WO2016201890A1 - 频率可调复合减振器 - Google Patents

频率可调复合减振器 Download PDF

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Publication number
WO2016201890A1
WO2016201890A1 PCT/CN2015/095406 CN2015095406W WO2016201890A1 WO 2016201890 A1 WO2016201890 A1 WO 2016201890A1 CN 2015095406 W CN2015095406 W CN 2015095406W WO 2016201890 A1 WO2016201890 A1 WO 2016201890A1
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WO
WIPO (PCT)
Prior art keywords
base
flexible hinge
frequency
vibration damping
disposed
Prior art date
Application number
PCT/CN2015/095406
Other languages
English (en)
French (fr)
Inventor
杨志军
白有盾
陈新
陈超然
李成祥
Original Assignee
广东工业大学
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 广东工业大学 filed Critical 广东工业大学
Priority to US15/376,654 priority Critical patent/US9746123B2/en
Publication of WO2016201890A1 publication Critical patent/WO2016201890A1/zh

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    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
    • F16F15/073—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only leaf springs
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
    • F16F15/085—Use of both rubber and metal springs
    • 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
    • F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
    • F16F3/08—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of a material having high internal friction, e.g. rubber
    • F16F3/10—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of a material having high internal friction, e.g. rubber combined with springs made of steel or other material having low internal friction
    • 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
    • F16M—FRAMES, CASINGS OR BEDS OF ENGINES, MACHINES OR APPARATUS, NOT SPECIFIC TO ENGINES, MACHINES OR APPARATUS PROVIDED FOR ELSEWHERE; STANDS; SUPPORTS
    • F16M7/00—Details of attaching or adjusting engine beds, frames, or supporting-legs on foundation or base; Attaching non-moving engine parts, e.g. cylinder blocks
    • 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
    • F16F2224/00—Materials; Material properties
    • F16F2224/02—Materials; Material properties solids
    • 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
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/04—Frequency effects
    • 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
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/06—Stiffness
    • F16F2228/066—Variable stiffness
    • 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
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/08—Functional characteristics, e.g. variability, frequency-dependence pre-stressed
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/34—Flexural hinges

Definitions

  • the invention relates to the field of vibration damping devices, in particular to a frequency adjustable composite shock absorber.
  • the damper is mainly used to reduce the vibration output of the vibration source, thereby reducing noise and impact on other components.
  • Most of the common dampers are unadjustable stiffness, that is, the natural frequency of the damper is fixed and cannot be adjusted.
  • the damper whose dynamic characteristics such as the stiffness frequency are not adjustable often has many inconveniences.
  • the vibration characteristics of large equipment have a lot to do with the platform on which it is placed.
  • the use of a non-adjustable vibration damper may result in the equipment failing to meet the original design specifications in actual use.
  • the use of multiple sets of dampers of different stiffness specifications for on-site matching will bring many difficulties to the installation and commissioning of actual equipment.
  • a damper with adjustable dynamic characteristics such as stiffness frequency helps to avoid the above problem.
  • the adjustable damper disclosed in the patent 201410169456.0 is realized in the form of a conventional elastic element connected in parallel, and needs to be provided with a plurality of sets of elastic elements and a matching governor, which has high cost, and the damper of the form cannot realize the damper work.
  • the continuous adjustment of the stiffness allows only a preset discrete working stiffness adjustment.
  • the composite vibration absorber disclosed in Patent No. 201410299504.8 has the following main disadvantages: (1) The rigidity adjustment unit adopts a magnetorheological elastic body, the control is complicated and the cost is high; (2) the quality adjustment unit uses a liquid pump to change the liquid. The way in which the reserves change the quality, the response time of the regulating unit is long, and the additional heavy components such as the water storage tank need to be added, which is not conducive to its use in engineering, resulting in limited application range.
  • the main problem of the shock absorber disclosed in the patent 201410462858.X is that the magneto-rheological elastomer is used to adjust the rigidity, the requirements on the control system are high, and the overall cost is high, which limits Its scope of use.
  • an object of the present invention is to provide a frequency tunable composite damper that uses a low-cost adjustment scheme to achieve high- and low-frequency composite damping in a wider frequency band.
  • the frequency adjustable composite damper comprises a moving main body leg and a vibration damping device disposed on the base bearing platform; the vibration damping device is divided into an upper vibration damping device and a lower vibration damping device, wherein the vibration damping device is disposed inside a base of the cavity, the upper vibration damping device for suppressing low frequency vibration and the lower vibration damping device for absorbing additional high frequency vibration;
  • the upper vibration damping device includes a flexible hinge group and a pre-stress adjusting device, the flexible hinge group being disposed in an internal cavity of the base, and the pre-stress adjusting device for adjusting a natural frequency of the flexible hinge group
  • the flexible hinge sets are coupled, and the moving body legs are fixed to the bearing portions of the flexible hinge set.
  • the flexible hinge group includes a longitudinally disposed connecting side plate and an elastic steel sheet disposed laterally in the base, the connecting side plates being respectively fixed at two ends of the elastic steel sheet, the prestressing
  • the adjustment device changes the stiffness and natural frequency of the flexible hinge set by adjusting the distance between the connecting side plate and the inner side wall of the base to generate stress on the elastic steel sheet.
  • the prestressing adjustment device includes an adjusting bolt that sequentially passes through a side wall of the base and the connecting side plate.
  • the pre-stress adjusting device comprises a screw rod and a rotating electric machine, the screw rod sequentially passes through a side wall of the base and the connecting side plate, and the rotating electric machine drives the screw rod to perform a rotary motion.
  • the flexible hinge group is disposed in an inner cavity of the mounting frame, the mounting frame is fixed on an upper portion of the inner cavity of the base; and the prestressing device adjusts the connecting side plate and the installation The distance between the inner side walls of the frame creates stress on the elastic steel sheet to change the stiffness and natural frequency of the flexible hinge set.
  • the bottom plate of the mounting frame is provided with a limiting slot near the connecting side plate, the bottom surface of the limiting slot is lower than the ground of the mounting frame, and the limiting slot is in the length direction of the elastic steel sheet.
  • the width is greater than the thickness of the connecting side panels.
  • the lower vibration damping device is a damping element.
  • the anti-off bolt is not provided with the initial pre-tightening force, and the anti-off bolt is sequentially fixed through the moving main body leg, the flexible hinge group, the lower vibration damping device, the bottom plate of the base and the foundation bearing platform, and then fixed by the anti-off nut.
  • the bottom of the base is provided with a base fixing bolt, and the base fixing bolt sequentially passes through the bottom plate of the base and the base bearing platform.
  • Figure 1 is an overall isometric view of one embodiment of the present invention.
  • Figure 2 is a 1/4 cross-sectional view of the shaft side of one embodiment of the present invention.
  • Figure 3 is a front cross-sectional view of one embodiment of the present invention.
  • Flexible hinge group 201 connecting side plate 2011, elastic steel sheet 2012; mounting frame 202, prestressing adjustment device 203;
  • the frequency adjustable composite damper comprises a moving main body leg 1 and a vibration damping device disposed on the basic bearing platform 6 ; the vibration damping device is divided into an upper vibration damping device and a lower vibration damping device.
  • the vibration damping device is disposed on the base 301 having an internal cavity, and the upper vibration damping device for suppressing low frequency vibration is connected in series with the lower vibration damping device for absorbing additional high frequency vibration;
  • the upper vibration damping device includes a flexible hinge group 201 and a pre-stress adjusting device 203, and the flexible hinge group 201 is disposed in an internal cavity of the base 301 for adjusting the
  • the pre-stress adjusting device 203 of the natural frequency of the flexible hinge group 201 is coupled to the flexible hinge group 201, and the moving main body leg 1 is fixed to the bearing portion of the flexible hinge group 201.
  • ⁇ is the excitation frequency and ⁇ n is the natural frequency
  • the conventional rigid-fixed damper cannot be adapted to the specific quality of the equipment and the excitation frequency, and cannot meet the requirements of quality and drive frequency variation.
  • the invention adjusts the natural frequency of the system by adjusting the stiffness of the flexible hinge, and adapts to the vibration damping performance requirements under different mass and different excitation frequency conditions.
  • the natural frequency of the flexible hinge group 201 is adjusted by the prestressing adjustment device 203,
  • the low-frequency vibration isolation requirement is adapted to different masses and different excitation frequencies;
  • the flexible hinge group 201 is placed in the internal cavity of the base 301, and the sidewall of the internal cavity of the base 301 is used to carry the adjustment force and limit the amplitude.
  • the lower vibration damping device is disposed at a lower portion of the inner cavity of the base 301 for absorbing high-frequency vibration energy; in the technical solution, the frequency is adjustable and the high-frequency vibration damping device absorbs vibration to achieve different quality, Effective isolation of high and low frequency bands of different excitation frequency vibration systems, simple operation and low cost.
  • the flexible hinge group 201 includes a longitudinally disposed connecting side plate 2011 and an elastic steel sheet 2012 disposed laterally in the base 301, and the connecting side plates 2011 are respectively fixed at both ends of the elastic steel sheet 2012.
  • the pre-stress adjusting device 203 changes the rigidity and the natural frequency of the flexible hinge group by stressing the elastic steel sheet 2012 by adjusting the distance between the connecting side plate 2011 and the inner side wall of the base 301.
  • the distance between the connecting side plate 2011 and the inner side wall of the base 301 is changed accordingly.
  • the degree of deformation of the associated elastic steel sheet 2012 will change, and the natural frequency of the entire flexible hinge group 201 is changed to realize effective isolation of high and low frequency bands of different quality and different excitation frequency vibration systems, simple structure, convenient adjustment, and low cost. high.
  • the prestressing adjustment device 203 adjusts the distance between the connecting side plate 2011 and the inner side wall of the base 301 from the two ends or one end of the elastic steel sheet 2012, so that the degree of deformation of the elastic steel sheet 2012 can be changed.
  • the adjustment method is flexible and simple.
  • the connecting side plate 2011 and the elastic steel piece 2012 are an integrated structure, and the whole piece of material is obtained by milling, electric discharge machining, etc., thereby avoiding assembly error of the parts and improving the movement precision.
  • the pre-stress adjusting device 203 includes an adjusting bolt that sequentially passes through a side wall of the base 301 and the connecting side plate 2011.
  • the large end of the adjusting bolt is located on the outer side wall of the base 301, and the small end sequentially passes through the side wall of the base 301 and the connecting side plate 2011 to manually adjust the elastic steel.
  • the connecting side plate 2011 moves in a direction away from the inner side wall of the base 301, and the elastic steel sheet 2012 receives the pressing force from the both ends inward, and the rigidity becomes large.
  • the stiffness becomes smaller, and the natural frequency of the system is affected by the inherent characteristics of the stiffness system. The stiffness changes and the natural frequency changes accordingly. Manual adjustment is flexible and convenient.
  • the prestressing adjustment device 203 includes a lead screw that sequentially passes through a side wall of the base 301 and the connecting side plate, and a rotating electric machine that drives the screw shaft to perform a rotational motion.
  • the screw rod sequentially passes through the side wall of the base 301 and the connecting side plate 2011, and the threaded rod and the connecting side plate 2011 are screwed and rotated.
  • the motor drives the screw to rotate, so that the connecting side plate 2011 moves away from the inner side wall of the base 301, and the elastic steel piece 2012 receives the pressing force from the two ends inward, and the rigidity becomes larger; otherwise, the rigidity becomes smaller, and
  • the natural frequency of the system is affected by the inherent characteristics of the stiffness system. The stiffness changes and the natural frequency changes accordingly.
  • the drive motor is adjusted and the automatic adjustment accuracy is high.
  • the flexible hinge group 201 is disposed in an inner cavity of the mounting frame 202, and the mounting frame 202 is fixed on an upper portion of the inner cavity of the base 301; the pre-stress adjusting device 203 adjusts the connecting side plate 2011 by The distance between the inner sidewalls of the mounting frame 202 creates stress on the resilient steel sheet 2012 that changes the stiffness and natural frequency of the flexible hinge set.
  • the flexible hinge group 201 is disposed in the mounting frame 202, and the pre-stress adjusting device 203 adjusts the distance between the connecting side plate 2011 and the inner side wall of the mounting frame 202.
  • the mounting frame 202 is placed in the base 301.
  • the internal cavity is convenient, and the installation is accurate, ensuring the effect of frequency adjustment and vibration reduction.
  • the bottom plate of the mounting frame 202 is disposed on the two sides of the connecting side plate 2011, and the bottom surface of the limiting slot 7 is lower than the ground of the mounting frame 202.
  • the limiting slot 7 is in the elastic steel. Film 2012 long The width in the degree direction is greater than the thickness of the connecting side plate 2011.
  • the limiting slot 7 facilitates positioning when the connecting side panel 2011 is installed.
  • the movable range of the connecting side panel 2011 is also limited, and the excessive deformation of the elastic steel sheet 2012 is avoided to reduce the vibration effect. Not good.
  • the lower damping device is a damping element.
  • the lower vibration damping device is a damping element that absorbs high frequency, and is directly disposed in the internal cavity of the base 301, and is connected with the upper vibration damping device to form a secondary vibration isolation system, and the vibration damping effect is optimal.
  • a retaining bolt 5 is provided which does not apply an initial pre-tightening force, and the retaining bolt 5 passes through the moving main body leg 1, the flexible hinge group 201, the lower vibration damping device 4, the bottom plate of the base 301, and the base bearing platform 6 through the defense. Remove the nut and fix it.
  • the flexible hinge group 201 and the lower vibration damping device 4 are connected in series and fixed by sequentially passing through the moving main body leg 1, the flexible hinge group 201, the lower vibration damping device 4, the bottom plate of the base 301, and the retaining bolt 5 of the base bearing platform 6.
  • the retaining bolt 5 is not applied with an initial preload, it is mainly used to prevent accidental disengagement of the moving body leg 1 in extreme cases.
  • the moving body leg 1 is provided with a hollow cavity through which the retaining bolt 5 passes.
  • the anti-off bolt 5 is inserted into the working host leg 1
  • the hollow cavity body is then passed through the lower vibration damping device 4, the bottom plate of the base 301 and the base bearing platform 6, and then fixed by the anti-off nut, which is compact in structure and convenient to install.
  • the bottom of the base 301 is provided with a base fixing bolt 302, which in turn passes through the bottom plate of the base 301 and the base bearing platform 6.
  • the base 301 is fixed by the base fixing bolt 302, and the accidental disengagement of the moving main body leg 1 and the entire vibration damping device is placed under extreme conditions to ensure its use.

Abstract

频率可调复合减振器，包括设置在基础承载平台（6）上的运动主机支脚（1）和减振装置；减振装置分为上部减振装置和下部减振装置，减振装置设于具有内部腔体的基座（301），用于抑制低频振动的上部减振装置与用于吸收额外高频振动的下部减振装置串接；上部减振装置包括基于柔性铰链组（201）的弹性构件和预应力调节装置（203），柔性铰链组（201）设置在基座（301）的内部腔体，用于调节柔性铰链组（201）固有频率的预应力调节装置（203）与柔性铰链组（201）连接，运动主机支脚（1）固定在柔性铰链组（201）的承重部。整个柔性铰链组（201）的固有频率发生改变，实现不同质量、不同激励频率振动系统高、低频段的有效隔离，结构简单，调节方便，成本不高。

Description

频率可调复合减振器 技术领域
本发明涉及减振装置领域，特别是一种频率可调复合减振器。
背景技术
减振器主要用于减小振动源的振动输出，从而减低噪音以及对其他部件的冲击。常见的减振器多为刚度不可调节型，即减振器的固有频率固定，不可调节。在实际的工程应用中，上述刚度频率等动态特性不可调的减振器往往存在诸多不便。例如，大型设备的振动特性与其所安放的平台有很大关系，采用刚度不可调节型减振器可能导致设备在实际使用场合无法达到原有的设计指标。采用多组不同刚度规格的减振器来现场匹配的方式又会给实际设备的安装调试带来诸多困难。由此，刚度频率等动态特性可调的减振器有助于规避上述问题。
专利201410169456.0中公开的可调式减振器，其实现形式为传统的弹性元件并联，需要设置多组弹性元件以及配套的调控器，成本较高，且该形式的减振器不能实现减振器工作刚度的连续可调，只能实现预设的离散工作刚度调节。
专利201410299504.8中公开的复合型吸振器，其存在的主要不足有：(1)刚度调节单元采用磁流变弹性体，控制较为复杂，成本较高；(2)质量调节单元采用液体泵来改变液体储量进而改变质量的方式，调节单元的响应时间较长，且需要额外增加储水箱等笨重部件，不利于其在工程中的使用，导致其适用范围有限。
专利201410462858.X中公开的减震器存在的主要问题为：采用磁流变弹性体方式调节刚度，对控制系统的要求较高，且整体成本较高，限制了 其使用范围。
发明内容
针对上述问题，本发明的目的在于提出一种频率可调复合型减振器，采用低成本的调节方案来实现较宽频带内高低频率的复合减振。
为达此目的，本发明采用以下技术方案：
频率可调复合减振器，包括设置在基础承载平台上的运动主机支脚和减振装置；所述减振装置分为上部减振装置和下部减振装置，所述减振装置设于具有内部腔体的基座，用于抑制低频振动的所述上部减振装置与用于吸收额外高频振动的所述下部减振装置串接；
所述上部减振装置包括柔性铰链组和预应力调节装置，所述柔性铰链组设置在所述基座的内部腔体，用于调节所述柔性铰链组固有频率的所述预应力调节装置与所述柔性铰链组连接，所述运动主机支脚固定在所述柔性铰链组的承重部。
进一步的：所述柔性铰链组包括纵向设置的连接侧板和横向设置在所述基座内的弹性钢片，所述连接侧板分别固定在所述弹性钢片的两端，所述预应力调节装置通过调节所述连接侧板与所述基座的内侧壁之间的距离，在弹性钢片上产生应力而改变所述柔性铰链组的刚度和固有频率。
进一步的：所述预应力调节装置包括调节螺栓，所述调节螺栓依次穿过所述基座的侧壁和所述连接侧板。
进一步的：所述预应力调节装置包括丝杆和旋转电机，所述丝杆依次穿过所述基座的侧壁和所述连接侧板，所述旋转电机驱动所述丝杆作旋转运动。
进一步的：所述柔性铰链组设置在安装框的内部空腔，所述安装框固定在所述基座的内部腔体上部；所述预应力调节装置通过调节所述连接侧板与安装 框的内侧壁之间的距离，在弹性钢片上产生应力而改变所述柔性铰链组的刚度和固有频率。
进一步的：所述安装框的底板靠近所述连接侧板的两侧设有限位槽，所述限位槽的底面低于所述安装框的地面，所述限位槽在弹性钢片长度方向的宽度大于所述连接侧板的厚度。
进一步的：所述下部减振装置为阻尼元件。
进一步的：设有不施加初始预紧力的防脱螺栓，防脱螺栓依次穿过运动主机支脚、柔性铰链组、下部减振装置、基座的底板和基础承载平台后通过防脱螺母固定。
进一步的，所述基座的底部设有基座固定螺栓，所述基座固定螺栓依次穿过所述基座的底板和基础承载平台。
本发明的有益效果：通过所述预应力调节装置通过调节所述连接侧板与所述基座的内侧壁之间的距离，则弹性钢片两端的连接侧板之间的距离随之被改变，连带的弹性钢片的变形程度会发生改变，则整个柔性铰链组的固有频率发生改变，实现不同质量、不同激励频率振动系统高、低频段的有效隔离，结构简单，调节方便，成本不高。
附图说明
图1是本发明的一个实施例的整体轴测图；
图2是本发明的一个实施例的轴侧1/4剖视图；
图3是本发明的一个实施例的正面剖视图。
其中：运动主机支脚1；
柔性铰链组201，连接侧板2011，弹性钢片2012；安装框202，预应力调节装置203；
基座301，基座固定螺栓302；
阻尼元件4，防脱螺栓5，基础承载平台6，限位槽7。
具体实施方式
下面结合附图并通过具体实施方式来进一步说明本发明的技术方案。
如图1所示，频率可调复合减振器，包括设置在基础承载平台6上的运动主机支脚1和减振装置；所述减振装置分为上部减振装置和下部减振装置，所述减振装置设于具有内部腔体的基座301，用于抑制低频振动的所述上部减振装置与用于吸收额外高频振动的所述下部减振装置串接；
如图2及图3所示，所述上部减振装置包括柔性铰链组201和预应力调节装置203，所述柔性铰链组201设置在所述基座301的内部腔体，用于调节所述柔性铰链组201固有频率的所述预应力调节装置203与所述柔性铰链组201连接，所述运动主机支脚1固定在所述柔性铰链组201的承重部。
不论阻尼大小，欲得隔振效果，频率比需要满足条件：
Figure PCTCN2015095406-appb-000001
其中，ω为激励频率，ωn为固有频率；
即
Figure PCTCN2015095406-appb-000002
其中，k为刚度，m为质量；
因此，欲得到较好的隔振效果，应采用刚性系数较低的隔振器或适当加大机器底座的质量；λ的值越大，隔振效果越好，而在实际应用中常取λ＝2.5～5。
然而，由于被减振设备的质量和激励频率往往是未知的，因此，传统刚度固定的减振器不能只能适应于特定的质量的设备和激励频率，无法满足质量和驱动频率变化的要求。本发明通过对柔性铰链刚度的调节，进而调节系统的固有频率，适应不同质量、不同激励频率工况下的减振性能要求。
本发明中，通过预应力调节装置203调节柔性铰链组201的固有频率，用 于适应不同质量，不同激励频率的低频隔振要求；所述柔性铰链组201置于基座301的内部腔体，基座301内部腔体的侧壁用于承载调节力和对振幅进行限位，防止柔性铰链失效；而下部减振装置设于基座301内部空腔的下部，用于吸收高频振动能量；本技术方案中，通过频率可调和高频减振装置吸振，实现不同质量、不同激励频率振动系统高、低频段的有效隔离，操作简单，成本低。
所述柔性铰链组201包括纵向设置的连接侧板2011和横向设置在所述基座301内的弹性钢片2012，所述连接侧板2011分别固定在所述弹性钢片2012的两端，所述预应力调节装置203通过调节所述连接侧板2011与所述基座301的内侧壁之间的距离，在弹性钢片2012上产生应力而改变所述柔性铰链组的刚度和固有频率。
通过所述预应力调节装置203通过调节所述连接侧板2011与所述基座301的内侧壁之间的距离，则弹性钢片2012两端的连接侧板2011之间的距离随之被改变，连带的弹性钢片2012的变形程度会发生改变，则整个柔性铰链组201的固有频率发生改变，实现不同质量、不同激励频率振动系统高、低频段的有效隔离，结构简单，调节方便，成本不高。
所述预应力调节装置203从弹性钢片2012两端或一端的调节所述连接侧板2011与所述基座301的内侧壁之间的距离，使得弹性钢片2012的变形程度发生改变即可，调节方式灵活简单。
且本实施例中，连接侧板2011和弹性钢片2012为一体式结构，由整块材料经过铣削、电火花加工等方式获取，避免了零件的装配误差，可以提高运动精度。
所述预应力调节装置203包括调节螺栓，所述调节螺栓依次穿过所述基座301的侧壁和所述连接侧板2011。
预应力调节装置203的一种实施例结构，调节螺栓的大端位于所述基座301的外侧壁，小端依次穿过基座301的侧壁和所述连接侧板2011，手动调节弹性钢片2012两端的调节螺栓向基座301的内侧方向旋进时，连接侧板2011向远离基座301内侧壁的方向运动，弹性钢片2012受到由两端向内的挤压力，刚度变大；反之则刚度变小，而系统的固有频率受刚度这一系统的固有特性影响，刚度改变，固有频率也会随之改变，手动调节，灵活方便。
所述预应力调节装置203包括丝杆和旋转电机，所述丝杆依次穿过所述基座301的侧壁和所述连接侧板，所述旋转电机驱动所述丝杆作旋转运动。
预应力调节装置203的另一种实施例结构，丝杆依次穿过所述基座301的侧壁和所述连接侧板2011，丝杆与所述连接侧板2011之间为螺纹连接，旋转电机驱动所述丝杆转动，使得连接侧板2011向远离基座301内侧壁的方向运动，弹性钢片2012受到由两端向内的挤压力，刚度变大；反之则刚度变小，而系统的固有频率受刚度这一系统的固有特性影响，刚度改变，固有频率也会随之改变，驱动电机调节，自动调节精度高。
所述柔性铰链组201设置在安装框202的内部空腔，所述安装框202固定在所述基座301的内部腔体上部；所述预应力调节装置203通过调节所述连接侧板2011与安装框202的内侧壁之间的距离，在弹性钢片2012上产生应力而改变所述柔性铰链组的刚度和固有频率。
将柔性铰链组201设置在安装框202内，预应力调节装置203调节所述连接侧板2011与安装框202的内侧壁之间的距离即可，安装时，将安装框202放入基座301的内部腔体即可，方便且安装准确，保证频率调节和减振的效果。
所述安装框202的底板靠近所述连接侧板2011的两侧设有限位槽7，所述限位槽7的底面低于所述安装框202的地面，所述限位槽7在弹性钢片2012长 度方向的宽度大于所述连接侧板2011的厚度。
限位槽7方便了连接侧板2011安装时定位，在通过连接侧板2011进行调节时，也限制了连接侧板2011的活动范围，避免了弹性钢片2012发生过大的变形使得减振效果不佳。
所述下部减振装置为阻尼元件。
下减振装置为吸收高频的阻尼元件，直接设置在基座301的内部腔体，与上部减振装置连接成二级隔振系统，减振效果最佳。
设有不施加初始预紧力的防脱螺栓5，防脱螺栓5依次穿过运动主机支脚1、柔性铰链组201、下部减振装置4、基座301的底板和基础承载平台6后通过防脱螺母固定。
通过依次穿过运动主机支脚1、柔性铰链组201、下部减振装置4、基座301的底板和基础承载平台6的防脱螺栓5，将柔性铰链组201和下部减振装置4串联后固定在基座301内，且防脱螺栓5是不施加初始预紧力的，主要用于防止在极端情况下运动主机支脚1的意外脱离。
而本实施例中，运动主机支脚1设有供防脱螺栓5穿过的中空腔体，运动主机支脚1插入所述柔性铰链组201的承重部后，防脱螺栓5插入运功主机支脚1的中空腔体，再依次穿过下部减振装置4、基座301的底板和基础承载平台6后通过防脱螺母固定，结构紧凑，安装方便。
所述基座301的底部设有基座固定螺栓302，所述基座固定螺栓302依次穿过所述基座301的底板和基础承载平台6。
通过基座固定螺栓302将基座301固定，放置在极端情况下运动主机支脚1及整个减振装置的意外脱离，保证其使用。
以上结合具体实施例描述了本发明的技术原理。这些描述只是为了解释本 发明的原理，而不能以任何方式解释为对本发明保护范围的限制。基于此处的解释，本领域的技术人员不需要付出创造性的劳动即可联想到本发明的其它具体实施方式，这些方式都将落入本发明的保护范围之内。

Claims (9)

  1. 一种频率可调复合减振器，包括设置在基础承载平台上的运动主机支脚和减振装置，其特征在于：所述减振装置分为上部减振装置和下部减振装置，所述减振装置设于具有内部腔体的基座，用于抑制低频振动的所述上部减振装置与用于吸收额外高频振动的所述下部减振装置串接；
    所述上部减振装置包括柔性铰链组和预应力调节装置，所述柔性铰链组设置在所述基座的内部腔体，用于调节所述柔性铰链组固有频率的所述预应力调节装置与所述柔性铰链组连接，所述运动主机支脚固定在所述柔性铰链组的承重部。
  2. 根据权利要求1所述的频率可调复合减振器，其特征在于：所述柔性铰链组包括纵向设置的连接侧板和横向设置在所述基座内的弹性钢片，所述连接侧板分别固定在所述弹性钢片的两端，所述预应力调节装置通过调节所述连接侧板与所述基座的内侧壁之间的距离，在弹性钢片上产生应力而改变所述柔性铰链组的刚度和固有频率。
  3. 根据权利要求2所述的频率可调复合减振器，其特征在于：所述预应力调节装置包括调节螺栓，所述调节螺栓依次穿过所述基座的侧壁和所述连接侧板。
  4. 根据权利要求2所述的频率可调复合减振器，其特征在于：所述预应力调节装置包括丝杆和旋转电机，所述丝杆依次穿过所述基座的侧壁和所述连接侧板，所述旋转电机驱动所述丝杆作旋转运动。
  5. 根据权利要求2所述的频率可调复合减振器，其特征在于：所述柔性铰链组设置在安装框的内部空腔，所述安装框固定在所述基座的内部腔体上部；所述预应力调节装置通过调节所述连接侧板与安装框的内侧壁之间的距离，在弹性钢片上产生应力而改变所述柔性铰链组的刚度和固有频率。
  6. 根据权利要求5所述的频率可调复合减振器，其特征在于：所述安装框的底板靠近所述连接侧板的两侧设有限位槽，所述限位槽的底面低于所述安装框的地面，所述限位槽在弹性钢片长度方向的宽度大于所述连接侧板的厚度。
  7. 根据权利要求1所述的频率可调复合减振器，其特征在于：所述下部减振装置为阻尼元件。
  8. 根据权利要求1所述的频率可调复合减振器，其特征在于：设有不施加初始预紧力的防脱螺栓，防脱螺栓依次穿过运动主机支脚、柔性铰链组、下部减振装置、基座的底板和基础承载平台后通过防脱螺母固定。
  9. 根据权利要求1所述的频率可调复合减振器，其特征在于：所述基座的底部设有基座固定螺栓，所述基座固定螺栓依次穿过所述基座的底板和基础承载平台。
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