CN104747652A - Quasi-zero stiffness vibration isolator connected with magnetic spring in parallel through spiral spring - Google Patents
Quasi-zero stiffness vibration isolator connected with magnetic spring in parallel through spiral spring Download PDFInfo
- Publication number
- CN104747652A CN104747652A CN201510097824.XA CN201510097824A CN104747652A CN 104747652 A CN104747652 A CN 104747652A CN 201510097824 A CN201510097824 A CN 201510097824A CN 104747652 A CN104747652 A CN 104747652A
- Authority
- CN
- China
- Prior art keywords
- permanent magnet
- clamping mechanism
- spring
- magnetic
- coil spring
- 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.)
- Granted
Links
- 239000002184 metal Substances 0.000 claims description 5
- 229910052751 metal Inorganic materials 0.000 claims description 5
- 238000009434 installation Methods 0.000 claims description 4
- 239000007769 metal material Substances 0.000 claims description 4
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 238000002955 isolation Methods 0.000 abstract description 29
- 238000000034 method Methods 0.000 abstract description 8
- 238000013016 damping Methods 0.000 abstract description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 230000005389 magnetism Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000012216 screening Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器，包括质量支撑杆，质量支撑杆的一端与螺旋弹簧通过螺纹固连；被螺旋弹簧夹持的永磁体与螺旋弹簧、质量支撑杆一起沿轴向相对于螺旋弹簧夹持机构运动，同时螺旋弹簧沿轴向为系统提供正刚度；由永磁体夹持机构固定的两块环形永磁体分别对由螺旋弹簧夹持的永磁体施加吸引力，三块永磁体构成一磁性弹簧，并为系统提供非线性恢复力和非线性负刚度；通过旋扭永磁体夹持机构，即可调节上、下两块永磁体与被螺旋弹簧夹持的永磁体之间的相对距离；本发明装置能够有效地降低隔振系统的固有频率，进而拓宽了隔振频带；同时，提高并改善到了结构的阻尼特性，为低频振动控制提供一种可靠的方法。
A quasi-zero-stiffness vibration isolator adopting a parallel connection of a coil spring and a magnetic spring, including a mass support rod, one end of the mass support rod and the coil spring are fixedly connected by threads; the permanent magnet clamped by the coil spring, the coil spring, and the mass support rod They move together in the axial direction relative to the helical spring clamping mechanism, and the helical spring provides positive stiffness for the system in the axial direction; two ring-shaped permanent magnets fixed by the permanent magnet clamping mechanism respectively exert attraction to the permanent magnets clamped by the helical spring Force, three permanent magnets constitute a magnetic spring, and provide nonlinear restoring force and nonlinear negative stiffness for the system; by twisting the permanent magnet clamping mechanism, the upper and lower permanent magnets can be adjusted to be clamped by the coil spring The relative distance between the permanent magnets; the device of the present invention can effectively reduce the natural frequency of the vibration isolation system, thereby widening the vibration isolation frequency band; at the same time, it improves and improves the damping characteristics of the structure, providing a reliable low-frequency vibration control method.
Description
技术领域technical field
本发明涉及隔振技术领域，具体涉及一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器。The invention relates to the technical field of vibration isolation, in particular to a quasi-zero-stiffness vibration isolator using a helical spring and a magnetic spring connected in parallel.
背景技术Background technique
机械结构振动现象普遍存在于实际的生产实践当中。当系统受到外界振源的激励时，将会产生振动。人们利用振动可为生产实践服务，如工业上常采用的振动筛选，振动沉桩，振动输送以及按振动理论设计的传感器等；然而，在国防科技、工业机械以及仪表、仪器等技术领域，机械振动往往会导致结构的破坏失效，测量精度降低，使用寿命缩短等问题。例如，仪表、仪器的振动会导致其测量精度降低；航天器发射时，冲击载荷可能会造成结构的破坏失效等。The phenomenon of mechanical structure vibration generally exists in the actual production practice. When the system is excited by an external vibration source, it will vibrate. People use vibration to serve production practice, such as vibration screening, vibration pile sinking, vibration transmission and sensors designed according to vibration theory, etc. commonly used in industry; however, in the technical fields of national defense technology, industrial machinery, instruments, instruments, etc. Vibration often leads to structural failure, reduced measurement accuracy, and shortened service life. For example, the vibration of instruments and instruments will reduce their measurement accuracy; when the spacecraft is launched, the impact load may cause structural damage and failure.
在处理有害振动问题时，隔振技术常常是优先考虑的方法。与常见的主动隔振、半主动隔振相比，被动式隔振由于其具有使用简单，不需要外界提供能源，稳定性好等优点而被广泛采用。对于机械振动问题中的中高频振动部分，可采用已发展成熟的线性隔振理论以及相应方法来实现有效的控制，当激励频率大于隔振系统无阻尼固有频率的倍时，传统的线性隔振器才具有隔振效果，但对于低频带范围的振动往往难以有效的隔离。由于一般线性隔振器的隔振频带受到限制，为了能够对低频区域的振动进行有效的控制，非线性低频隔振理论和方法已经有了一些相关的研究。常采用的一种方法是通过减小隔振系统的刚度来拓宽隔振频带，但减小隔振系统的刚度将会导致静变形增大，降低系统的稳定性。为解决该问题，准零刚度隔振器、高静态-低动态刚度隔振系统得到了许多学者的关注。由于永磁体的性能与制备已取得了一定的进展，采用永磁结构设计出具有准零刚度特性的隔振系统显得相对容易；然而，在一定的设计指标下，设计出固有频率低，结构简单并且空间尺寸小的非线性隔振系统，就显得较为困难。When dealing with unwanted vibration problems, vibration isolation techniques are often the preferred method. Compared with common active vibration isolation and semi-active vibration isolation, passive vibration isolation is widely used because of its advantages of simple use, no external energy supply, and good stability. For the medium and high frequency vibration part of the mechanical vibration problem, the well-developed linear vibration isolation theory and corresponding methods can be used to achieve effective control. When the excitation frequency is greater than the natural frequency of the vibration isolation system without damping The traditional linear vibration isolator has the effect of vibration isolation, but it is often difficult to effectively isolate the vibration in the low frequency range. Since the vibration isolation frequency band of general linear vibration isolators is limited, in order to effectively control the vibration in the low frequency region, some related researches have been done on nonlinear low frequency vibration isolation theory and methods. A commonly used method is to widen the vibration isolation frequency band by reducing the stiffness of the vibration isolation system, but reducing the stiffness of the vibration isolation system will lead to an increase in static deformation and reduce the stability of the system. To solve this problem, quasi-zero stiffness vibration isolators and high static-low dynamic stiffness vibration isolation systems have attracted the attention of many scholars. Since the performance and preparation of permanent magnets have made some progress, it is relatively easy to design a vibration isolation system with quasi-zero stiffness characteristics using a permanent magnet structure; And the nonlinear vibration isolation system with small space size is more difficult.
发明内容Contents of the invention
为克服现有技术存在的问题，本发明的目的是提出一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器，本发明装置在其工作位置附近具有高静态刚度-低动态刚度特性，可用于低频隔振，缓冲等工况，并具有结构简单，安装方便，承载力大，成本低的特点，能够有效地降低隔振系统的固有频率，进而拓宽了隔振频带；同时，提高并改善到了结构的阻尼特性，为低频振动控制提供一种可靠的方法。In order to overcome the problems existing in the prior art, the purpose of the invention is to propose a quasi-zero stiffness vibration isolator that adopts helical springs and magnetic springs connected in parallel. The device of the invention has high static stiffness-low dynamic stiffness characteristics near its working position, It can be used in low-frequency vibration isolation, buffering and other working conditions, and has the characteristics of simple structure, convenient installation, large bearing capacity, and low cost. It can effectively reduce the natural frequency of the vibration isolation system, thereby broadening the vibration isolation frequency band; The damping characteristics of the structure are improved, providing a reliable method for low frequency vibration control.
为了解决上述技术问题，本发明采用的技术方案如下：In order to solve the problems of the technologies described above, the technical scheme adopted in the present invention is as follows:
一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器，包括螺旋弹簧7，设置在螺旋弹簧7中心腔体内的第一环形永磁体15，设置在螺旋弹簧7中心腔体上端的中间永磁体固定盖6；两端带有螺纹段的质量支撑杆1的一端螺纹段穿过永磁体固定盖6的螺纹孔、中间环形永磁体15的中心孔以及螺旋弹簧7中心腔体底部的中心螺纹孔，所述中间永磁体固定盖6的螺纹孔和螺旋弹簧7中心腔体底部的中心螺纹孔与质量支撑杆1的螺纹段相适配，所述第一环形永磁体15的中心孔与质量支撑杆1的螺纹段间隙配合；所述质量支撑杆1的中间无螺纹段轴向设置有约束质量支撑杆1使其沿轴向运动的不导磁直线轴承2，不导磁直线轴承2的外部设置有内壁和外壁带有螺纹的上端永磁体夹持机构4，上端永磁体夹持机构4和不导磁直线轴承2间形成的腔体中放置上端环形永磁体16，上端永磁体夹持机构4的顶部开口处设置有与上端永磁体夹持机构4内壁螺纹相适配的带有外螺纹的上端永磁体固定盖3，用于固定上端环形永磁体16；所述上端永磁体固定盖3与不导磁直线轴承2通过第一螺栓14固连，螺旋弹簧7的外端上下设置有通过第二螺栓13固定的上端螺旋弹簧夹持机构5和下端螺旋弹簧夹持机构8；上端螺旋弹簧夹持机构5通过其上端凸台的内螺纹与上端永磁体夹持机构4的外壁螺纹配合连接；下端螺旋弹簧夹持机构8的下端凸台内螺纹处固定有带有外螺纹的下端永磁体夹持机构9，下端永磁体夹持机构9内放置下端环形永磁体17，下端永磁体夹持机构9下端通过内螺纹固定有用于连接外部振源的固定键10；所述上端螺旋弹簧夹持机构5的上端凸台通过第三螺栓12将上端永磁体夹持机构4固定，下端螺旋弹簧夹持机构8的下端凸台通过第四螺栓11将下端永磁体夹持机构9固定。A quasi-zero-stiffness vibration isolator adopting a parallel connection of a coil spring and a magnetic spring, comprising a coil spring 7, a first annular permanent magnet 15 arranged in the center cavity of the coil spring 7, an intermediate permanent magnet arranged at the upper end of the center cavity of the coil spring 7 Magnet fixed cover 6; one end threaded section of mass support bar 1 with threaded section at both ends passes through the threaded hole of permanent magnet fixed cover 6, the central hole of the middle annular permanent magnet 15 and the central thread at the bottom of the coil spring 7 central cavity hole, the threaded hole of the middle permanent magnet fixing cover 6 and the central threaded hole at the bottom of the central cavity of the coil spring 7 are compatible with the threaded section of the mass support rod 1, and the central hole of the first annular permanent magnet 15 is compatible with the mass support rod The threaded section of 1 has a clearance fit; the middle unthreaded section of the mass support rod 1 is axially provided with a non-magnetic linear bearing 2 that constrains the mass support rod 1 to move in the axial direction, and the external setting of the non-magnetic linear bearing 2 There is an upper permanent magnet clamping mechanism 4 with threads on the inner wall and outer wall, and an upper annular permanent magnet 16 is placed in the cavity formed between the upper permanent magnet clamping mechanism 4 and the non-magnetic linear bearing 2, and the upper permanent magnet clamping mechanism 4 The top opening of the top is provided with an upper permanent magnet fixing cover 3 with an external thread that is compatible with the inner wall thread of the upper permanent magnet clamping mechanism 4, and is used to fix the upper end ring permanent magnet 16; the upper permanent magnet fixing cover 3 and The non-magnetic linear bearing 2 is fixedly connected by the first bolt 14, and the outer end of the coil spring 7 is provided with an upper helical spring clamping mechanism 5 and a lower helical spring clamping mechanism 8 fixed by the second bolt 13; the upper helical spring clamp The holding mechanism 5 is threadedly connected with the outer wall of the upper permanent magnet clamping mechanism 4 through the internal thread of the upper end boss; Holding mechanism 9, the lower end permanent magnet holding mechanism 9 is placed with a lower end annular permanent magnet 17, and the lower end of the lower end permanent magnet holding mechanism 9 is fixed with a fixed key 10 for connecting to an external vibration source through an internal thread; the upper end helical spring holding mechanism The upper end boss of 5 fixes the upper permanent magnet clamping mechanism 4 by the third bolt 12, and the lower end boss of the lower end helical spring clamping mechanism 8 fixes the lower permanent magnet clamping mechanism 9 by the fourth bolt 11.
通过旋钮上端永磁体夹持机构4和下端永磁体夹持机构9来调节上端环形永磁体16和下端环形永磁体17沿轴向的相对位置。The relative positions of the upper ring permanent magnet 16 and the lower ring permanent magnet 17 in the axial direction are adjusted by the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9 of the knob.
将上端永磁体固定盖3和固定键10在上端永磁体夹持机构4和下端永磁体夹持机构9分别旋进不同深度来调节安装的上端环形永磁体16和下端环形永磁体17的厚度。The upper permanent magnet fixed cover 3 and the fixed key 10 are respectively screwed into different depths in the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9 to adjust the thickness of the upper end annular permanent magnet 16 and the lower end annular permanent magnet 17 installed.
所述不导磁直线轴承2采用金属铜，所述隔振器除不导磁直线轴承2外的其余部件采用非导磁的金属材料。The non-magnetic linear bearing 2 is made of metal copper, and the other parts of the vibration isolator except the non-magnetic linear bearing 2 are made of non-magnetic metal materials.
所述上端环形永磁体16和下端环形永磁体17与中间环形永磁体15的初始安装距离设置为10mm。The initial installation distance between the upper end ring permanent magnet 16 and the lower end ring permanent magnet 17 and the middle ring permanent magnet 15 is set to 10 mm.
本发明和现有的技术相比，具有如下优点：Compared with the prior art, the present invention has the following advantages:
1、当沿着质量支撑杆1的轴向加载时，与质量支撑杆1固连的螺旋弹簧7将沿轴向发生弹性变形。本发明根据弹性元件的特性，采用螺旋弹簧7作为隔振系统的正刚度弹性支撑元件，螺旋弹簧具有低的应力集中，沿轴向可产生较大的位移，占用空间小的特点。1. When the mass support rod 1 is loaded in the axial direction, the coil spring 7 fixedly connected with the mass support rod 1 will elastically deform in the axial direction. According to the characteristics of the elastic element, the present invention adopts the coil spring 7 as the positive stiffness elastic support element of the vibration isolation system. The coil spring has the characteristics of low stress concentration, large displacement along the axial direction, and small space occupation.
2、采用三块环形永磁体构成本发明所需要的磁性弹簧并为该隔振系统提供负刚度，从而降低隔振装置在其工作位置附近的刚度，进而拓宽隔振频带，实现低频隔振。2. Three ring-shaped permanent magnets are used to form the magnetic spring required by the present invention and provide negative stiffness for the vibration isolation system, thereby reducing the stiffness of the vibration isolation device near its working position, further widening the vibration isolation frequency band, and realizing low frequency vibration isolation.
3、由于永磁结构的引入，使本发明装置具有快速响应、非接触、占用空间小等特点；可以通过旋扭上端永磁体夹持机构4和下端永磁体夹持机构9来调节永磁体之间的相对位置来为系统在工作位置附近获得理想的负刚度特性。3. Due to the introduction of the permanent magnet structure, the device of the present invention has the characteristics of quick response, non-contact, and small space occupation; the permanent magnet can be adjusted by twisting the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9. The relative position between them is used to obtain the ideal negative stiffness characteristics for the system near the working position.
4、本发明采用带有外螺纹的上端永磁体固定盖3与固定键10将上端环形永磁体16和下端环形永磁体17与上端永磁体夹持机构4和下端永磁体夹持机构9固连。可将上端永磁体固定盖3与固定键10在上端永磁体夹持机构4和下端永磁体夹持机构9中旋进不同深度，即可调节并装配不同厚度的上端环形永磁体16和下端环形永磁体17。4. The present invention adopts the upper permanent magnet fixing cover 3 with external threads and the fixing key 10 to securely connect the upper annular permanent magnet 16 and the lower annular permanent magnet 17 with the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9 . The upper permanent magnet fixing cover 3 and the fixing key 10 can be screwed into different depths in the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9, and the upper annular permanent magnet 16 and the lower annular permanent magnet of different thicknesses can be adjusted and assembled. Permanent magnet 17.
5、本发明所有零部件均采用不导磁材料，避免对永磁体产生的磁场的造成干扰。5. All parts of the present invention are made of non-magnetic materials to avoid interference with the magnetic field generated by the permanent magnet.
6、本发明装置中所有部件均可采用不导磁的金属材料；当系统工作时，将会在金属部件中产生涡电流，可改善本发明装置的阻尼特性。6. All parts in the device of the present invention can be made of non-magnetic metal materials; when the system is working, eddy currents will be generated in the metal parts, which can improve the damping characteristics of the device of the present invention.
7、本发明结构装置，使用方便，成本低廉，承载能力强，对于低频振动具有良好的隔离效果。7. The structural device of the present invention is easy to use, low in cost, strong in bearing capacity, and has a good isolation effect on low-frequency vibrations.
附图说明Description of drawings
图1为本发明隔振器装配体半剖视图。Fig. 1 is a half-sectional view of a vibration isolator assembly of the present invention.
图2为螺旋弹簧零件图。Figure 2 is a diagram of the coil spring parts.
图3为永磁体夹持机构零件图，其中：图3a为上端永磁体夹持机构零件图，图3b为下端永磁体夹持机构零件图。Figure 3 is a part diagram of the permanent magnet clamping mechanism, wherein: Figure 3a is a part diagram of the upper permanent magnet clamping mechanism, and Figure 3b is a part diagram of the lower permanent magnet clamping mechanism.
具体实施方式Detailed ways
下面结合附图对本发明的结构原理和工作原理进一步做详细说明。The structural principle and working principle of the present invention will be further described in detail below in conjunction with the accompanying drawings.
如图1、图2和图3所示，本发明一种采用螺旋弹簧与磁性弹簧并联的准零刚度隔振器，包括螺旋弹簧7，设置在螺旋弹簧7中心腔体内的第一环形永磁体15，设置在螺旋弹簧7中心腔体上端的永磁体固定盖6；两端带有螺纹段的质量支撑杆1的一端螺纹段穿过永磁体固定盖6的螺纹孔、中间环形永磁体15的中心孔以及螺旋弹簧7中心腔体底部的中心螺纹孔，所述中间永磁体固定盖6的螺纹孔和螺旋弹簧7中心腔体底部的中心螺纹孔与质量支撑杆1的螺纹段相适配，所述第一环形永磁体15的中心孔与质量支撑杆1的螺纹段间隙配合；所述质量支撑杆1的中间无螺纹段轴向设置有约束质量支撑杆1使其沿轴向运动的不导磁直线轴承2，不导磁直线轴承2的外部设置有内壁和外壁带有螺纹的上端永磁体夹持机构4，上端永磁体夹持机构4和不导磁直线轴承2间形成的腔体中放置上端环形永磁体16，上端永磁体夹持机构4的顶部开口处设置有与上端永磁体夹持机构4内壁螺纹相适配的带有外螺纹的上端永磁体固定盖3，用于固定上端环形永磁体16；所述上端永磁体固定盖3与不导磁直线轴承2通过第一螺栓14固连，螺旋弹簧7的外端上下设置有通过第二螺栓13固定的上端螺旋弹簧夹持机构5和下端螺旋弹簧夹持机构8；上端螺旋弹簧夹持机构5通过其上端凸台的内螺纹与上端永磁体夹持机构4的外壁螺纹配合连接；下端螺旋弹簧夹持机构8的下端凸台内螺纹处固定有带有外螺纹的下端永磁体夹持机构9，下端永磁体夹持机构9内放置下端环形永磁体17，下端永磁体夹持机构9下端通过内螺纹固定有用于连接外部振源的固定键10；所述上端螺旋弹簧夹持机构5的上端凸台通过第三螺栓12将上端永磁体夹持机构4固定，下端螺旋弹簧夹持机构8的下端凸台通过第四螺栓11将下端永磁体夹持机构9固定。As shown in Fig. 1, Fig. 2 and Fig. 3, a quasi-zero-stiffness vibration isolator using a helical spring and a magnetic spring in parallel in the present invention includes a helical spring 7 and a first annular permanent magnet arranged in the central cavity of the helical spring 7 15, the permanent magnet fixed cover 6 arranged on the upper end of the coil spring 7 central cavity; the threaded section at one end of the mass support rod 1 with threaded sections at both ends passes through the threaded hole of the permanent magnet fixed cover 6, the ring permanent magnet 15 in the middle Central hole and the central threaded hole at the bottom of the central cavity of the coil spring 7, the threaded hole at the bottom of the central permanent magnet fixing cover 6 and the central threaded hole at the bottom of the central cavity of the coil spring 7 are compatible with the threaded section of the mass support rod 1, the The central hole of the first annular permanent magnet 15 is in clearance fit with the threaded section of the mass support rod 1; the middle unthreaded section of the mass support rod 1 is axially provided with a non-magnetism that constrains the mass support rod 1 to move axially. The linear bearing 2, the non-magnetic linear bearing 2 is provided with an upper permanent magnet clamping mechanism 4 with threads on the inner wall and the outer wall, and placed in the cavity formed between the upper permanent magnet clamping mechanism 4 and the non-magnetic linear bearing 2 The upper end ring permanent magnet 16, the top opening of the upper end permanent magnet clamping mechanism 4 is provided with an upper end permanent magnet fixing cover 3 with an external thread that is compatible with the upper end permanent magnet clamping mechanism 4 inner wall threads, for fixing the upper end ring Permanent magnet 16; the upper end permanent magnet fixed cover 3 and the non-magnetic linear bearing 2 are fixedly connected by the first bolt 14, and the outer end of the coil spring 7 is provided with an upper end coil spring clamping mechanism 5 fixed by the second bolt 13 up and down and the lower end helical spring clamping mechanism 8; the upper end helical spring clamping mechanism 5 is connected with the outer wall thread of the upper end permanent magnet clamping mechanism 4 through the internal thread of its upper end boss; the lower end boss of the lower end helical spring clamping mechanism 8 A lower permanent magnet clamping mechanism 9 with an external thread is fixed at the thread, and a lower annular permanent magnet 17 is placed in the lower permanent magnet clamping mechanism 9. The lower end of the lower permanent magnet clamping mechanism 9 is fixed with an internal thread for connecting to an external vibration source. fixed key 10; the upper end boss of the upper end helical spring clamping mechanism 5 is fixed by the third bolt 12 to the upper end permanent magnet clamping mechanism 4, and the lower end boss of the lower end helical spring clamping mechanism 8 is fixed by the fourth bolt 11 The lower permanent magnet clamping mechanism 9 is fixed.
通过旋钮上端永磁体夹持机构4和下端永磁体夹持机构9来调节上端环形永磁体16和下端环形永磁体17沿轴向的相对位置。The relative positions of the upper ring permanent magnet 16 and the lower ring permanent magnet 17 in the axial direction are adjusted by the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9 of the knob.
在所述的螺旋弹簧7的中心腔体内设置第一环形永磁体15，并通过质量支撑杆1与中间永磁体固定盖6以及螺旋弹簧7的内外螺纹将第一环形永磁体15安装紧固并随螺旋弹簧7一起运动。所述的螺旋弹簧7由上端螺旋弹簧夹持机构5和下端螺旋弹簧夹持机构8夹持，通过第二螺栓13将上端螺旋弹簧夹持机构5和下端螺旋弹簧夹持机构8锁紧使螺旋弹簧7被夹持紧固。The first annular permanent magnet 15 is arranged in the central cavity of the coil spring 7, and the first annular permanent magnet 15 is installed and fastened by the internal and external threads of the mass support rod 1 and the middle permanent magnet fixing cover 6 and the coil spring 7. Move together with coil spring 7. The coil spring 7 is clamped by the upper coil spring clamping mechanism 5 and the lower coil spring clamping mechanism 8, and the upper coil spring clamping mechanism 5 and the lower coil spring clamping mechanism 8 are locked by the second bolt 13 to make the coil The spring 7 is clamped and tightened.
优选的，所述的下端螺旋弹簧夹持机构8的下端通过内圆柱表面螺纹与下端永磁体夹持机构9外圆柱表面螺纹配合相连，并调节下端环形永磁体17沿轴向的位置。所述的下端永磁体夹持机构9通过内圆柱表面的螺纹与固定键10圆帽外螺纹相配合，并将下端环形永磁体17紧固其中。所述的下端螺旋弹簧夹持机构8的凸台侧面通过第四螺栓11将下端螺旋弹簧夹持机构8与下端永磁体夹持机构9紧固在一起。Preferably, the lower end of the lower coil spring clamping mechanism 8 is connected to the outer cylindrical surface of the lower permanent magnet clamping mechanism 9 through threads on the inner cylindrical surface, and the axial position of the lower annular permanent magnet 17 is adjusted. The lower end permanent magnet clamping mechanism 9 cooperates with the outer thread of the round cap of the fixing key 10 through the thread on the inner cylindrical surface, and fastens the lower end annular permanent magnet 17 therein. The boss side of the lower coil spring clamping mechanism 8 fastens the lower coil spring clamping mechanism 8 and the lower permanent magnet clamping mechanism 9 together through the fourth bolt 11 .
将上端永磁体固定盖3和固定键10在上端永磁体夹持机构4和下端永磁体夹持机构9分别旋进不同深度来调节安装的上端环形永磁体16和下端环形永磁体17的厚度。The upper permanent magnet fixed cover 3 and the fixed key 10 are respectively screwed into different depths in the upper permanent magnet clamping mechanism 4 and the lower permanent magnet clamping mechanism 9 to adjust the thickness of the upper end annular permanent magnet 16 and the lower end annular permanent magnet 17 installed.
所述不导磁直线轴承2采用金属铜，所述隔振器除不导磁直线轴承2外的其余部件采用非导磁的金属材料。The non-magnetic linear bearing 2 is made of metal copper, and the other parts of the vibration isolator except the non-magnetic linear bearing 2 are made of non-magnetic metal materials.
优选的，所述上端环形永磁体16和下端环形永磁体17与中间环形永磁体15的初始安装距离设置为10mm。Preferably, the initial installation distance between the upper ring permanent magnet 16 and the lower ring permanent magnet 17 and the middle ring permanent magnet 15 is set to 10 mm.
本发明的工作原理是：使用时，将质量支撑杆1的上端与被控结构相连，固定键10与外部振源相连；当质量支撑杆1、螺旋弹簧7以及中间环形永磁体15与上端螺旋弹簧夹持机构5和下端螺旋弹簧夹持机构8之间产生相对运动时，上端环形永磁体16和下端环形永磁体17分别吸引被螺旋弹簧7夹持的中间环形永磁体15；上端环形永磁体16、中间环形永磁体15和下端环形永磁体17产生的磁场在发明装置的非导磁金属结构中产生涡电流，从而产生与运动方向相反的阻尼力，提高并改善到了本发明的阻尼特性。在本发明装置中，上端环形永磁体16、中间环形永磁体15和下端环形永磁体17构成磁性弹簧，上端环形永磁体16和下端环形永磁体17作用在中间环形永磁体15上总的磁性恢复力与螺旋弹簧7为中间环形永磁体15提供的恢复力方向相反。因此，磁性弹簧可为隔振系统提供非线性磁性恢复力以及非线性负刚度，从而可以降低本发明装置在其工作位置附近的刚度，拓宽隔振频带，进而可以隔离低频振动。The working principle of the present invention is: when in use, the upper end of the mass support rod 1 is connected with the controlled structure, and the fixed key 10 is connected with the external vibration source; When relative movement occurs between the spring clamping mechanism 5 and the lower end helical spring clamping mechanism 8, the upper end annular permanent magnet 16 and the lower end annular permanent magnet 17 attract the middle annular permanent magnet 15 clamped by the coil spring 7 respectively; the upper end annular permanent magnet 16. The magnetic fields generated by the middle annular permanent magnet 15 and the lower end annular permanent magnet 17 generate eddy currents in the non-magnetic metal structure of the inventive device, thereby generating a damping force opposite to the direction of motion, which improves and improves the damping characteristics of the present invention. In the device of the present invention, the upper end annular permanent magnet 16, the middle annular permanent magnet 15 and the lower end annular permanent magnet 17 form a magnetic spring, and the upper end annular permanent magnet 16 and the lower end annular permanent magnet 17 act on the total magnetic recovery of the middle annular permanent magnet 15 The force is in the opposite direction to the restoring force provided by the helical spring 7 for the intermediate annular permanent magnet 15 . Therefore, the magnetic spring can provide nonlinear magnetic restoring force and nonlinear negative stiffness for the vibration isolation system, thereby reducing the stiffness of the device of the present invention near its working position, widening the frequency band of vibration isolation, and then isolating low frequency vibration.
Claims (5)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510097824.XA CN104747652B (en) | 2015-03-05 | 2015-03-05 | A kind of quasi-zero stiffness vibration isolators using helical spring in parallel with magnet spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510097824.XA CN104747652B (en) | 2015-03-05 | 2015-03-05 | A kind of quasi-zero stiffness vibration isolators using helical spring in parallel with magnet spring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104747652A true CN104747652A (en) | 2015-07-01 |
| CN104747652B CN104747652B (en) | 2016-08-17 |
Family
ID=53587773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510097824.XA Expired - Fee Related CN104747652B (en) | 2015-03-05 | 2015-03-05 | A kind of quasi-zero stiffness vibration isolators using helical spring in parallel with magnet spring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104747652B (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105156577A (en) * | 2015-09-07 | 2015-12-16 | 西安交通大学 | Overdamped vibration isolator capable of generating negative stiffness through inclined magnets |
| CN105179543A (en) * | 2015-10-08 | 2015-12-23 | 厦门艾美森新材料科技股份有限公司 | Mini magnetic damping control device and buffer cushion machine |
| CN107654551A (en) * | 2017-10-25 | 2018-02-02 | 西安交通大学 | A kind of multiple degrees of freedom low frequency vibration isolation device based on mode of oscillation and pendulum modal coupling |
| CN108662055A (en) * | 2018-07-30 | 2018-10-16 | 上海大学 | A kind of quasi-zero stiffness vibration isolators of positive and negative Stiffness |
| CN108708927A (en) * | 2018-05-24 | 2018-10-26 | 上海大学 | A kind of Variable Stiffness Vibration Isolator based on multilayer dielectric elastomer film |
| CN109027124A (en) * | 2018-09-12 | 2018-12-18 | 西安交通大学 | A kind of adjustable torsion quasi-zero stiffness vibration isolators of negative stiffness and control method |
| CN111963602A (en) * | 2020-08-31 | 2020-11-20 | 合肥工业大学 | Bistable Nonlinear Energy Hydrazine Based on Electromagnetic Negative Stiffness |
| CN111981085A (en) * | 2020-08-31 | 2020-11-24 | 合肥工业大学 | Elastic-hysteretic low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness |
| CN113759570A (en) * | 2020-06-02 | 2021-12-07 | Oppo广东移动通信有限公司 | Nose Pads and Glasses |
| CN113757285A (en) * | 2021-09-08 | 2021-12-07 | 重庆大学 | Negative stiffness generating mechanism and quasi-zero stiffness vibration isolator |
| CN115596795A (en) * | 2022-10-27 | 2023-01-13 | 重庆大学（Cn） | A viscous inertial damper |
| EP4549775A1 (en) * | 2023-10-30 | 2025-05-07 | Cryo Tech Ltd. | Tuned dynamic counter-balancer with magnetic spring |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109139760B (en) * | 2018-09-12 | 2020-08-14 | 西安交通大学 | A quasi-zero stiffness vibration isolator with parallel positive and negative stiffness |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU750172A1 (en) * | 1977-10-06 | 1980-07-23 | Предприятие П/Я А-1923 | Non-linear shock absorber |
| JPH09184539A (en) * | 1996-01-04 | 1997-07-15 | Yoshikazu Tsuchiya | Magnetic cushion |
| CN201554805U (en) * | 2009-10-30 | 2010-08-18 | 西格玛集团有限公司 | Spring shock absorber |
| CN103511529A (en) * | 2013-10-09 | 2014-01-15 | 哈尔滨工程大学 | Rigidity-adjustable electromagnetic vibration isolator |
| CN103775550A (en) * | 2014-02-14 | 2014-05-07 | 华中科技大学 | Single-degree-of-freedom magnetic vibration isolation device |
-
2015
- 2015-03-05 CN CN201510097824.XA patent/CN104747652B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU750172A1 (en) * | 1977-10-06 | 1980-07-23 | Предприятие П/Я А-1923 | Non-linear shock absorber |
| JPH09184539A (en) * | 1996-01-04 | 1997-07-15 | Yoshikazu Tsuchiya | Magnetic cushion |
| CN201554805U (en) * | 2009-10-30 | 2010-08-18 | 西格玛集团有限公司 | Spring shock absorber |
| CN103511529A (en) * | 2013-10-09 | 2014-01-15 | 哈尔滨工程大学 | Rigidity-adjustable electromagnetic vibration isolator |
| CN103775550A (en) * | 2014-02-14 | 2014-05-07 | 华中科技大学 | Single-degree-of-freedom magnetic vibration isolation device |
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105156577B (en) * | 2015-09-07 | 2017-03-29 | 西安交通大学 | A kind of employing tilting magnet produces the super damping isolator of negative stiffness |
| CN105156577A (en) * | 2015-09-07 | 2015-12-16 | 西安交通大学 | Overdamped vibration isolator capable of generating negative stiffness through inclined magnets |
| CN105179543A (en) * | 2015-10-08 | 2015-12-23 | 厦门艾美森新材料科技股份有限公司 | Mini magnetic damping control device and buffer cushion machine |
| CN107654551A (en) * | 2017-10-25 | 2018-02-02 | 西安交通大学 | A kind of multiple degrees of freedom low frequency vibration isolation device based on mode of oscillation and pendulum modal coupling |
| CN107654551B (en) * | 2017-10-25 | 2019-08-13 | 西安交通大学 | A kind of multiple degrees of freedom low frequency vibration isolation device based on mode of oscillation and pendulum modal coupling |
| CN108708927A (en) * | 2018-05-24 | 2018-10-26 | 上海大学 | A kind of Variable Stiffness Vibration Isolator based on multilayer dielectric elastomer film |
| CN108708927B (en) * | 2018-05-24 | 2019-04-30 | 上海大学 | A Variable Stiffness Vibration Isolator Based on Multilayer Dielectric Elastomer Film |
| CN108662055A (en) * | 2018-07-30 | 2018-10-16 | 上海大学 | A kind of quasi-zero stiffness vibration isolators of positive and negative Stiffness |
| CN109027124A (en) * | 2018-09-12 | 2018-12-18 | 西安交通大学 | A kind of adjustable torsion quasi-zero stiffness vibration isolators of negative stiffness and control method |
| CN109027124B (en) * | 2018-09-12 | 2020-02-11 | 西安交通大学 | A torsional quasi-zero stiffness vibration isolator with adjustable negative stiffness and its control method |
| CN113759570A (en) * | 2020-06-02 | 2021-12-07 | Oppo广东移动通信有限公司 | Nose Pads and Glasses |
| CN113759570B (en) * | 2020-06-02 | 2023-10-31 | Oppo广东移动通信有限公司 | Nose pad assembly and glasses |
| CN111963602A (en) * | 2020-08-31 | 2020-11-20 | 合肥工业大学 | Bistable Nonlinear Energy Hydrazine Based on Electromagnetic Negative Stiffness |
| CN111963602B (en) * | 2020-08-31 | 2021-09-21 | 合肥工业大学 | Bistable nonlinear energy hydrazine based on electromagnetic negative stiffness |
| CN111981085B (en) * | 2020-08-31 | 2022-03-15 | 合肥工业大学 | Elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness |
| CN111981085A (en) * | 2020-08-31 | 2020-11-24 | 合肥工业大学 | Elastic-hysteretic low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness |
| CN113757285A (en) * | 2021-09-08 | 2021-12-07 | 重庆大学 | Negative stiffness generating mechanism and quasi-zero stiffness vibration isolator |
| US12203526B2 (en) | 2021-09-08 | 2025-01-21 | Chongqing University | Negative stiffness generating mechanism and quasi-zero stiffness vibration isolator |
| CN115596795A (en) * | 2022-10-27 | 2023-01-13 | 重庆大学（Cn） | A viscous inertial damper |
| EP4549775A1 (en) * | 2023-10-30 | 2025-05-07 | Cryo Tech Ltd. | Tuned dynamic counter-balancer with magnetic spring |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104747652B (en) | 2016-08-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104747652B (en) | A kind of quasi-zero stiffness vibration isolators using helical spring in parallel with magnet spring | |
| CN103775550B (en) | Single-degree-of-freedom magnetic force isolation mounting | |
| CN104455181B (en) | A kind of accurate zero stiffness vibration isolator that adopts annular permanent magnet to produce negative stiffness | |
| CN105402297B (en) | Magnetic negative rigidity damper | |
| CN104179868B (en) | Active-passive integrated formula electromagnetism isolation mounting | |
| CN108443382A (en) | A kind of active-passive composite vibration isolator and control method using electromagnetism negative stiffness | |
| CN207818356U (en) | Three-phase reactors and motor drives | |
| CN108167362A (en) | It is a kind of using multi-electrode Squeeze Mode magnetic spring and the quasi-zero stiffness vibration isolators of swing rod | |
| CN107654551B (en) | A kind of multiple degrees of freedom low frequency vibration isolation device based on mode of oscillation and pendulum modal coupling | |
| CN103939520B (en) | A kind of passive vibration isolation device being applicable to low-frequency vibration | |
| CN105805204B (en) | Passive linear magnetic negative stiffness device | |
| CN102705414A (en) | Cylindrical electromagnetic damper | |
| CN111981085B (en) | Elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness | |
| CN111810585A (en) | A combined vibration isolation system | |
| CN105156577B (en) | A kind of employing tilting magnet produces the super damping isolator of negative stiffness | |
| CN206595877U (en) | Electromagnetic type touches the raising frequency vibrational energy harvester that shakes | |
| KR101440523B1 (en) | Dynamic vibration absorber using permanent magnets | |
| CN106763410B (en) | An ultra-low frequency non-resonant metal vibration isolator | |
| CN108019452B (en) | A kind of half actively controllable linear Stiffness electromagnetism vibration isolator | |
| CN109027124B (en) | A torsional quasi-zero stiffness vibration isolator with adjustable negative stiffness and its control method | |
| CN104373493B (en) | The low rigidity vibration isolator of a kind of magnetic in parallel | |
| CN205350179U (en) | Adopt asymmetric magnetism tooth structure to realize half initiative isolator of electromagnetic type of zero accurate rigidity characteristic | |
| Nguyen et al. | Development of high damping magneto-rheological mount for ship engines | |
| CN202579783U (en) | Novel electromagnetic damper | |
| CN207989620U (en) | A kind of half actively controllable linear Stiffness electromagnetism vibration isolator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160817 Termination date: 20190305 |