够连同所述连接杆在上环形永磁体和下环形永磁体之间轴向运动; 中心永磁体和上环形永磁体相向面磁极的极性相反, 中心永磁体和下环形 永磁体相向面磁极的极性相反。 所述的单自由度磁力隔振装置, 其特征在于:
所述金属导体筒的内壁具有内螺纹, 所述上环形衬套的外侧面和下环 形衬套的外侧面分别具有外螺纹, 以便上环形衬套和下环形衬套分别螺纹 连接于所述金属导体筒 1内壁的上端和下端。 所述的单自由度磁力隔振装置, 其特征在于:
所述底座、 连接杆、 上环形衬套和下环形衬套采用非导磁材料制成; 所述金属导体筒采用电导率高的金属材料制成。 本发明所提供的第二种单自由度磁力隔振装置, 包括底座、 上环形永 磁体、 下环形永磁体, 连接杆和中心永磁体, 其特征在于:
所述底座上表面连接安装筒, 所述安装筒为空心圆筒, 所述底座将安 装筒的下端面封闭;
所述上环形永磁体和下环形永磁体形状相同, 各自均为空心圆环; 所 述上环形永磁体和下环形永磁体分别嵌于上环形衬套和下环形衬套内, 上 环形衬套和下环形衬套分别连接于所述安装筒内壁的上端和下端, 使得所 述上环形永磁体、 下环形永磁体和所述安装筒在轴向同心, 且所述上环形 永磁体和下环形永磁体相向面磁极的极性相反;
所述上导体板和下导体板形状相同, 均为具有中心螺纹孔的圆板, 圆 板外径小于所述安装筒的内径, 以便在安装筒的内孔滑动;
所述连接杆的轴线与所述安装筒的中轴线同轴, 所述中心永磁体为空 心圆环, 同心套于连接杆的杆身并固接; 所述连接杆的上端和下端分别穿 过所述上环形永磁体和下环形永磁体的中心孔, 穿过所述上环形永磁体中 心孔的连接杆上端具有外螺纹, 并与上导体板的中心螺纹孔螺纹连接; 穿 过所述下环形永磁体中心孔的连接杆下端具有外螺纹, 并与下导体板的中 心螺纹孔螺纹连接;
所述中心永磁体位于所述上环形永磁体和下环形永磁体之间, 能够连 同所述连接杆在上环形永磁体和下环形永磁体之间轴向运动; 中心永磁体 和上环形永磁体相向面磁极的极性相反, 中心永磁体和下环形永磁体相向 面磁极的极性相反。 所述的单自由度磁力隔振装置, 其特征在于:
所述安装筒的内壁具有内螺纹, 所述上环形衬套的外侧面和下环形衬 套的外侧面分别具有外螺纹, 以便上环形衬套和下环形衬套分别螺纹连接 于所述安装筒内壁的上端和下端。 所述的单自由度磁力隔振装置, 其特征在于:
所述底座、 连接杆、 上环形衬套和下环形衬套采用非导磁材料制成; 所述安装筒采用非金属材料制成; 所述上导体板和下导体板采用电导率高 的金属材料制成。 本发明结构简单、 不需供给能源且可靠性高, 可产生静磁力和动磁力, 静磁力通过永磁体异极相吸实现, 动磁力通过金属导体筒与永磁体相对运 动产生涡流阻尼实现; 由于静磁力大小只与位移相关, 当本发明的装置静 止时磁力也存在, 可以看成是一种刚度力, 涡流阻尼只与相对运动速度相 关, 只在磁力机构发生运动时存在, 可以看成是一种粘性阻尼力。 将本发 明与被动隔振系统如刚性螺旋弹簧、 空气弹簧等并联, 在不影响隔振系统 高频衰减性能的同时减小固有频率处的幅值放大, 可以有效的改善原系统 的被动隔振性能。
【附图说明】
图 1为本发明实施例一的结构示意图;
图 2为实施例一的应用原理图;
图 3为图 2所示系统的效果示意图;
图 4为本发明实施例三的结构示意图。
【具体实施方式】
以下结合附图和实施例对本发明进一歩说明。
如图 1所示, 本发明的实施例一, 包括金属导体筒 1、 底座 2、 上环形 永磁体 3a、 下环形永磁体 3b, 连接杆 5和中心永磁体 6;
所述底座 2上表面连接金属导体筒 1,所述金属导体筒 1为空心金属圆 筒, 所述底座 2将金属导体筒 1的下端面封闭;
所述上环形永磁体 3a和下环形永磁体 3b形状相同, 各自均为空心圆 环; 所述上环形永磁体 3a和下环形永磁体 3b分别嵌于上环形衬套 4a和下 环形衬套 4b内, 上环形衬套 4a和下环形衬套 4b分别连接于所述金属导体 筒 1 内壁的上端和下端, 使得所述上环形永磁体 3a、 下环形永磁体 3b和 所述金属导体筒 1在轴向同心,且所述上环形永磁体 3a和下环形永磁体 3b 相向面磁极的极性相反, 分别为 N极和 S极 ·'
所述连接杆 5的轴线与所述金属导体筒 1的中轴线同轴, 所述中心永 磁体 6为空心圆环, 同心套于连接杆 5并固接; 所述连接杆 5的上端穿过 所述上环形永磁体 3a的中心孔, 所述中心永磁体 6位于所述上环形永磁体 3a和下环形永磁体 3b之间, 能够连同所述连接杆 5在上环形永磁体 3a和 下环形永磁体 3b之间轴向运动; 中心永磁体 6和上环形永磁体 3a相向面 磁极的极性相反, 分别为 S极和 N极; 中心永磁体 6和下环形永磁体 3b 相向面磁极的极性相反, 分别为 N极和 S极。
为了不影响永磁体的磁场分布, 所述底座 2、 连接杆 5、 上环形衬套 4a 和下环形衬套 4b采用高分子复合材料如聚氨酯、 有机玻璃制成; 所述金属 导体筒 1采用电导率高的金属铜制成。
中心永磁体 6同时受到上环形永磁体 3a和下环形永磁体 3b的磁力吸 引。 当中心永磁体 6正好位于上环形永磁体 3a和下环形永磁体 3b的正中 间时, 上下磁吸引力大小相同, 方向相反, 此时中心永磁体 6受力平衡。 当中心永磁体 6偏向一侧的上环形永磁体 3a或下环形永磁体 3b时, 这一 侧的上环形永磁体 3a或下环形永磁体 3b会将中心永磁体 6吸引过来。 这 种与位移相关的静磁力可以看成为一种负刚度。 中心永磁体 6与金属导体 筒 1发生相对运动时, 会在金属导体筒 1 中产生涡电流, 涡电流受到中心 永磁体 6激发的磁场的安培力, 这种与速度相关的动磁力可以看成一种粘 性阻尼, 该阻尼力始终与相对运动方向相反。
图 2为实施例一的应用原理图。 负载 10由被动弹簧元件 9支撑, 用以 隔离地基 11 的振动传递到负载 10上。 实施例一的单自由度磁力隔振装置 12与被动弹簧元件 9并联, 其中, 实施例一的连接杆 5与负载 10相连, 底 座 2与地基 11相连。 为了不影响被动隔振系统的静态变形量, 当单自由度 磁力隔振装置 12与被动弹簧元件 9并联时, 中心永磁体 6正好位于上环形 永磁体 3a和下环形永磁体 3b的中间位置, 此时中心永磁体 6受力为零, 不会改变被动隔振系统的平衡位置。 当负载 10位于平衡位置上方时, 被动 弹簧元件 9处于拉伸状态, 产生向下的弹簧力, 此时在本发明的单自由度 磁力隔振装置 12中, 中间永磁体 6会靠近上环形永磁体 3a, 受到上环形永 磁体 3a和下环形永磁体 3b的合力向上, 抵消掉一部分被动弹簧元件 9产 生向下的弹簧力。 当负载 10位于平衡位置下方时, 被动弹簧元件 9处于压 缩状态,产生向上的弹簧力,此时在本发明的单自由度磁力隔振装置 12中, 中间永磁体 6会靠近下环形永磁体 3b,受到上环形永磁体 3a和下环形永磁 体 3b的合力向下, 抵消掉一部分被动弹簧元件 9产生向上的弹簧力。 总体 上来看负载 10受到的弹簧力减小了, 即隔振系统的刚度变小。
图 3为图 2所示系统的效果示意图。 图 3中纵轴为系统的传递率, 横 轴为频率。 传统的被动隔振系统在高频率段可以有效隔离地基振动, 但是 在固有频率处存在较大的振幅放大。 而通过被动隔振系统与实施例一并联, 可以看出, 固有频率处传递率大大减小, 且高频性能也没有恶化。 在本发 明实际应用时, 需要根据实际的隔振系统来设计本发明中的参数来与之匹 配, 静磁力由上环形永磁体 3a、下环形永磁体 3b及中心永磁体 6的磁场强 度和尺寸决定, 静磁力的大小主要影响系统峰值频率, 过大的静磁力会使 系统的峰值频率过小甚至接近 OHz, 使系统失去稳定性。 动磁力由中间永 磁体 6的磁场强度和尺寸以及金属导体筒 1 的尺寸及电导率决定, 主要影 响系统峰值的幅值大小, 动磁力越大, 系统峰值的幅值越小, 使用者需要 根据对共振峰值的要求来设计动磁力的大小。
本发明的实施例二, 结构组成和实施例一相同, 如图 1 所示, 区别仅 在于: 所述金属导体筒 1的内壁具有内螺纹, 所述上环形衬套 4a的外侧面 和下环形衬套 4b的外侧面分别具有外螺纹, 以便上环形衬套 4a和下环形 衬套 4b分别螺纹连接于所述金属导体筒 1 内壁的上端和下端。
上环形永磁体 3a和下环形永磁体 3b之间的距离越小, 中心永磁体 6 受到的静磁力越强, 其负刚度数值越大。 反之, 上环形永磁体 3a和下环形 永磁体 3b之间的距离越大, 中心永磁体 6受到的静磁力越弱, 其负刚度数 值越小。 与第一实施例相比, 第二实施例的优点在于能够通过改变上环形 衬套 4a和下环形衬套 4b在金属导体筒 1 内壁上端和下端的配合位置, 从 而调整上环形永磁体 3a和下环形永磁体 3b之间的距离, 改变负刚度数值, 避免因为负刚度数值超过了被动隔振系统的正刚度数值, 使系统失去稳定 性。
如图 4所示, 本发明的实施例三, 包括底座 2、 上环形永磁体 3a、 下 环形永磁体 3b, 连接杆 5和中心永磁体 6;
所述底座 2上表面连接安装筒 8, 所述安装筒 8为空心圆筒, 所述底座 2将安装筒 8的下端面封闭;
所述上环形永磁体 3a和下环形永磁体 3b形状相同, 各自均为空心圆 环; 所述上环形永磁体 3a和下环形永磁体 3b分别嵌于上环形衬套 4a和下 环形衬套 4b内,上环形衬套 4a和下环形衬套 4b分别连接于所述安装筒 8 内 壁的上端和下端, 使得所述上环形永磁体 3a、下环形永磁体 3b和所述安装 筒 8在轴向同心, 且所述上环形永磁体 3a和下环形永磁体 3b相向面磁极 的极性相反;
所述安装筒 8的内壁具有内螺纹, 所述上环形衬套 4a的外侧面和下环 形衬套 4b的外侧面分别具有外螺纹, 以便上环形衬套 4a和下环形衬套 4b 分别螺纹连接于所述安装筒 8内壁的上端和下端;
所述上导体板 7a和下导体板 7b形状相同, 均为具有中心螺纹孔的圆 板, 圆板外径小于所述安装筒 8的内径, 以便在安装筒 8的内孔滑动; 所述连接杆 5的轴线与所述安装筒 8的中轴线同轴,所述中心永磁体 6 为空心圆环, 同心套于连接杆 5的杆身并固接; 所述连接杆 5的上端和下 端分别穿过所述上环形永磁体 3a和下环形永磁体 3b的中心孔, 穿过所述 上环形永磁体 3a中心孔的连接杆 5上端具有外螺纹,并与上导体板 7a的中 心螺纹孔螺纹连接; 穿过所述下环形永磁体 3b中心孔的连接杆 5下端具有 外螺纹, 并与下导体板 7b的中心螺纹孔螺纹连接;
所述中心永磁体 6位于所述上环形永磁体 3a和下环形永磁体 3b之间, 能够连同所述连接杆 5在上环形永磁体 3a和下环形永磁体 3b之间轴向运 动; 中心永磁体 6和上环形永磁体 3a相向面磁极的极性相反, 中心永磁体 6和下环形永磁体 3b相向面磁极的极性相反。 为了不影响永磁体的磁场分布, 底座 2、 连接杆 5、 上环形衬套 4a和 下环形衬套 4b采用高分子复合材料如聚氨酯、 有机玻璃制成; 为了不影响 涡流阻尼的大小, 安装筒 8采用高分子复合材料如聚氨酯、 有机玻璃制成; 上导体板 7a和下导体板 7b采用电导率高的金属铜制成。 与实施例一、 实施例二相比, 实施例三的优点是:
中心永磁体与金属导体筒间的相对运动改变为上环形永磁体 3a和下环 形永磁体 3b与上导体板 7a和下导体板 7b间的相对运动。 中心永磁体 6的 运动带动上导体板 7a和下导体板 7b的运动,使上导体板 7a和下导体板 7b 与上环形永磁体 3a和下环形永磁体 3b发生相对运动产生涡流阻尼。
可以在连接杆 5上改变上导体板 7a和下导体板 7b与上环形永磁体 3a 和下环形永磁体 3b之间的距离, 可以根据不同的应用场合调整动磁力的大 小, 增加了磁力机构的适用性。

Claims

1.一种单自由度磁力隔振装置, 包括底座 (2)、 上环形永磁体 (3a)、 下环形永磁体 (3b), 连接杆 (5) 和中心永磁体 (6), 其特征在于:
所述底座 (2) 上表面连接金属导体筒 (1), 所述金属导体筒 (1) 为 空心金属圆筒, 所述底座 (2) 将金属导体筒 (1) 的下端面封闭;
所述上环形永磁体 (3a) 和下环形永磁体 (3b) 形状相同, 各自均为 空心圆环; 所述上环形永磁体 (3a) 和下环形永磁体 (3b) 分别嵌于上环 形衬套(4a)和下环形衬套(4b) 内, 上环形衬套(4a)和下环形衬套(4b) 分别连接于所述金属导体筒 (1) 内壁的上端和下端, 使得所述上环形永 磁体 (3a)、 下环形永磁体 3b和所述金属导体筒 (1) 在轴向同心, 且所述 上环形永磁体 (3a) 和下环形永磁体 (3b) 相向面磁极的极性相反;
所述连接杆 (5) 的轴线与所述金属导体筒 (1) 的中轴线同轴, 所述 中心永磁体 (6) 为空心圆环, 同心套于连接杆 (5) 并固接; 所述连接杆 (5) 的上端穿过所述上环形永磁体 (3a) 的中心孔, 所述中心永磁体 (6) 位于所述上环形永磁体 (3a) 和下环形永磁体 (3b) 之间, 能够连同所述 连接杆 (5) 在上环形永磁体 (3a) 和下环形永磁体 (3b) 之间轴向运动; 中心永磁体 (6) 和上环形永磁体 (3a) 相向面磁极的极性相反, 中心永磁 体 (6) 和下环形永磁体 (3b) 相向面磁极的极性相反。
2.如权利要求 1所述的单自由度磁力隔振装置, 其特征在于:
所述金属导体筒 (1) 的内壁具有内螺纹, 所述上环形衬套 (4a) 的外 侧面和下环形衬套 (4b) 的外侧面分别具有外螺纹, 以便上环形衬套 (4a) 和下环形衬套 (4b) 分别螺纹连接于所述金属导体筒 (1) 内壁的上端和下
3. 如权利要求 1或 2所述的单自由度磁力隔振装置, 其特征在于: 所述底座 (2)、 连接杆 (5)、 上环形衬套 (4a) 和下环形衬套 (4b) 采用非导磁材料制成; 所述金属导体筒(1)采用电导率高的金属材料制成。
4. 一种单自由度磁力隔振装置, 包括底座 (2)、 上环形永磁体 (3a)、 下环形永磁体 (3b), 连接杆 (5) 和中心永磁体 (6), 其特征在于:
所述底座 (2) 上表面连接安装筒 (8), 所述安装筒 (8) 为空心圆筒, 所述底座 (2) 将安装筒 (8) 的下端面封闭;
所述上环形永磁体 (3a) 和下环形永磁体 (3b) 形状相同, 各自均为 空心圆环; 所述上环形永磁体 (3a) 和下环形永磁体 (3b) 分别嵌于上环 形衬套(4a)和下环形衬套(4b) 内, 上环形衬套(4a)和下环形衬套(4b) 分别连接于所述安装筒 (8) 内壁的上端和下端, 使得所述上环形永磁体 (3a), 下环形永磁体 (3b) 和所述安装筒 (8) 在轴向同心, 且所述上环 形永磁体 (3a) 和下环形永磁体 (3b) 相向面磁极的极性相反;
所述上导体板 (7a) 和下导体板 (7b) 形状相同, 均为具有中心螺纹 孔的圆板, 圆板外径小于所述安装筒 (8) 的内径, 以便在安装筒 (8) 的 内孔滑动;
所述连接杆 (5) 的轴线与所述安装筒 (8) 的中轴线同轴, 所述中心 永磁体 (6) 为空心圆环, 同心套于连接杆 (5) 的杆身并固接; 所述连接 杆(5)的上端和下端分别穿过所述上环形永磁体(3a)和下环形永磁体(3b) 的中心孔, 穿过所述上环形永磁体 (3a) 中心孔的连接杆 (5) 上端具有外 螺纹, 并与上导体板 (7a) 的中心螺纹孔螺纹连接; 穿过所述下环形永磁 体 (3b) 中心孔的连接杆 (5) 下端具有外螺纹, 并与下导体板 (7b) 的中 心螺纹孔螺纹连接;
所述中心永磁体(6)位于所述上环形永磁体(3a)和下环形永磁体(3b) 之间,能够连同所述连接杆(5)在上环形永磁体(3a)和下环形永磁体(3b) 之间轴向运动; 中心永磁体 (6) 和上环形永磁体 (3a) 相向面磁极的极性 相反, 中心永磁体 (6 ) 和下环形永磁体 (3b) 相向面磁极的极性相反。
5. 如权利要求 4所述的单自由度磁力隔振装置, 其特征在于: 所述安装筒 (8 ) 的内壁具有内螺纹, 所述上环形衬套 (4a) 的外侧面 和下环形衬套 (4b ) 的外侧面分别具有外螺纹, 以便上环形衬套 (4a) 和 下环形衬套 (4b) 分别螺纹连接于所述安装筒 (8 ) 内壁的上端和下端。
6. 如权利要求 4或 5所述的单自由度磁力隔振装置, 其特征在于: 所述底座 (2)、 连接杆 (5 )、 上环形衬套 (4a) 和下环形衬套 (4b ) 采用非导磁材料制成; 所述安装筒 (8 ) 采用非金属材料制成; 所述上导体 板 (7a) 和下导体板 (7b) 采用电导率高的金属材料制成。
PCT/CN2014/080357 2014-02-14 2014-06-20 单自由度磁力隔振装置 Ceased WO2015120683A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2016551172A JP6317822B2 (ja) 2014-02-14 2014-06-20 一自由度磁力防振装置
US15/118,776 US9829059B2 (en) 2014-02-14 2014-06-20 Single degree-of-freedom magnetic vibration isolation device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410051123.8A CN103775550B (zh) 2014-02-14 2014-02-14 单自由度磁力隔振装置
CN201410051123.8 2014-02-14

Publications (1)

Publication Number Publication Date
WO2015120683A1 true WO2015120683A1 (zh) 2015-08-20

Family

ID=50568154

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/080357 Ceased WO2015120683A1 (zh) 2014-02-14 2014-06-20 单自由度磁力隔振装置

Country Status (4)

Country Link
US (1) US9829059B2 (zh)
JP (1) JP6317822B2 (zh)
CN (1) CN103775550B (zh)
WO (1) WO2015120683A1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112458874A (zh) * 2020-11-05 2021-03-09 安徽建筑大学 一种桥梁多级防震抗倾覆联动装置
CN113685474A (zh) * 2021-08-12 2021-11-23 天津大学 单稳态磁悬浮式减振装置及其磁悬浮力的计算方法
CN115830975A (zh) * 2022-12-27 2023-03-21 重庆大学 一种六自由度运动模拟平台
CN119712754A (zh) * 2024-11-06 2025-03-28 浙江宇嘉新能源科技股份有限公司 一种磁力减震器

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103775550B (zh) * 2014-02-14 2015-09-23 华中科技大学 单自由度磁力隔振装置
PT3180542T (pt) * 2014-08-13 2019-01-11 Esm Energie Und Schwingungstechnik Mitsch Gmbh Amortecedor magnético para absorção de vibrações
CN104260902B (zh) * 2014-09-11 2016-08-17 上海卫星工程研究所 卫星敏感载荷系统及其磁悬浮非线性隔振器及设计方法
CN104879411A (zh) * 2014-11-21 2015-09-02 上海卫星工程研究所 卫星敏感载荷的磁悬浮非线性隔振器及设计方法
CN104747652B (zh) * 2015-03-05 2016-08-17 西安交通大学 一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器
CN105156577B (zh) * 2015-09-07 2017-03-29 西安交通大学 一种采用倾斜磁体产生负刚度的超阻尼隔振器
CN105221642B (zh) * 2015-10-16 2018-06-19 吴炳臣 一种减震方法、减震装置及其应用
CN105365846B (zh) * 2015-12-01 2018-04-17 王向东 永磁减速顶
CN105805204B (zh) * 2016-03-29 2018-11-02 石翔 一种被动线性磁负刚度装置
CN105912044B (zh) * 2016-06-06 2018-08-03 上海交通大学 频率分辨率可调谐动力吸振器
CN106763396B (zh) * 2017-01-18 2019-01-29 华中科技大学 一种动磁式阻尼器
KR101759704B1 (ko) 2017-06-15 2017-07-20 한유씨스템 (주) 완충용 댐퍼 장치
CN107889038B (zh) * 2017-12-22 2023-10-31 国光电器股份有限公司 一种电磁动铁式微型扬声器
US20190234480A1 (en) * 2018-01-31 2019-08-01 Suhder Ind Co., Ltd. Magnetic suspension shock absorber
NL2020783B1 (en) * 2018-04-18 2019-10-24 Flanders Make Vzw Magnetic spring
RU184575U1 (ru) * 2018-06-13 2018-10-30 федеральное государственное автономное образовательное учреждение высшего образования "Российский университет дружбы народов" (РУДН) Магнитный амортизатор
CN108547896B (zh) * 2018-06-15 2019-11-26 郑州大学 一种电磁弹簧智能减振器
CN109114147B (zh) * 2018-09-29 2023-11-24 西南交通大学 减振装置及行驶设备
CN109356962B (zh) * 2018-11-27 2019-11-12 华中科技大学 一种多维磁负刚度机构及其构成的多维磁负刚度减振系统
CN110439961B (zh) * 2019-07-19 2024-06-21 中国船舶重工集团公司第七一九研究所 一种磁阻式电磁主被动一体化复合隔振器
CN110762159B (zh) * 2019-12-03 2024-04-12 金陵科技学院 一种双向作用筒式电永磁弹簧
CN111981085B (zh) * 2020-08-31 2022-03-15 合肥工业大学 基于电磁负刚度的弹性-迟滞低频大位移隔振器
CN112503308A (zh) * 2020-12-14 2021-03-16 伍文洪 磁悬浮避震脚钉
CN113669406A (zh) * 2021-08-23 2021-11-19 南京林业大学 一种三维磁浮减振装置
CN113700788A (zh) * 2021-08-26 2021-11-26 华中科技大学 一种包含组合型磁负刚度机构的近零刚度隔振系统
CN113757285B (zh) * 2021-09-08 2022-06-21 重庆大学 负刚度生成机构及准零刚度隔振器
CN113898693B (zh) 2021-10-22 2024-04-19 合肥工业大学 减振执行器
CN114509154A (zh) * 2022-03-10 2022-05-17 北京源振科技有限公司 一种拾振器的双磁体磁路结构
PL441303A1 (pl) * 2022-05-26 2023-11-27 Politechnika Bydgoska Im. Jana I Jędrzeja Śniadeckich Magnetyczny reduktor drgań silników liniowych sterowanych siłą wychylenia
CN115571378B (zh) * 2022-10-09 2024-05-07 沈阳航空航天大学 一种用于在轨航天器微振动的复合式振动控制装置
CN115727094B (zh) * 2022-11-29 2024-09-10 武汉理工大学 一种并列磁式负刚度结构的紧凑型低频隔振装置
CN116818077A (zh) * 2023-06-28 2023-09-29 中航电测仪器股份有限公司 一种适用于变质量随机载荷的准零刚度隔振系统
CN118686878B (zh) * 2024-08-26 2024-11-05 江苏耐玛鑫精密机械有限公司 一种磁力弹簧及其使用方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4710656A (en) * 1986-12-03 1987-12-01 Studer Philip A Spring neutralized magnetic vibration isolator
US7290642B2 (en) * 2002-05-03 2007-11-06 Integrated Dynamics Engineering Gmbh Magnetic spring device with negative stiffness
US7628254B1 (en) * 2005-10-11 2009-12-08 The United States Of America As Represented By The Secretary Of The Air Force Passive magneto-rheological vibration isolation apparatus using a shielding sleeve
CN102200689A (zh) * 2010-03-23 2011-09-28 上海微电子装备有限公司 一种混合磁浮式的重力补偿装置
CN102506110A (zh) * 2011-10-25 2012-06-20 清华大学 一种基于负刚度原理的永磁低频单自由度隔振机构
CN103775550A (zh) * 2014-02-14 2014-05-07 华中科技大学 单自由度磁力隔振装置

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5160868A (en) * 1974-11-22 1976-05-27 Japan Servo 3 konoeikyujishakuyorinaruseidomataha seishinsochi
JPS643338A (en) * 1987-06-26 1989-01-09 Bridgestone Corp Shock absorber
JPS6448445U (zh) * 1987-09-21 1989-03-24
US5120030A (en) * 1991-05-28 1992-06-09 General Motors Corporation Magnet assisted liftgate strut
TW316874B (zh) 1995-05-30 1997-10-01 Philips Electronics Nv
US5780943A (en) * 1996-04-04 1998-07-14 Nikon Corporation Exposure apparatus and method
CN1077966C (zh) * 1996-04-08 2002-01-16 株式会社三角工具加工 具有阻尼特性的磁弹簧和具有所述磁弹簧的振动机构
JPH10521A (ja) * 1996-06-07 1998-01-06 Nikon Corp 支持装置
DE29715711U1 (de) * 1997-09-02 1997-11-06 NSM Magnettechnik GmbH, 59399 Olfen Dämpfungsanschlag an der Stapelstation für Scheibenelemente, insbesondere Blechzuschnitte u.dgl.
NL1007127C2 (nl) * 1997-09-26 1999-03-29 Univ Delft Tech Draagsysteem.
US5979882A (en) * 1997-11-22 1999-11-09 Honeywell Inc. Direct fluid shear damper
US6129185A (en) * 1997-12-30 2000-10-10 Honeywell International Inc. Magnetically destiffened viscous fluid damper
US6448679B1 (en) * 2000-12-14 2002-09-10 Joseph Imlach Passive magnetic support and damping system
CN2575367Y (zh) * 2002-08-13 2003-09-24 经玉凤 稀土永磁减振器
CN1715701A (zh) * 2005-07-15 2006-01-04 哈尔滨工业大学 涡流磁阻尼式缓冲阻尼装置
DE102005038797B3 (de) * 2005-08-17 2006-10-26 Thyssenkrupp Bilstein Suspension Gmbh Einrichtung zur amplitudenabhängigen Dämpfung
CN201982560U (zh) * 2010-12-07 2011-09-21 吕国富 一种减震结构
CN202732815U (zh) * 2012-07-10 2013-02-13 北京航空航天大学 一种用于抑制轴向振动的电涡流耗能阻尼器
JP3187011U (ja) * 2013-08-08 2013-11-07 株式会社レイホー 磁力式アクチュエータおよび開閉補助装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4710656A (en) * 1986-12-03 1987-12-01 Studer Philip A Spring neutralized magnetic vibration isolator
US7290642B2 (en) * 2002-05-03 2007-11-06 Integrated Dynamics Engineering Gmbh Magnetic spring device with negative stiffness
US7628254B1 (en) * 2005-10-11 2009-12-08 The United States Of America As Represented By The Secretary Of The Air Force Passive magneto-rheological vibration isolation apparatus using a shielding sleeve
CN102200689A (zh) * 2010-03-23 2011-09-28 上海微电子装备有限公司 一种混合磁浮式的重力补偿装置
CN102506110A (zh) * 2011-10-25 2012-06-20 清华大学 一种基于负刚度原理的永磁低频单自由度隔振机构
CN103775550A (zh) * 2014-02-14 2014-05-07 华中科技大学 单自由度磁力隔振装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112458874A (zh) * 2020-11-05 2021-03-09 安徽建筑大学 一种桥梁多级防震抗倾覆联动装置
CN112458874B (zh) * 2020-11-05 2022-03-15 安徽建筑大学 一种桥梁多级防震抗倾覆联动装置
CN113685474A (zh) * 2021-08-12 2021-11-23 天津大学 单稳态磁悬浮式减振装置及其磁悬浮力的计算方法
CN113685474B (zh) * 2021-08-12 2022-09-13 天津大学 单稳态磁悬浮式减振装置及其磁悬浮力的计算方法
CN115830975A (zh) * 2022-12-27 2023-03-21 重庆大学 一种六自由度运动模拟平台
CN119712754A (zh) * 2024-11-06 2025-03-28 浙江宇嘉新能源科技股份有限公司 一种磁力减震器

Also Published As

Publication number Publication date
US20170045107A1 (en) 2017-02-16
JP6317822B2 (ja) 2018-04-25
JP2017505889A (ja) 2017-02-23
CN103775550B (zh) 2015-09-23
CN103775550A (zh) 2014-05-07
US9829059B2 (en) 2017-11-28

Similar Documents

Publication Publication Date Title
WO2015120683A1 (zh) 单自由度磁力隔振装置
CN112303175B (zh) 基于主动电磁负刚度结构的六自由度隔微振器
CN101917143B (zh) 一种具有磁浮重力平衡功能的音圈电机
CN106015420B (zh) 一种半主动式振动控制电涡流阻尼器
CN108443382B (zh) 一种采用电磁负刚度的主被动复合隔振器及控制方法
CN101915283B (zh) 一种磁流变复合阻尼控制方法与装置
CN112377561B (zh) 基于主动电磁负刚度结构的三自由度隔微振器
CN105402297A (zh) 磁负刚度阻尼器
CN105805204B (zh) 一种被动线性磁负刚度装置
CN102705414A (zh) 一种圆筒式电磁阻尼器
CN108144829B (zh) 一种刚度可控的正应力电磁式振动平台及控制方法
CN108111057B (zh) 一种多功能三方向压电-电磁耦合式换能器
CN105927694B (zh) 一种基于变电流磁场的可调负刚度机构
CN105840727B (zh) 一种轴向磁力耦合的可调刚度机构
CN105156577B (zh) 一种采用倾斜磁体产生负刚度的超阻尼隔振器
CN111963602B (zh) 基于电磁负刚度的双稳态非线性能量肼
CN109039007A (zh) 磁流体驱动的防微振柔性微位移调节平台
CN109027124B (zh) 一种负刚度可调的扭转准零刚度隔振器及控制方法
CN201802802U (zh) 一种磁流变复合阻尼控制装置
CN108019452B (zh) 一种半主动可控刚度非线性电磁隔振器
Yu et al. Design of coaxial integrated macro–micro composite actuator with long-stroke and high-precision
CN114215877B (zh) 一种沙漏型宽幅宽频准零刚度电磁隔振器
CN113258743B (zh) 非接触式电磁激振器
CN202579783U (zh) 一种新型电磁阻尼器
CN207664892U (zh) 一种多功能三方向压电-电磁耦合式换能器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14882657

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2016551172

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 15118776

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14882657

Country of ref document: EP

Kind code of ref document: A1