CN111853126A - Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency - Google Patents

Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency Download PDF

Info

Publication number
CN111853126A
CN111853126A CN202010723892.3A CN202010723892A CN111853126A CN 111853126 A CN111853126 A CN 111853126A CN 202010723892 A CN202010723892 A CN 202010723892A CN 111853126 A CN111853126 A CN 111853126A
Authority
CN
China
Prior art keywords
spring
springs
pair
oblique
vertical
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
Application number
CN202010723892.3A
Other languages
Chinese (zh)
Other versions
CN111853126B (en
Inventor
赵峰
巩晓赟
王才东
陈鹿民
何文斌
田二林
杜辉翔
李俊苇
关明航
许平
仝博博
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhengzhou University of Light Industry
Original Assignee
Zhengzhou University of Light Industry
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 Zhengzhou University of Light Industry filed Critical Zhengzhou University of Light Industry
Priority to CN202010723892.3A priority Critical patent/CN111853126B/en
Publication of CN111853126A publication Critical patent/CN111853126A/en
Application granted granted Critical
Publication of CN111853126B publication Critical patent/CN111853126B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1028—Vibration-dampers; Shock-absorbers using inertia effect the inertia-producing means being a constituent part of the system which is to be damped
    • 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
    • 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
    • F16F2230/0011—Balancing, e.g. counterbalancing to produce static balance

Landscapes

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

Abstract

The invention provides a quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and having high linear resonance frequency, which comprises three pairs of inclined spring assemblies, a vertical spring assembly, a loading platform assembly and a supporting structure, wherein the three pairs of inclined spring assemblies are arranged on the vertical spring assembly; the loading platform assembly is hinged with the three pairs of inclined spring assemblies, the loading platform assembly is in contact connection with the vertical spring, and the three pairs of inclined spring assemblies and the vertical spring assembly are fixedly connected with the supporting structure through bolts; in the initial state, the cross points of the three pairs of inclined spring assemblies are positioned between the vertical distance between the fixed points of the pair of inclined spring assemblies on the upper side and the static balance position, and the static balance position is the middle point of the two fixed points of the middle inclined spring assembly. The invention keeps the wide quasi-zero stiffness range, simultaneously reduces the distance from the initial position to the static balance position, and has small bearing mass; under the condition that the vertical spring stiffness is not changed, the linear natural frequency is increased, the vibration isolation frequency band difference between the quasi-zero stiffness system and the corresponding linear system is increased, and the vibration isolation frequency band performance of the quasi-zero stiffness system is greatly improved.

Description

Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency
Technical Field
The invention relates to the technical field of mechanical structure vibration isolation, in particular to a quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and having high linear resonant frequency.
Background
The high static low dynamic vibration isolator is formed by combining a negative stiffness structure and a positive stiffness structure, so that the negative stiffness counteracts the positive stiffness, the dynamic stiffness reaches a quasi-zero state, and meanwhile, higher static bearing capacity is kept. Types of structures that achieve negative stiffness are cam rollers, magnetic springs, canted coil springs or beams, plate structures, and truss structures (X-shaped), among others. The existing high-static low-dynamic vibration isolator is narrow in quasi-zero stiffness range and unsatisfactory in vibration isolation performance, so that the invention patent with the application number of 201910864288.X discloses a three-diagonal spring structure, and the quasi-zero stiffness range is obviously improved.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a quasi-zero steel vibration isolation device based on three pairs of inclined springs and having high linear resonance frequency, and solves the technical problem of large corresponding linear resonance frequency in the prior art.
The technical scheme of the invention is realized as follows:
a quasi-zero stiffness vibration isolation device based on high linear resonant frequency of three pairs of inclined springs comprises an inclined spring assembly, a vertical spring assembly, a loading platform assembly and a supporting structure; the carrying platform assembly is hinged with the inclined spring assembly, the carrying platform assembly is in contact connection with the vertical spring, and the inclined spring assembly and the vertical spring assembly are both connected with the supporting structure; under the initial state, the cross points of the three pairs of inclined spring assemblies are positioned between the vertical distance between the fixed points of the pair of inclined spring assemblies on the upper side and the static balance position, namely the middle point of the two fixed points of the middle inclined spring assembly, and the rigidity corresponding to the vibration isolation device is realized under the configuration
Figure BDA0002600988740000011
The calculation formula of (2) is as follows:
Figure BDA0002600988740000012
wherein,
Figure BDA0002600988740000013
the stiffness ratio of the upper side or lower side inclined spring to the vertical spring is shown, the stiffness and length of the upper side and lower side inclined springs are the same, k1Represents a linear stiffness coefficient, k, of the upper pair of oblique springs or the lower pair of oblique springs2The linear stiffness coefficient of the vertical spring is shown,
Figure BDA0002600988740000014
represents the stiffness ratio, k, of a central pair of canted springs to a perpendicular spring3The linear stiffness coefficient of the middle pair of oblique springs is shown, the length of the middle pair of oblique springs is the same as that of the upper pair or the lower pair of oblique springs,
Figure BDA0002600988740000015
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000016
representing intermediate variables，
Figure BDA0002600988740000017
The dimensionless horizontal distance of the hinge points at the two ends of the oblique spring is shown, a represents the horizontal distance between the hinge points at the two ends of the oblique spring, and h1Indicating the vertical distance from the initial position to a pair of oblique spring fixation points on the upper side,
Figure BDA0002600988740000021
representing a dimensionless displacement, x representing the displacement from the intersection of the three diagonal springs in the initial state,
Figure BDA0002600988740000022
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000023
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000024
a dimensionless amount of compression of the upper pair of canted springs in the initial state, an amount of compression of the upper pair of canted springs in the initial state,
Figure BDA0002600988740000025
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000026
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000027
represents an intermediate parameter, h represents a vertical distance between the initial position and the static equilibrium position, d represents a half of a vertical distance between the fixing points of the upper pair of oblique springs and the fixing points of the lower pair of oblique springs,
Figure BDA0002600988740000028
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000029
Figure BDA00026009887400000210
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000211
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000212
representing the dimensionless amount of compression of the middle pair of canted springs in the initial state,1indicating the amount of compression of the center pair of canted springs in the initial state,
Figure BDA00026009887400000213
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000214
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000215
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000216
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000217
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000218
showing the dimensionless amount of compression of the lower pair of canted springs in the initial state,2represents the compression amount dp of the lower oblique spring pair in the initial state5Representing an intermediate variable p5For dimensionless displacement
Figure BDA00026009887400000219
D is a differential of8Representing an intermediate variable p8For dimensionless displacement
Figure BDA00026009887400000220
Differentiation of (2).
The intermediate variable p5For dimensionless displacement
Figure BDA00026009887400000221
Differential dp of5The expression of (a) is:
Figure BDA00026009887400000222
the intermediate variable p8For dimensionless displacement
Figure BDA00026009887400000223
Differential dp of8The expression of (a) is:
Figure BDA00026009887400000224
the calculation formula of the force corresponding to the shock isolation device is as follows:
Figure BDA00026009887400000225
wherein,
Figure BDA00026009887400000226
representing dimensionless force and f representing dimensionless force.
The inclined spring assembly is provided with three pairs, the three pairs of inclined spring assemblies comprise a pair of upper inclined spring assemblies, a pair of middle inclined spring assemblies and a pair of lower inclined spring assemblies, the pair of upper inclined springs and the pair of lower inclined springs are arranged in a vertically symmetrical mode by taking the pair of middle inclined springs as centers, the pair of upper inclined spring assemblies, the pair of middle inclined spring assemblies and the pair of lower inclined spring assemblies are all arranged on two sides of the loading platform assembly in a symmetrical mode, the pair of upper inclined springs and the pair of lower inclined springs have the same rigidity and length, and the pair of upper inclined springs, the pair of lower inclined springs and the pair of middle inclined springs have the same length; the upper oblique spring assemblies, the middle oblique spring assemblies and the lower oblique spring assemblies respectively comprise oblique springs, bearing seats, linear bearing fixing plates, second linear bearings, oblique spring guide rods and oblique rod U-shaped connecting pieces; the bearing seat is movably connected with the supporting structure through a first radial bearing, and the bearing seat, the linear bearing fixing plate and the second linear bearing are fixedly connected through bolts and nuts in sequence; an inner hole of the second linear bearing is inserted into one end of the inclined spring guide rod, the other end of the inclined spring guide rod is fixedly connected with the inclined rod U-shaped connecting piece through a bolt, and the inclined rod U-shaped connecting piece is movably connected with the loading platform assembly; the inclined spring guide rod is arranged inside the inclined spring, one end of the inclined spring is in end face contact with the inclined rod U-shaped connecting piece, the other end of the inclined spring is in end face contact with the second linear bearing, and the inclined spring is in a compressed state.
The loading platform assembly comprises a loading platform, a sleeve, a first linear bearing, an inclined spring connecting plate, a linear bearing fixing plate and a bearing supporting seat; the lower part of the carrying platform is fixedly connected with the sleeve, the lower part of the sleeve is fixedly connected with the first linear bearing, and a vertical spring assembly is movably arranged in the first linear bearing; the loading platform, the sleeve, the first linear bearing and the inclined spring connecting plate are connected through a bolt and a nut in sequence; the inclined spring connecting plate is fixedly connected with the bearing support fixing piece through a bolt, the bearing support fixing piece is fixedly connected with the bearing support seat through a bolt, and the bearing support seat is movably connected with the inclined rod U-shaped connecting piece through a second radial bearing.
The vertical spring assembly comprises a vertical guide rod and a vertical spring, the vertical guide rod is arranged in the vertical spring, the top end of the vertical guide rod is arranged in a first linear bearing, the top end of the vertical spring is in contact connection with the bottom end of the first linear bearing, the bottom end of the vertical guide rod is fixed in a hole of a guide rod fixing seat, the bottom end of the vertical spring is in contact connection with the top end of the guide rod fixing seat, and the vertical spring is in a compressed state.
The middle part of the guide rod fixing seat is provided with a round hole, a vertical guide rod is fixedly arranged in the round hole, and a vertical spring is arranged on the upper part of the round hole.
The supporting structure comprises a supporting frame and a bracket U-shaped connecting piece; the support frame is provided with a groove, the groove is connected with a support U-shaped connecting piece through a bolt, and the support U-shaped connecting piece is movably connected with the bearing seat through a first radial bearing.
A debugging method of a quasi-zero rigid vibration isolation device based on high linear resonant frequency of three diagonal springs comprises the following steps:
s1, according to the mass m of the loading platform and the rigidity k of the vertical spring2Determining the static equilibrium position mg/k2；
S2, according to the static equilibrium position mg/k obtained in the step S12The positions of the inclined springs are adjusted by moving the position of the U-shaped connecting piece of the bracket on the supporting frame, so that the middle pair of inclined springs are positioned in the horizontal direction of the static balance position mg/k2, and the upper pair of inclined springs and the lower pair of inclined springs are symmetrical along the horizontal direction of the static balance position mg/k 2;
and S3, the support frames on the two sides are transversely and symmetrically moved through a symmetrical moving support frame U-shaped connecting piece on the upper side and the lower side, so that the negative stiffness of the three groups of inclined springs and the positive stiffness k2 of the vertical springs are offset to reach zero dynamic stiffness, and finally the support frame U-shaped connecting piece is fixed on the support frame, and the support frame is synchronously fixed with an external device.
The beneficial effect that this technical scheme can produce: compared with the invention patent 201910863713.3, under the condition that the vertical spring is kept unchanged, the distance from the initial position to the static balance position is reduced, the bearing mass is small, the linear natural frequency is increased, the vibration isolation frequency band difference between the quasi-zero stiffness system and the corresponding linear system is increased, the wide vibration isolation frequency band performance of the quasi-zero stiffness is improved, and the problem that the vibration isolation frequency band of the quasi-zero stiffness vibration isolator is close to the vibration isolation frequency band of the corresponding linear system is solved; the quasi-zero stiffness vibration isolator (corresponding linear system) not only greatly reduces the vibration amplitude, but also greatly reduces the vibration isolation frequency and increases the vibration isolation bandwidth.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic diagram of the initial state of the present invention.
Fig. 2 is a schematic view of the static equilibrium state of the present invention.
FIG. 3 is an example of a quasi-zero stiffness curve of the present invention.
Fig. 4 is a schematic structural diagram according to the present invention.
Fig. 5 is a plan view of a linear bearing retainer plate of the present invention.
Fig. 6 is a left side view of the bearing housing of the present invention.
Fig. 7 is a front view of the bearing housing of the present invention.
Fig. 8 is a top view of the connection between the linear bearing fixing plate and the bearing seat according to the present invention.
Fig. 9 is a front view of the bracket U-shaped connector of the present invention.
Fig. 10 is a top view of a bracket U-shaped connector of the present invention.
FIG. 11 is a front view of the diagonal member U-shaped connector of the present invention.
FIG. 12 is a top view of the diagonal member U-shaped connector of the present invention.
Fig. 13 is a front view of the bearing support of the present invention.
Fig. 14 is a front view of a linear bearing retainer plate of the present invention.
Fig. 15 is a left side view of the linear bearing fixing plate of the present invention.
Fig. 16 is a plan view of a linear bearing retainer plate of the present invention.
Fig. 17 is a front view of the canted spring coupling plate of the present invention.
FIG. 18 is a top view of the canted spring coupling plate of the present invention.
Fig. 19 is a front view of the stand of the present invention.
Fig. 20 is a left side view of the stand of the present invention.
Fig. 21 is a top view of the support bracket of the present invention.
FIG. 22 is a schematic view showing the connection between the linear bearing fixing plate, the bearing support and the inclined spring connecting plate according to the present invention.
In the figure, 1-supporting frame, 1-1-slotting, 1-2-screw hole, 2-bracket U-shaped connecting piece, 2-1-small hole IV, 2-2-concave hole I, 3-bearing seat, 3-1-small hole III, 3-2-big hole II, 4-first radial bearing, 5-linear bearing fixing plate, 5-1-big hole I, 5-2-small hole I, 5-3-small hole II, 6-second linear bearing, 7-oblique spring guide rod, 8-oblique spring, 9-carrying platform, 10-bolt, 11-sleeve, 12-first linear bearing, 13-oblique spring connecting plate, 13-1-big hole V, 13-2-small hole VIII, 13-3-concave hole III, 14-nut, 15-bearing support fixing piece, 15-1-big hole IV, 15-2-small hole VII, 16-bearing support, 16-1-big hole III, 16-2-small hole VI, 17-second radial bearing, 18-inclined rod U-shaped connecting piece, 18-1-small hole V, 18-2-concave hole II, 19-vertical guide rod, 20-vertical spring and 21-guide rod fixing seat.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without inventive effort based on the embodiments of the present invention, are within the scope of the present invention.
A quasi-zero stiffness vibration isolation device based on high linear resonant frequency of three pairs of inclined springs comprises an inclined spring assembly, a vertical spring assembly, a loading platform assembly and a supporting structure; the model of the high static low dynamic vibration isolation device with high linear resonance frequency and wide quasi-zero stiffness range formed by the three pairs of oblique springs is shown in fig. 1 and fig. 2, wherein fig. 1 is a schematic diagram of the initial state of the vibration isolation device, the initial state is a state without mass load, and fig. 2 is a schematic diagram of the working state of the vibration isolation device, namely the state of a static balance position, and the static balance position is a static balance point. The inclined spring is configured as follows, the initial position of the loading platform is positioned between the line AB and the static balance position, is not lower than the static balance position and is not higher than the line AB. The static balance position is at the central point position of the ABFE rectangle, and the pair of oblique springs at the upper side and the lower side have the same rigidity and length, and have the same length but different rigidity as the middle oblique spring. One end of each inclined spring 8 is hinged to the vibration isolation platform 9, the other end of each inclined spring 8 is inserted into the second linear bearing 6, and the second linear bearing 6 is hinged to the support frame 1. AO and BO are a pair (upper pair) of canted springs, CO and DO are a second pair (middle pair) of canted springs, and EO and FO are a third pair (lower pair) of canted springs. According to the model designed by the invention, the distance from the initial position to the static balance position is reduced, the bearing quality is small, the linear natural frequency is increased, the vibration isolation frequency band difference between the quasi-zero stiffness system and the corresponding linear system is increased, the wide vibration isolation frequency band performance of the quasi-zero stiffness is improved, and the problem that the vibration isolation frequency band of the quasi-zero stiffness vibration isolator is close to that of the corresponding linear system is solved; the quasi-zero stiffness vibration isolator (corresponding linear system) not only greatly reduces the vibration amplitude, but also greatly reduces the vibration isolation frequency and increases the vibration isolation bandwidth.
In an initial state, the cross points of the three pairs of inclined spring assemblies are positioned between the vertical distance between the fixed point of the pair of inclined spring assemblies on the upper side and the static balance position, and the calculation formula of the force corresponding to the shock isolation device is as follows:
Figure BDA0002600988740000051
wherein,
Figure BDA0002600988740000052
representing dimensionless force, f representing dimensionless force, a representing horizontal distance between hinge points at two ends of the oblique spring, k2Represents the linear stiffness coefficient, h, of the vertical spring1Indicating the vertical distance from the initial position to a pair of oblique spring fixation points on the upper side,
Figure BDA0002600988740000053
represents a dimensionless displacement, alpha represents a stiffness ratio of a pair of oblique springs at the upper side or a pair of oblique springs at the lower side to a vertical spring (20), alpha1Represents the stiffness ratio, p, of a pair of diagonal springs to a vertical spring (20) in the middle1、p2、p3、p4、p5、p6、p7、p8、p9Both represent intermediate variables.
Under the initial state, the cross points of the three pairs of inclined spring assemblies are positioned between the vertical distance of the fixed point of the upper inclined spring assembly and the static balance position, and under the configuration, the rigidity corresponding to the vibration isolation device
Figure BDA0002600988740000061
The calculation formula of (2) is as follows:
Figure BDA0002600988740000062
wherein,
Figure BDA0002600988740000063
showing the stiffness ratio of the upper or lower inclined spring to the vertical spring, the upper and lower inclined springs having the same stiffness and length, k1Represents a linear stiffness coefficient, k, of the upper pair of oblique springs or the lower pair of oblique springs2The linear stiffness coefficient of the vertical spring is shown,
Figure BDA0002600988740000064
represents the stiffness ratio, k, of a central pair of canted springs to a perpendicular spring3The linear stiffness coefficient of the middle pair of oblique springs is shown, the length of the middle pair of oblique springs is the same as that of the upper pair or the lower pair of oblique springs,
Figure BDA0002600988740000065
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000066
the intermediate variable is represented by a number of variables,
Figure BDA0002600988740000067
the dimensionless horizontal distance of the hinge points at the two ends of the oblique spring is shown, a represents the horizontal distance between the hinge points at the two ends of the oblique spring, and h1Indicating the vertical distance from the initial position to a pair of oblique spring fixation points on the upper side,
Figure BDA0002600988740000068
representing a dimensionless displacement, x representing the displacement from the intersection of the three diagonal springs in the initial state,
Figure BDA0002600988740000069
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000610
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000611
a dimensionless amount of compression of the upper pair of canted springs in the initial state, an amount of compression of the upper pair of canted springs in the initial state,
Figure BDA00026009887400000612
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000613
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000614
represents an intermediate parameter, h represents a vertical distance between the initial position and the static equilibrium position, d represents a half of a vertical distance between the fixing points of the upper pair of oblique springs and the fixing points of the lower pair of oblique springs,
Figure BDA00026009887400000615
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000616
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000617
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000618
representing the dimensionless amount of compression of the middle pair of canted springs in the initial state,1indicating the amount of compression of the center pair of canted springs in the initial state,
Figure BDA00026009887400000619
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000620
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000621
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000622
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000623
the intermediate variable is represented by a number of variables,
Figure BDA00026009887400000624
showing the dimensionless amount of compression of the lower pair of canted springs in the initial state,2represents the compression amount dp of the lower oblique spring pair in the initial state5Representing an intermediate variable p5For dimensionless displacement
Figure BDA00026009887400000625
D is a differential of8Representing an intermediate variable p8For dimensionless displacement
Figure BDA00026009887400000626
Differentiation of (2).
The intermediate variable p5For dimensionless displacement
Figure BDA00026009887400000627
Differential dp of5The expression of (a) is:
Figure BDA0002600988740000071
the intermediate variable p8For dimensionless displacement
Figure BDA0002600988740000072
Differential dp of8The expression of (a) is:
Figure BDA0002600988740000073
seven independent parameters
Figure BDA0002600988740000074
Can take more parameter value combinations according to the rigidity of three groups of inclined springs
Figure BDA0002600988740000075
The calculation formula of (a) can obtain a quasi-zero stiffness curve as shown in fig. 3, and fig. 3 is just a few examples of wide quasi-zero stiffness range which can be achieved, and there are many parameter combinations like this. Compared with the quasi-zero stiffness curve of a single group of inclined springs, the quasi-zero stiffness characteristic of the three groups of inclined springs is improved, so that the vibration damping performance of the invention is improved.
A quasi-zero stiffness vibration isolation device based on high linear resonant frequency of three pairs of inclined springs is shown in figure 4 and comprises an inclined spring assembly, a vertical spring assembly, a carrying platform assembly and a supporting structure; the carrying platform assembly is hinged with the inclined spring assembly, the carrying platform assembly is in contact connection with the vertical spring, and the inclined spring assembly and the vertical spring assembly are both connected with the supporting structure; the inclined spring assembly is provided with three pairs, the three pairs of inclined spring assemblies comprise an upper pair of inclined spring assemblies, a middle pair of inclined spring assemblies and a lower pair of inclined spring assemblies, the upper pair of inclined springs and the lower pair of inclined springs are vertically and symmetrically arranged by taking the middle pair of inclined springs as a center, the upper pair of inclined spring assemblies, the middle pair of inclined spring assemblies and the lower pair of inclined spring assemblies are symmetrically arranged at two sides of the loading platform assembly, the upper pair of inclined springs and the lower pair of inclined springs have the same rigidity and length, and the upper pair of inclined springs, the lower pair of inclined springs and the middle pair of inclined springs have the same length; the pair of oblique spring assembly of upside, a pair of oblique spring assembly in the middle of and a pair of oblique spring assembly of downside are located same vertical plane, adjust three pairs of oblique spring assembly when being convenient for use. The upper oblique spring assemblies, the middle oblique spring assemblies and the lower oblique spring assemblies respectively comprise oblique springs 8, bearing seats 3, linear bearing fixing plates 5, second linear bearings 6, oblique spring guide rods 7 and oblique rod U-shaped connecting pieces 18; the bearing seat 3 is movably connected with the supporting structure through a first radial bearing 4, and the bearing seat 3, the linear bearing fixing plate 5 and the second linear bearing 6 are fixedly connected through bolts and nuts in sequence; an inclined spring guide rod 7 is movably arranged in the second linear bearing 6; as shown in fig. 5, a large hole I5-1 is formed in the middle of the linear bearing fixing plate 5, 4 small holes I5-2 are uniformly formed around the large hole I5-1, a second linear bearing 6 is arranged in the large hole I5-1, the linear bearing fixing plate 5 is fixedly connected with the second linear bearing 6 through the small holes I5-2, an inclined spring guide rod 7 is movably arranged in the second linear bearing 6, and a small hole II 5-3 is formed at the vertex of the linear bearing fixing plate 5; as shown in figures 6-7, both ends of the bearing seat 3 are provided with small holes III 3-1, the small holes III 3-1 are correspondingly connected with small holes II 5-3 (as shown in figure 8), the middle part of the bearing seat 3 is provided with large holes II 3-2, and the large holes II 3-2 are connected with the bracket U-shaped connecting piece 2. As shown in fig. 9-10, the U-shaped bracket connector 2 is provided with a concave hole I2-2 and a small hole IV 2-1, the small hole IV 2-1 on the U-shaped bracket connector 2 is connected with the large hole II 3-2 on the bearing seat 3 through the first radial bearing 4, and the concave hole I2-2 is connected with the support frame 1 through a bolt. An inner hole of the second linear bearing 6 is inserted into one end of the inclined spring guide rod 7, the other end of the inclined spring guide rod 7 is fixedly connected with an inclined rod U-shaped connecting piece 18 through a bolt, and the inclined rod U-shaped connecting piece 18 is movably connected with the loading platform assembly; the inclined spring guide rod 7 is arranged inside the inclined spring 8, the inclined spring guide rod 7 guides the inclined spring 8 to prevent the inclined spring 8 from bending and deforming, one end of the inclined spring 8 is in end face contact with the inclined rod U-shaped connecting piece 18, the other end of the inclined spring 8 is in end face contact with the second linear bearing 6, and the inclined spring 8 is in a compressed state. The number of the inclined springs 8 is four, the inclined springs 8 are used in pairs to generate rigidity, and compared with a single group of inclined springs, the range of quasi-zero rigidity achieved is longer; the three pairs (six) of inclined springs 8 do reciprocating compression and return motion along the inclined spring guide rods 7 to form three pairs of inclined spring structures, so that the rigidity generated by the vertical springs 20 which are compressed in a reciprocating mode along the vertical guide rods 19 is offset, the overall dynamic rigidity reaches a quasi-zero state, and meanwhile, the static bearing capacity is high.
The loading platform assembly comprises a loading platform 9, a sleeve 11, a first linear bearing 12, an inclined spring connecting plate 13, a linear bearing fixing plate 15 and a bearing supporting seat 16; the inclined spring connecting plate 13 is fixedly connected with the bearing support fixing piece 15 through a bolt, the bearing support fixing piece 15 is fixedly connected with the bearing support base 16 through a bolt, and the bearing support base 16 is movably connected with the inclined rod U-shaped connecting piece 18 through a second radial bearing 17. As shown in fig. 14-16, the two ends of the linear bearing fixing plate 15 are provided with large holes IV 15-1, the middle of the linear bearing fixing plate 15 is provided with two protrusions, and the protrusions are provided with small holes VII 15-2; as shown in fig. 17-18, a large hole V13-1 is formed in the middle of the inclined spring connecting plate 13, a first linear bearing 12 is arranged in the large hole V13-1, 4 small holes VIII 13-2 are uniformly formed around the large hole V13-1, a bolt 10 is arranged in the small hole VIII 13-2, and the bolt 10 sequentially penetrates through the objective platform 9, the sleeve 11, the first linear bearing 12 and the small hole VIII 13-2 from top to bottom and is fixed by a nut 14; two sides of the inclined spring connecting plate 13 are provided with symmetrical concave holes III 13-3, the concave holes III 13-3 correspond to the large holes IV 15-1, and the linear bearing fixing plate 15 is fixedly connected with the inclined spring connecting plate 13 by penetrating through the large holes IV 15-1 and screwing into the concave holes III 13-3 through bolts, as shown in figure 22; as shown in fig. 13, a large hole III 16-1 and a small hole VI 16-2 are provided on the bearing support base 16, the small hole VI 16-2 and the small hole VII 15-2 are fixedly connected with a nut through a bolt, the large hole III 16-1 is movably connected with an inclined rod U-shaped connecting piece 18 through a second radial bearing 17, the inclined rod U-shaped connecting piece 18 is fixedly connected with an inclined spring guide rod 7, and the inclined spring guide rod 7 is provided in the second linear bearing 6. As shown in the figures 11-12, a concave hole II 18-2 and a small hole V18-1 are arranged on the inclined rod U-shaped connecting piece 18, the small hole V18-1 is connected with a large hole III 16-1 through a second radial bearing 17, and the concave hole II 18-2 is fixedly connected with the inclined spring guide rod 7. The lower part of the carrying platform 9 is fixedly connected with a sleeve 11, the lower part of the sleeve 11 is fixedly connected with a first linear bearing 12, and a vertical spring assembly is movably arranged in the first linear bearing 12; the loading platform 9, the sleeve 11, the first linear bearing 12 and the inclined spring connecting plate 13 are connected through the bolt 10 and the nut 14 in sequence, so that the four components can move up and down synchronously; the first linear bearing 12 is reciprocated up and down along the vertical guide rod 19 while compressing the vertical spring 20. The objective platform 9 is the vibration isolation platform, and the object to be isolated is placed on the objective platform 9, and because the displacement excitation that the quasi-zero rigidity characteristic was transmitted from bottom fixed equipment can be attenuated by a wide margin on transmitting to the objective platform 9, consequently can place the instrument and equipment sensitive to vibration or the structure that needs to be protected on the objective platform 9 to play the effect of protection.
The vertical spring assembly comprises a vertical guide rod 19 and a vertical spring 20, the vertical guide rod 19 is arranged in the vertical spring 20, the vertical guide rod 19 plays a role of vertically positioning the vertical spring 20, in order to avoid the deformation of the vertical spring 20 during the movement, the top end of the vertical guide rod 19 is arranged in the first linear bearing 12 so that the first linear bearing 12 can move up and down along the upper part of the vertical guide rod 19, the top end of the vertical spring 20 is in contact connection with the bottom end of the first linear bearing 12 so as to limit the vertical spring 20, the bottom end of the vertical guide rod 19 is fixed in the hole of the guide rod fixing seat (21), the bottom end of the vertical spring 20 is in contact connection with the top end of the guide rod fixing seat 21 so that the first linear bearing 12 can move up and down along the top end of the guide rod 19, the first linear bearing 12 may compress the vertical spring 20, with the vertical spring 20 in a compressed state. The middle part of guide bar fixing base 21 is equipped with the round hole, and the round hole internal fixation is equipped with vertical guide bar 19, vertical guide bar 19 and guide bar fixing base 21 clearance fit to avoid the slope of vertical guide bar 19, round hole upper portion is provided with perpendicular spring 20, and perpendicular spring 20 contacts with the upper portion of guide bar fixing base 21.
The supporting structure comprises a supporting frame 1 and a bracket U-shaped connecting piece 2; 4 support frames 1 are symmetrically arranged on two sides of the loading platform 9, the support frames 1 can be fixed with an external device through bolts, the support frames 1 can transversely move on the external device through adjusting the fixed positions of the bolts, and the rigidity of the inclined springs and the rigidity of the vertical springs are adjusted to be mutually offset to achieve the characteristic of quasi-zero rigidity; as shown in fig. 19 to 21, a slot 1-1 is formed in the support frame 1, the slot 1-1 is connected to the support U-shaped connector 2 through a bolt, and the support U-shaped connector 2 can move freely and without obstacles in the slot 1-1, so as to prevent the oblique spring guide rod 7 from moving and interfering with the support frame 1 when the oblique spring 8 is compressed along the oblique spring guide rod 7 and the oblique spring guide rod 7 passes through the second linear bearing 6 for a long distance. The bracket U-shaped connecting piece 2 is movably connected with the bearing seat 3 through a first radial bearing 4.
In this embodiment, the number of the oblique springs 8, the oblique spring guide rods 7, the oblique rod U-shaped connecting pieces 18 and the bracket U-shaped connecting pieces 2 is six, and the number of the sleeves 11 is two. The vertical spring 20 has a stiffness k2, and the stiffness generated by the inclined spring 8 and the stiffness of the vertical spring 20 are offset to achieve a zero dynamic stiffness, at which the loading platform 9 has a high static load-bearing capacity. The static load capacity is equal to the load mass m of the load platform 9 and the zero stiffness position, i.e. the static equilibrium position, is equal to mg/k 2. According to the determined static balance position, the loading platform 9 is matched with the static balance position by adjusting the four bracket U-shaped connecting pieces 2 or the supporting frame 1.
A debugging method of a quasi-zero rigid vibration isolation device based on high linear resonant frequency of three diagonal springs comprises the following specific steps:
s1, according to mass m of the loading platform 9 and rigidity k of the vertical spring 202Determining the static equilibrium position mg/k2；
S2, according to the static equilibrium position mg/k obtained in the step S12The position of the inclined spring 8 is adjusted by moving the position of the bracket U-shaped connecting piece (2) on the support frame 1, so that the middle pair of inclined springs are positioned in the horizontal direction of the static balance position mg/k2, and the upper pair of inclined springs and the lower pair of inclined springs are symmetrical along the horizontal direction of the static balance position mg/k 2;
s3, the negative stiffness of the three groups of oblique springs and the positive stiffness k of the vertical spring 20 are enabled to be respectively realized by the symmetrical moving bracket U-shaped connecting piece 2 at the upper side and the lower side or the transversely symmetrical moving bracket 1 at the two sides2Offsetting to reach zero dynamic rigidity, finally fixing the bracket U-shaped connecting piece 2 on the support frame 1, and synchronously fixing the support frame 1 with an external device to keep carrying objectsThe platform 9 is fixed at a static balance point.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.

Claims (9)

1. A quasi-zero stiffness vibration isolation device based on high linear resonant frequency of three pairs of inclined springs is characterized by comprising an inclined spring assembly, a vertical spring assembly, a carrying platform assembly and a supporting structure; the carrying platform assembly is hinged with the inclined spring assembly, the carrying platform assembly is in contact connection with the vertical spring, and the inclined spring assembly and the vertical spring assembly are both connected with the supporting structure; under the initial state, the cross points of the three pairs of inclined spring assemblies are positioned between the vertical distance between the fixed points of the pair of inclined spring assemblies on the upper side and the static balance position, namely the middle point of the two fixed points of the middle inclined spring assembly, and the rigidity corresponding to the vibration isolation device is realized under the configuration
Figure FDA00026009887300000124
The calculation formula of (2) is as follows:
Figure FDA0002600988730000011
wherein,
Figure FDA0002600988730000012
the stiffness ratio of the upper side or lower side inclined spring to the vertical spring is shown, the stiffness and length of the upper side and lower side inclined springs are the same, k1Represents a linear stiffness coefficient, k, of the upper pair of oblique springs or the lower pair of oblique springs2The linear stiffness coefficient of the vertical spring is shown,
Figure FDA0002600988730000013
represents the stiffness ratio, k, of a central pair of canted springs to a perpendicular spring3Indicating the linear stiffness coefficient of a central pair of canted springs, middle oneThe length of the diagonal spring is the same as that of the upper pair or the lower pair of diagonal springs,
Figure FDA00026009887300000125
the intermediate variable is represented by a number of variables,
Figure FDA0002600988730000014
the intermediate variable is represented by a number of variables,
Figure FDA0002600988730000015
the dimensionless horizontal distance of the hinge points at the two ends of the oblique spring is shown, a represents the horizontal distance between the hinge points at the two ends of the oblique spring, and h1Indicating the vertical distance from the initial position to a pair of oblique spring fixation points on the upper side,
Figure FDA0002600988730000016
representing a dimensionless displacement, x representing the displacement from the intersection of the three diagonal springs in the initial state,
Figure FDA0002600988730000017
the intermediate variable is represented by a number of variables,
Figure FDA0002600988730000018
the intermediate variable is represented by a number of variables,
Figure FDA0002600988730000019
a dimensionless amount of compression of the upper pair of canted springs in the initial state, an amount of compression of the upper pair of canted springs in the initial state,
Figure FDA00026009887300000110
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000111
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000112
represents an intermediate parameter, h represents a vertical distance between the initial position and the static equilibrium position, d represents a half of a vertical distance between the fixing points of the upper pair of oblique springs and the fixing points of the lower pair of oblique springs,
Figure FDA00026009887300000113
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000114
Figure FDA00026009887300000115
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000116
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000117
representing the dimensionless amount of compression of the middle pair of canted springs in the initial state,1indicating the amount of compression of the center pair of canted springs in the initial state,
Figure FDA00026009887300000118
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000119
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000120
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000121
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000122
the intermediate variable is represented by a number of variables,
Figure FDA00026009887300000123
showing the dimensionless amount of compression of the lower pair of canted springs in the initial state,2represents the compression amount dp of the lower oblique spring pair in the initial state5Representing an intermediate variable p5For dimensionless displacement
Figure FDA0002600988730000021
D is a differential of8Representing an intermediate variable p8For dimensionless displacement
Figure FDA0002600988730000022
Differentiation of (2).
2. The quasi-zero steel vibration isolation device with high linear resonance frequency based on three pairs of canted springs according to claim 1, wherein the intermediate variable p is5For dimensionless displacement
Figure FDA0002600988730000023
Differential dp of5The expression of (a) is:
Figure FDA0002600988730000024
the intermediate variable p8For dimensionless displacement
Figure FDA0002600988730000025
Differential dp of8The expression of (a) is:
Figure FDA0002600988730000026
3. the quasi-zero steel vibration isolator based on high linear resonant frequency of three diagonal springs according to claim 1, wherein the calculation formula of the corresponding force of the vibration isolator is as follows:
Figure FDA0002600988730000027
wherein,
Figure FDA0002600988730000028
representing dimensionless force and f representing dimensionless force.
4. The quasi-zero stiffness vibration isolation device based on high linear resonance frequency of three pairs of oblique springs according to claim 1, wherein the oblique spring assemblies are provided in three pairs, each of the three pairs of oblique spring assemblies comprises an upper pair of oblique spring assemblies, a middle pair of oblique spring assemblies and a lower pair of oblique spring assemblies, the upper pair of oblique springs and the lower pair of oblique springs are vertically and symmetrically arranged by taking the middle pair of oblique springs as a center, the upper pair of oblique spring assemblies, the middle pair of oblique spring assemblies and the lower pair of oblique spring assemblies are symmetrically arranged on two sides of the loading platform assembly, the upper pair of oblique springs and the lower pair of oblique springs have the same stiffness and length, and the upper pair of oblique springs, the lower pair of oblique springs and the middle pair of oblique springs have the same length; the upper oblique spring assemblies, the middle oblique spring assemblies and the lower oblique spring assemblies respectively comprise an oblique spring (8), a bearing seat (3), a linear bearing fixing plate (5), a second linear bearing (6), an oblique spring guide rod (7) and an oblique rod U-shaped connecting piece (18); the bearing seat (3) is movably connected with the supporting structure through a first radial bearing (4), and the bearing seat (3), the linear bearing fixing plate (5) and the second linear bearing (6) are fixedly connected through bolts and nuts in sequence; an inner hole of the second linear bearing (6) is inserted into one end of the inclined spring guide rod (7), the other end of the inclined spring guide rod (7) is fixedly connected with an inclined rod U-shaped connecting piece (18) through a bolt, and the inclined rod U-shaped connecting piece (18) is movably connected with the loading platform assembly; the inclined spring guide rod (7) is arranged inside the inclined spring (8), one end of the inclined spring (8) is in end face contact with the inclined rod U-shaped connecting piece (18), the other end of the inclined spring (8) is in end face contact with the second linear bearing (6), and the inclined spring (8) is in a compressed state.
5. The quasi-zero stiffness vibration isolation device based on high linear resonance frequency of three pairs of canted springs according to claim 5, wherein the stage assembly comprises a stage (9), a sleeve (11), a first linear bearing (12), a canted spring coupling plate (13), a linear bearing fixing plate (15), and a bearing support base (16); the lower part of the object carrying platform (9) is fixedly connected with a sleeve (11), the lower part of the sleeve (11) is fixedly connected with a first linear bearing (12), and a vertical spring assembly is movably arranged in the first linear bearing (12); the object carrying platform (9), the sleeve (11), the first linear bearing (12) and the inclined spring connecting plate (13) are connected with each other through a bolt (10) and a nut (14) in sequence; the inclined spring connecting plate (13) is fixedly connected with the bearing support fixing piece (15) through a bolt, the bearing support fixing piece (15) is fixedly connected with the bearing support seat (16) through a bolt, and the bearing support seat (16) is movably connected with the inclined rod U-shaped connecting piece (18) through a second radial bearing (17).
6. The quasi-zero stiffness vibration isolation device based on high linear resonance frequency of three pairs of canted springs according to claim 5, wherein the vertical spring assembly comprises a vertical guide rod (19) and a vertical spring (20), the vertical guide rod (19) is disposed in the vertical spring (20), the top end of the vertical guide rod (19) is disposed in the first linear bearing (12), the top end of the vertical spring (20) is in contact connection with the bottom end of the first linear bearing (12), the bottom end of the vertical guide rod (19) is fixed in the hole of the guide rod fixing seat (21), the bottom end of the vertical spring (20) is in contact connection with the top end of the guide rod fixing seat (21), and the vertical spring (20) is in a compressed state.
7. The quasi-zero stiffness vibration isolation device based on high linear resonance frequency of three diagonal springs according to claim 6, wherein a circular hole is formed in the middle of the guide rod fixing seat (21), a vertical guide rod (19) is fixedly arranged in the circular hole, and a vertical spring (20) is arranged on the upper portion of the circular hole.
8. The quasi-zero steel vibration isolation device based on high linear resonance frequency of three pairs of canted springs according to claim 6, wherein the support structure comprises a support bracket (1) and a bracket U-shaped connector (2); the support frame (1) is provided with a notch (1-1), the notch (1-1) is connected with a support U-shaped connecting piece (2) through a bolt, and the support U-shaped connecting piece (2) is movably connected with a bearing seat (3) through a first radial bearing (4).
9. The tuning method of the quasi-zero steel vibration-isolating device based on the high linear resonant frequency of the three diagonal springs according to any one of claims 1 to 8, characterized by comprising the following steps:
s1, according to the mass m of the loading platform (9) and the rigidity k of the vertical spring (20)2Determining the static equilibrium position mg/k2；
S2, according to the static equilibrium position mg/k obtained in the step S12The position of the inclined springs (8) is further adjusted by moving the position of the bracket U-shaped connecting piece (2) on the support frame (1), so that the middle pair of inclined springs are positioned in the horizontal direction of the static balance position mg/k2, and the upper pair of inclined springs and the lower pair of inclined springs are symmetrical along the horizontal direction of the static balance position mg/k 2;
s3, the support frames (1) on two sides are transversely and symmetrically moved through a symmetrical moving support frame U-shaped connecting piece (2) on the upper side and the lower side, so that the negative stiffness of the three groups of inclined springs and the positive stiffness k2 of the vertical spring (11) are offset to reach zero dynamic stiffness, and finally the support frame U-shaped connecting piece (2) is fixed on the support frame (1), and the support frame (1) is synchronously fixed with an external device.
CN202010723892.3A 2020-07-24 2020-07-24 Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency Active CN111853126B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010723892.3A CN111853126B (en) 2020-07-24 2020-07-24 Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010723892.3A CN111853126B (en) 2020-07-24 2020-07-24 Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency

Publications (2)

Publication Number Publication Date
CN111853126A true CN111853126A (en) 2020-10-30
CN111853126B CN111853126B (en) 2021-08-27

Family

ID=72950974

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202010723892.3A Active CN111853126B (en) 2020-07-24 2020-07-24 Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency

Country Status (1)

Country Link
CN (1) CN111853126B (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104154170A (en) * 2014-08-01 2014-11-19 安徽工程大学 Parallel mechanism based multidimensional vibration platform
US20150369331A1 (en) * 2012-12-12 2015-12-24 Shanghai Micro Electronics Equipment Co., Ltd. Negative stiffness system for gravity compensation of micropositioner
CN107351860A (en) * 2017-08-11 2017-11-17 江苏瑞铁轨道装备股份有限公司 A kind of quasi- zero stiffness central mounting device of stepless changing
CN109505918A (en) * 2018-12-27 2019-03-22 哈尔滨工业大学 A kind of quasi-zero stiffness vibration isolators based on translot spring
CN110529554A (en) * 2019-09-12 2019-12-03 郑州轻工业学院 A kind of vibration-isolating platform being made of double groups of oblique springs
CN110541905A (en) * 2019-09-12 2019-12-06 郑州轻工业学院 Vibration isolation platform formed by three groups of inclined springs

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150369331A1 (en) * 2012-12-12 2015-12-24 Shanghai Micro Electronics Equipment Co., Ltd. Negative stiffness system for gravity compensation of micropositioner
CN104154170A (en) * 2014-08-01 2014-11-19 安徽工程大学 Parallel mechanism based multidimensional vibration platform
CN107351860A (en) * 2017-08-11 2017-11-17 江苏瑞铁轨道装备股份有限公司 A kind of quasi- zero stiffness central mounting device of stepless changing
CN109505918A (en) * 2018-12-27 2019-03-22 哈尔滨工业大学 A kind of quasi-zero stiffness vibration isolators based on translot spring
CN110529554A (en) * 2019-09-12 2019-12-03 郑州轻工业学院 A kind of vibration-isolating platform being made of double groups of oblique springs
CN110541905A (en) * 2019-09-12 2019-12-06 郑州轻工业学院 Vibration isolation platform formed by three groups of inclined springs

Also Published As

Publication number Publication date
CN111853126B (en) 2021-08-27

Similar Documents

Publication Publication Date Title
CN205780563U (en) Drawing quasi-zero stiffness vibration isolators
CN108167363B (en) Two-degree-of-freedom positive and negative stiffness parallel low-frequency vibration isolation device
CN101225865B (en) Single-degree-of-freedom ultralow frequency vertical vibration isolation system
CN106090115B (en) High linearity quasi-zero stiffness vibration isolators
CN109737168B (en) Quasi-zero stiffness vibration isolator
CN113503335B (en) Packaged constant-precision zero-stiffness vibration isolator
US5549270A (en) Vibration isolation system
CN111853126B (en) Quasi-zero-stiffness vibration isolation device based on three pairs of inclined springs and high linear resonant frequency
CN111853127B (en) Quasi-zero-stiffness vibration isolation device based on high linear resonant frequency of two diagonal springs
CN113503336B (en) Constant-accurate zero-rigidity vibration isolator
WO1997011288A1 (en) Vibration isolation device with a dynamic damper
EP0274802B1 (en) Vibration or shock isolator
CN116538233A (en) Horizontal multistage rigidity vibration isolation device with damping
CN110953279A (en) Multistage vibration isolation platform based on cam-roller mechanical principle
CN114110066B (en) Zero-rigidity vibration isolation structure and method formed by single pair of diagonal rods through negative rigidity mechanism
CN211550398U (en) Quasi-zero stiffness vibration isolator
CN112377563B (en) Vibration isolation device with high attitude precision
CN212561137U (en) Road and bridge damping support
CN115325096A (en) Constant value quasi-zero stiffness vibration isolation structure based on horizontal tension spring and debugging method
CN115289178A (en) Debugging method of constant-value quasi-zero-stiffness vibration isolation structure for negative stiffness of double diagonal rods
CN115263985A (en) Constant-value quasi-zero stiffness vibration isolation structure and method based on three pairs of inclined rod negative stiffness mechanisms
CN115263986A (en) Constant-value quasi-zero stiffness vibration isolation structure and method based on negative stiffness mechanism of two pairs of inclined rods
CN217896834U (en) Spring-track vertical rigidity-variable shock insulation support
CA2150955C (en) Vibration isolation system
CN113323979A (en) Quasi-zero stiffness vibration isolator with unstability simply supported beam as positive stiffness bearing element

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant