WO2020125067A1 - 一种准零刚度隔振器试验装置 - Google Patents

一种准零刚度隔振器试验装置 Download PDF

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WO2020125067A1
WO2020125067A1 PCT/CN2019/104277 CN2019104277W WO2020125067A1 WO 2020125067 A1 WO2020125067 A1 WO 2020125067A1 CN 2019104277 W CN2019104277 W CN 2019104277W WO 2020125067 A1 WO2020125067 A1 WO 2020125067A1
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stiffness
steel plate
fixed
screw
vibration
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English (en)
French (fr)
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仇越
罗忠
朱云鹏
韩贵鑫
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Northeastern University China
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Northeastern University China
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G01M7/025—Measuring arrangements
    • 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
    • F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
    • 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
    • F16F15/046—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 using combinations of springs of different kinds
    • 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
    • F16F15/067—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 wound springs
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/02—Gearings; Transmission mechanisms
    • G01M13/028—Acoustic or vibration analysis
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • 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
    • F16F2228/063—Negative 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
    • F16F2228/06—Stiffness
    • F16F2228/066—Variable stiffness

Definitions

  • the invention belongs to the technical field of vibration response test of a vibration isolator, and relates to a test device of a quasi-zero stiffness vibration isolator with flexible adjustment of positive and negative rigidities.
  • the present invention provides a test device for a quasi-zero stiffness isolator.
  • the present invention can flexibly adjust the positive and negative stiffness values of the platform to adjust the overall stiffness value of the system ; It can also stabilize the longitudinal vibration direction of the measured beam and reduce the impact of vibration in other directions on the test results; It can also achieve the replacement of the stiffness element at any time; this test device has more comprehensive functions and the adjustment of the stiffness value of the system The method is simpler, improves the adjustment accuracy than existing methods, and shortens the test period.
  • a test device for a quasi-zero stiffness isolator includes a negative stiffness adjustment mechanism, a positive stiffness adjustment mechanism, and a beam-damper block mechanism.
  • the negative stiffness adjustment mechanism drives the moving actuator to perform horizontal translation by adjusting the screw handwheel, thereby affecting the tension and compression state of the spring, thereby achieving adjustment of the negative stiffness of the overall device;
  • the negative stiffness adjustment mechanism includes a screw Handwheel, bearing seat A, bottom support plate, screw, moving actuator, screw slider, bearing seat B, spring, bolt, nut, deep groove ball bearing;
  • the bottom support plate is connected to bearing seat A through screws It is connected to the bearing bracket B;
  • the bearing bracket A and the bearing bracket B are fixed to the frame by bolts;
  • the screw is fixed to the bearing bracket A and the bearing bracket B by deep groove ball bearings, and the front end is connected to the screw handwheel by screws Fixed;
  • the mobile actuator is penetrated by the screw, and the screw slider and the screw are matched to ensure that the mobile actuator can move left and right on the bottom support plate; one end of the spring is fixed on the mobile actuator, and the other end is bolted Connected and fixed by the cooperation between the nut and the bolt.
  • the positive stiffness adjustment mechanism adjusts the nut to adjust the bending degree of the hollow steel plate to achieve the adjustment of the positive stiffness value of the overall system;
  • the positive stiffness adjustment mechanism includes a frame, a bottom support frame, and a hollow Steel plate, nut; the bottom of the bottom support base is connected to the hollow steel plate by screws, and the bottom is fixed to the rack by bolts; the support rod passes through the rack and cooperates with the nut, and the nut can be rotated on the support rod To move up and down to achieve the extrusion of the hollow steel plate to adjust the bending degree of the hollow steel plate, so as to complete the adjustment of the positive rigidity value of the overall system through the change of the rigidity of the steel plate.
  • the beam-damping block mechanism includes a supporting plate, a supporting base A, a damping block, a steel plate, a supporting rod, a mass block, and a supporting base; the supporting plate is fixed on the supporting base B and the bearing base A by screws, Limit the left and right movement of the damping block and the steel plate; the support rod is connected with the mass block, the steel plate and the damping block through the hole shaft, so that the beam-damping block mechanism is connected with the hollow steel plate; the support base A and the support base B are fixed by bolts On the frame, it is used to limit the movement of the damping block and the steel plate, so as to ensure the stability of the system during vibration.
  • the stiffness adjustment method of a quasi-zero stiffness vibration isolator test device is as follows:
  • Step 1 Adjust the negative stiffness value of the overall system
  • the movement of the screw slider is realized, so that the mobile actuator is driven to move on the bottom support plate, one end of the spring is fixed on the bolt, one end is fixed on the mobile actuator, the left and right of the mobile actuator
  • the movement drives the spring to compress or stretch, thereby adjusting the negative stiffness of the overall system.
  • Step 2 Adjust the positive stiffness value of the overall system
  • Step 3 Limit the lateral displacement of the beam-damping block mechanism during vibration
  • the lateral displacement of the beam-damper block mechanism during vibration is limited, so that the beam-damper block mechanism can perform longitudinal vibration when adding vibration to the mechanism .
  • Step 4 Designed for the quasi-zero stiffness of the overall mechanism
  • the longitudinal stiffness of the steel sheet by the lateral spring rate k 1 k 2 in combination with the rigidity of the entire adjustment mechanism reaches a state close to zero, the quality of the mass is m, a force is applied to the entire mechanism F (t), the lateral spring The displacement is x 0 , half the length L of the beam, and the vibration response formula of the overall mechanism is:
  • the test device of the variable-stiffness vibration isolator of the present invention adds negative stiffness elements and adopts a brand-new design scheme to solve the problems of the existing device that is bulky, complicated to operate, unable to complete flexible adjustment of stiffness, and difficult to replace stiffness elements.
  • the horizontal spring controls the displacement of the lead screw slider by the handwheel to control the stiffness of the negative stiffness element of the lateral spring, and controls the bending of the steel plate by tightening the bolts to control the stiffness of the positive stiffness element in the vertical direction.
  • the mobile actuator can be moved to achieve flexible installation and unloading of the lateral spring negative stiffness element.
  • FIG. 1 is a schematic view of the overall structure of a test device for a quasi-zero stiffness vibration isolator of the present invention
  • FIG. 2 is a schematic diagram of a negative stiffness adjustment mechanism of a test device for a quasi-zero stiffness isolator of the present invention
  • FIG. 3 is a schematic diagram of a positive stiffness adjustment mechanism of a test device for a quasi-zero stiffness isolator of the present invention
  • FIG. 4 is a schematic structural diagram of a beam-damping block mechanism of a test device for a quasi-zero stiffness vibration isolator of the present invention
  • FIG. 5 is a schematic diagram of a test device of a quasi-zero stiffness vibration isolator of the present invention.
  • 101 handwheel 102A bearing housing; 103 bottom support plate; 104 screw; 105 moving actuator; 106 screw slider; 107B bearing housing; 108 spring; 109 bolt; 110 nut; 111 deep groove ball bearing;
  • 301 support plate; 302A support base; 303 damping; 304 steel plate; 305 support rod; 306 mass; 307B support base;
  • the overall structure of a quasi-zero stiffness isolator test device includes a negative stiffness adjustment mechanism 1, a positive stiffness adjustment mechanism 2, and a beam-damper block mechanism 3.
  • the negative stiffness adjustment mechanism 1 is used to adjust the negative stiffness value of the system;
  • the negative stiffness adjustment mechanism includes a screw handwheel 101, a bearing seat A102, a bottom support plate 103, a screw 104, a mobile Actuator 105, screw slider 106, bearing seat B107, spring 108, bolt 109, nut 110, deep groove ball bearing 111;
  • the bottom support plate 103 is connected to the bearing seat A102 and the bearing seat B107 by screws;
  • the bearing seat A and the bearing bracket B are fixed on the frame 201 by bolts;
  • the screw 104 is fixed on the bearing bracket A and the bearing bracket B through the deep groove ball bearing 111, and the front end is connected and fixed to the screw handwheel 101 by screws; the movement is performed
  • the mechanism 105 is penetrated by the screw 104 and cooperates with the screw slider 106 and the screw to ensure that the mobile actuator 105 can move left and right on the bottom support plate; one end of the spring 108 is fixed on the mobile actuator and the other end is The
  • the positive stiffness adjustment mechanism 2 includes a frame 201; a bottom support frame 202; a hollow steel plate 203; a nut 204; the top of the bottom support frame 202 is connected to the hollow steel plate 203 by screws, and the bottom It is fixed on the frame 201 by bolts; the support rod 305 passes through the frame 201 and cooperates with the nut 204, and the nut can be moved up and down on the support rod by rotating the nut, thereby squeezing the hollow steel plate 203 to adjust The degree of bending of the hollow steel plate 203, so as to complete the adjustment of the positive rigidity value of the overall system through the change of the rigidity of the steel plate.
  • the beam-damping block mechanism includes a support base A302; a damping block 303; a steel plate 304; a support rod 305; a mass block 306; a support base B307; and the support plate 301 is fixed to the support base by screws B307 and bearing housing A102 are used to limit the left and right movement of the damping block 303 and the steel plate 304; the supporting rod 305 is connected with the mass block 306, the steel plate 304 and the damping block 303 through the hole shaft, so that the beam-damping block mechanism 3 It is connected with the hollow steel plate 203; the support base A302 and the support base B307 are fixed on the frame 201 by bolts, which are used to limit the movement of the damping block 303 and the steel plate 304, thereby ensuring the stability of the system during vibration.
  • Step 1 Adjust the negative stiffness value of the overall mechanism; realize the movement of the screw slider 106 by controlling the rotation of the screw handwheel 101, thereby driving the mobile actuator 105 to move on the bottom support plate 102; one end of the spring 108 It is fixed on the bolt 109, and the other end is fixed on the moving actuator 105.
  • the left and right movement of the moving actuator 105 drives the spring 108 to compress or stretch, thereby adjusting the negative stiffness value of the overall system.
  • Step 2 Adjust the positive stiffness value of the overall mechanism; squeeze the hollow steel plate 203 by rotating the nut 204, and adjust the bending degree of the hollow steel plate 203 by adjusting the position of the nut 204, thereby completing the change in the rigidity of the steel plate
  • the cooperation of the bottom support base 202 and the hollow steel plate 203 ensures the stability and accuracy of the operation of the positive stiffness adjustment mechanism.
  • Step 3 Limit the lateral displacement of the beam-damping block mechanism during vibration; through the fixed connection of the support plate 301 and the support base B307 and the bearing base A102, the lateral displacement of the beam-damping block mechanism during vibration is limited Position, so that the beam-damping block mechanism can perform longitudinal vibration when adding vibration to the mechanism.
  • Step 4 Designed for the quasi-zero stiffness of the overall mechanism
  • the stiffness of the whole mechanism is adjusted and combined to a state close to zero, the mass of the mass 306 is m402, and the force applied to the whole mechanism is F(t) 401, the displacement of the transverse spring is x 0 406, half the length of the beam L404, the vibration response formula of the overall mechanism can be expressed as:

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  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
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  • Mechanical Engineering (AREA)
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Abstract

一种准零刚度隔振器的试验装置，包括负刚度调节机构（1）、正刚度调节机构（2）、梁-阻尼块机构（3）。负刚度调节机构（1）、正刚度调节机构（2）依次相连，并安装在梁-阻尼块机构（3）上。装置既可实现被测系统平稳的纵向振动，又可对整体机构的正刚度与负刚度值进行灵活调整。适用于准零刚度隔振器的振动模型试验，解决了现准零刚度隔振器装置使用方法复杂、无法灵活调整体机构刚度、刚度元件替换过程复杂等问题。

Description

[根据细则26改正20.09.2019]　一种准零刚度隔振器试验装置 技术领域
本发明属于隔振器振动响应试验技术领域，涉及一种正、负刚度都可灵活调整的准零刚度隔振器的试验装置。
背景技术
工程技术中普遍存在着物理状态的循环变化或物体的往复运动现象即振动现象，车辆的震动让人感到不适，精密仪器的振动会影响测量的结果，地震的振动会对楼房的结构产生影响，桥梁和房屋的剧烈震动，在共振时可能发生突然崩塌，酿成死伤的悲剧，隔振器可以减缓该问题的影响。由于该问题属于复杂非线性振动动力学问题，涉及到冲击载荷、谐振、刚度非线性、阻尼非线性、材料非线性以及瞬态动力学等。目前的理论分析方法根本无法解决此类问题，因此试验研究是此类问题最有效的解决方法。由于其工作环境复杂、外物形状不一、因此模型试验的选用具有重要意义。
目前常用的隔振试验大多以几个刚度元件组合，搭建准零刚度隔振器试验平台，其不足之处在装置刚度的范围调节不灵活，装置的结构繁琐，装置的元件替换不方便、刚度元件的装载较为繁琐等。
发明内容
针对现有技术存在的问题，本发明提供了一种准零刚度隔振器的试验装置，本发明可以通过对平台的正刚度值、负刚度值进行灵活调整，从而实现系统整体刚度值的调节；还可以稳定被测梁的纵向的振动方向，降低其他方向的振动对试验结果带来的影响；也可实现刚度元件的随时替换；这种试验装置功能更为全面，系统的刚度值的调节方法更为简便，较现有方法提高了调节精度，同时缩短了试验周期。
为了实现上述的目的，本发明采用如下技术方案：
一种准零刚度隔振器的试验装置，该准零刚度隔振器的试验装置包括负刚 度调节机构，正刚度调节机构，梁—阻尼块机构。
所述的负刚度调节机构通过调节丝杠手轮，来带动移动执行机构进行水平方向的平移，进而影响弹簧的拉压状态，从而实现对整体装置负刚度的调整；负刚度调节机构包括丝杠手轮、轴承座A、底部支撑板、丝杠、移动执行机构、丝杠滑块、轴承座B、弹簧、螺栓、螺母、深沟球轴承；所述的底部支撑板通过螺钉与轴承座A和轴承座B相连；轴承座A和轴承座B通过螺栓固定在机架上；丝杠通过深沟球轴承固定在轴承座A与轴承座B上，其前端通过螺钉与丝杠手轮进行连接固定；移动执行机构被丝杠穿过，并通过丝杠滑块和丝杠相配合，确保移动执行机构可在底部支撑板上进行左右移动；弹簧一端固定在移动执行机构上，另一端与螺栓相连，并通过螺母与螺栓之间的配合进行固定。
所述的正刚度调节机构通过对螺母进行调节，进而对镂空钢板的弯曲程度进行调节，以实现整体系统正刚度值的调整；所述的正刚度调节机构包括机架、底部支撑机座、镂空钢板、螺母；所述的底部支撑机座顶部通过螺钉与镂空钢板相连，底部通过螺栓固定在机架上；支撑杆穿过机架并与螺母相配合，旋转螺母便可实现螺母在支撑杆上的上下移动，从而实现对镂空钢板的挤压，来调整镂空钢板的弯曲程度，从而通过钢板刚度的变化来完成对整体系统的正刚度值调节。
所述的梁-阻尼块机构包括支撑板、支撑座A、阻尼块、钢板、支撑杆、质量块、支撑座；所述的支撑板通过螺钉固定在支撑座B和轴承座A上，用来限制阻尼块和钢板的左右窜动；支撑杆通过孔轴配合与质量块、钢板和阻尼块相连接，从而使梁—阻尼块机构与镂空钢板相连接；支撑座A和支撑座B通过螺栓固定在机架上，其用来对阻尼块和钢板的窜动进行限制，从而保证系统振动时的稳定性。
一种准零刚度隔振器的试验装置的刚度调节方法步骤如下：
步骤一：针对整体系统负刚度值进行调节；
通过控制丝杠手轮的转动，来实现丝杠滑块的移动，从而带动移动执行机构在底部支撑板进行移动，弹簧一端固定在螺栓上，一端固定在移动执行机构上，移动执行机构的左右运动，带动弹簧进行压缩或拉伸，从而实现对整体系统的负刚度值的调节。
步骤二：针对整体系统正刚度值进行调节；
通过旋转螺母来实现对镂空钢板的挤压，通过调节螺母在支撑杆的位置来调整镂空钢板的弯曲程度，从而通过钢板刚度的变化来完成对整体系统正刚度值的调节，底部支撑机座和镂空钢板的配合来保证正刚度调节机构运行的稳定性与准确性。
步骤三：对振动时的梁-阻尼块机构进行横向位移的限位；
通过支撑板与支撑座B和轴承座A的固接，对梁-阻尼块机构在振动时的横向位移进行了限位，使梁-阻尼块机构在对机构加上振动时可以进行纵向的振动。
步骤四：针对整体机构的准零刚度进行了设计
通过纵向钢板的刚度k 1与横向弹簧刚度k 2，调整与组合使整体机构的刚度达到接近于零的状态，质量块的质量为m，对整体机构施加的力为F(t)，横向弹簧的位移为x 0，梁的一半长度L，整体机构的振动响应公式为：
Figure PCTCN2019104277-appb-000001
Figure PCTCN2019104277-appb-000002
本发明的一种变刚度隔振器的试验装置，增加了负刚度元件，采用了全新的设计方案，解决现有装置体积庞大、操作复杂、无法完成灵活调节刚度、更换刚度元件困难等问题。横向的弹簧作为整体系统的负刚度元件，通过手轮控制丝杠滑块的位移来控制横向弹簧负刚度元件的刚度大小，通过螺栓的拧紧控制钢板弯曲以控制垂直方向正刚度元件的刚度大小，从而实现系统整体的刚度调整，在初始安装阶段通过移动移动执行机构，可实现横向弹簧负刚度元件的灵活安装与卸载。
附图说明
图1为本发明一种准零刚度隔振器的试验装置整体结构示意图；
图2为本发明一种准零刚度隔振器的试验装置负刚度调节机构示意图；
图3为本发明一种准零刚度隔振器的试验装置正刚度调节机构示意图；
图4为本发明一种准零刚度隔振器的试验装置梁—阻尼块机构结构示意图；
图5为本发明一种准零刚度隔振器的试验装置的机构简图；
图中：1负刚度调节机构；2正刚度调节机构；3梁—阻尼块机构；
101手轮；102A轴承座；103底部支撑板；104丝杠；105移动执行机构；106丝杠滑块；107B轴承座；108弹簧；109螺栓；110螺母；111深沟球轴承；
201机架；202底部支撑机座；203镂空钢板；204螺母；
301支撑板；302A支撑座；303阻尼；304钢板；305支撑杆；306质量块；307B支撑座；
401整体机构施加的力；402质量块质量；403纵向钢板的刚度；404梁的一半长度；405横向弹簧刚度；406横向弹簧的位移。
具体实施方式
下面结合附图和技术方案，进一步说明本发明的具体实施方式。
如图1所示，本发明所述的一种准零刚度隔振器的试验装置整体结构，包括负刚度调节机构1，正刚度调节机构2，梁—阻尼块机构3。
如图2所示，所述的负刚度调节机构1用于对系统的负刚度值进行调节；负刚度调节机构包括丝杠手轮101、轴承座A102、底部支撑板103、丝杠104、移动执行机构105、丝杠滑块106、轴承座B107、弹簧108、螺栓109、螺母110、深沟球轴承111；所述的底部支撑板103通过螺钉与轴承座A102和轴承座B107相连；轴承座A和轴承座B通过螺栓固定在机架201上；丝杠104通过深沟球轴承111固定在轴承座A与轴承座B上，其前端通过螺钉与丝杠手轮101进行连接固定；移动执行机构105被丝杠104穿过，并通过丝杠滑块106和丝杠相 配合，确保移动执行机构105可在底部支撑板上进行左右移动；弹簧108一端固定在移动执行机构上，另一端与螺栓109相连，并通过螺母110与螺栓之间的配合进行固定。
如图3所示，所述的正刚度调节机构2包括机架201；底部支撑机座202；镂空钢板203；螺母204；所述的底部支撑机座202顶部通过螺钉与镂空钢板203相连，底部通过螺栓固定在机架201上；支撑杆305穿过机架201并与螺母204相配合，旋转螺母便可实现螺母在支撑杆上的上下移动，从而实现对镂空钢板203的挤压，来调整镂空钢板203的弯曲程度，从而通过钢板刚度的变化来完成对整体系统的正刚度值调节。
如图4所示，所述的梁-阻尼块机构包括支撑座A302；阻尼块303；钢板304；支撑杆305；质量块306；支撑座B307；所述的支撑板301通过螺钉固定在支撑座B307和轴承座A102上，用来限制阻尼块303和钢板304的左右窜动；支撑杆305通过孔轴配合与质量块306、钢板304和阻尼块303相连接，从而使梁—阻尼块机构3与镂空钢板203相连接；支撑座A302和支撑座B307通过螺栓固定在机架201上，其用来对阻尼块303和钢板304的窜动进行限制，从而保证系统振动时的稳定性。
一种准零刚度隔振器的试验装置刚度调节方法步骤如下：
步骤一：针对整体机构负刚度值进行调节；通过控制丝杠手轮101的转动，来实现丝杠滑块106的移动，从而带动移动执行机构105在底部支撑板102上进行移动；弹簧108一端固定在螺栓109上，另一端固定在移动执行机构105上，移动执行机构105的左右运动，带动弹簧108进行压缩或拉伸，从而实现对整体系统的负刚度值的调节。
步骤二：针对整体机构正刚度值进行调节；通过旋转螺母204，来实现对镂空钢板203的挤压，通过调节螺母204的位置来调整镂空钢板203的弯曲程度，从而通过钢板刚度的变化来完成对整体系统正刚度值的调节，底部支撑机座202 和镂空钢板203的配合来保证正刚度调节机构运行的稳定性与准确性。
步骤三：对振动时的梁-阻尼块机构进行横向位移的限位；通过支撑板301与支撑座B307和轴承座A102的固接，对梁-阻尼块机构在振动时的横向位移进行了限位，使梁-阻尼块机构在对机构加上振动时可以进行纵向的振动。
步骤四：针对整体机构的准零刚度进行了设计
通过纵向钢板的刚度k 1403与横向弹簧刚度k 2405，调整与组合使整体机构的刚度达到接近于零的状态，质量块306的质量为m402，对整体机构施加的力为F(t)401，横向弹簧的位移为x 0406，梁的一半长度L404，整体机构的振动响应公式可以表示为：
Figure PCTCN2019104277-appb-000003

Claims (4)

  1. 一种准零刚度隔振器的试验装置，其特征在于，包括负刚度调节机构(1)、正刚度调节机构(2)和梁-阻尼块机构(3)；
    所述的负刚度调节机构(1)通过调节丝杠手轮(101)，来带动移动执行机构(105)进行水平方向的平移，进而影响弹簧(108)的拉压状态，从而实现对整体装置负刚度的调整；负刚度调节机构包括丝杠手轮(101)、轴承座A(102)、底部支撑板(103)、丝杠(104)、移动执行机构(105)、丝杠滑块(106)、轴承座B(107)、弹簧(108)、螺栓(109)、螺母(110)和深沟球轴承(111)；所述的底部支撑板(103)通过螺钉与轴承座A(102)和轴承座B(107)相连；轴承座A(102)和轴承座B(107)通过螺栓固定在机架(201)上；丝杠(104)通过深沟球轴承(111)固定在轴承座A(102)与轴承座B(107)上，其前端通过螺钉与丝杠手轮(101)进行连接固定；移动执行机构(105)被丝杠(104)穿过，并通过丝杠滑块(106)和丝杠(104)相配合，确保移动执行机构(105)可在底部支撑板(103)上进行左右移动；弹簧(108)一端固定在移动执行机构(105)上，另一端与螺栓(109)相连，并通过螺母(110)与螺栓之间的配合进行固定；
    所述的正刚度调节机构(2)通过对螺母(204)进行调节，进而对镂空钢板(203)的弯曲程度进行调节，以实现整体系统正刚度值的调整；所述的正刚度调节机构(2)包括机架(201)、底部支撑机座(202)、镂空钢板(203)、螺母(204)；所述的底部支撑机座(202)顶部通过螺钉与镂空钢板(203)相连，底部通过螺栓固定在机架(201)上；支撑杆305穿过机架(201)并与螺母(204)相配合，旋转螺母(204)便可实现螺母在支撑杆(305)上的上下移动，从而实现对镂空钢板(203)的挤压，来调整镂空钢板的弯曲程度，从而通过钢板刚度的变化来完成对整体系统的正刚度值调节；
    所述的梁-阻尼块机构(3)包括支撑板(301)、支撑座A(302)、阻尼块(303)、钢板(304)、支撑杆(305)、质量块(306)、支撑座B(307)；所述的支撑板(301)通过螺钉固定在支撑座B(307)和轴承座A(102)上，用来限制阻尼块和钢板的左右窜动；支撑杆(305)通过孔轴配合与质量块(306)、钢板(304)和阻尼块(303)相连接，从而使梁—阻尼块机构(3)与镂空钢板(203)相连接；支撑座A(302)和支撑座B(307)通过螺栓固定在机架(201)上，其用来对阻尼块和钢板的窜动进行限制，从而保证系统振动时的稳定性。
  2. 根据权利要求1所述的一种准零刚度隔振器的试验装置，其特征在于，对振动时的梁-阻尼块机构进行横向位移的限位，通过支撑板(301)与支撑座B(307)和轴承座A(102)固接，对梁-阻尼块机构在振动时的横向位移进行了限位，使梁-阻尼块机构在对机构加上振动时可以进行纵向的振动。
  3. 根据权利要求1或2所述的一种准零刚度隔振器的试验装置，其特征在于，充当机构刚度元件的弹簧(108)与镂空钢板(202)的更换较为简便，卸载镂空钢板(203)固定在底部支撑机座(202)之间的螺钉，即对镂空钢板(203)更换；通过对移动执行机构(105)的位置进行左右调节，使弹簧(108)处于松弛状态，便对弹簧(108)进行卸载和更换。
  4. 用权利要求1-3任一所述一种准零刚度隔振器的试验装置的刚度调节方法，其特征在于，步骤如下：
    步骤一：针对整体机构负刚度值进行调节；
    通过控制丝杠手轮(101)的转动，来实现丝杠滑块(106)的移动，从而带动移动执行机构(105)在底部支撑板(102)上进行移动；弹簧(108)一端固定在螺栓(109)上，另一端固定在移动执行机构(105)上，移动执行机构(105)的左右运动，带动弹簧(108)进行压缩或拉伸，从而实现对整体系统 的负刚度值的调节；
    步骤二：针对整体机构正刚度值进行调节；
    通过旋转螺母(204)来实现对镂空钢板(203)的挤压，调节螺母(204)的位置来调整镂空钢板(203)的弯曲程度，从而通过钢板刚度的变化来完成对整体系统正刚度值的调节，底部支撑机座(202)和镂空钢板(203)的配合来保证正刚度调节机构运行的稳定性与准确性；
    步骤三：对振动时的梁-阻尼块机构进行横向位移的限位；
    通过支撑板(301)与支撑座B(307)和轴承座A(102)的固接，对梁-阻尼块机构在振动时的横向位移进行了限位，使梁-阻尼块机构在对机构加上振动时进行上下方向的纵向振动；
    步骤四：针对整体机构的准零刚度进行了设计
    通过纵向钢板的刚度(403)k 1与横向弹簧刚度(405)k 2的调整与组合使整体机构的刚度达到接近于零的状态，质量块(306)的质量(402)为m，对整体机构施加的力(401)为F(t)，横向弹簧的位移(406)为x 0，梁的一半长度(404)L，整体机构的振动响应公式表示为：
    Figure PCTCN2019104277-appb-100001
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