CN114370478B - Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity - Google Patents

Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity Download PDF

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CN114370478B
CN114370478B CN202111632050.8A CN202111632050A CN114370478B CN 114370478 B CN114370478 B CN 114370478B CN 202111632050 A CN202111632050 A CN 202111632050A CN 114370478 B CN114370478 B CN 114370478B
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vibrator
damping system
inerter
vibration damping
nonlinear
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CN114370478A (en
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蒋欢军
黄炜元
和留生
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Tongji University
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Tongji University
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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
    • F16F15/023—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 fluid means
    • F16F15/027—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 fluid means comprising control 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
    • F16F15/02—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
    • F16F15/30—Flywheels

Abstract

The invention relates to a vibration damping system, in particular to an inerter type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity, which comprises a bottom plate used for mounting the vibration damping system on a main body structure, and further comprises a vibrator, a slide rail, a gas spring, a control unit and an inerter; the sliding rail is fixedly arranged on the bottom plate, and the oscillator is arranged on the sliding rail in a sliding manner along the sliding rail; the gas springs are arranged in pairs and are symmetrically arranged on the vibrators, one end of each gas spring is fixed on the bottom plate through the supporting platform, and the other end of each gas spring is hinged with the side edge of each vibrator; the inerter is fixed on the bottom plate through a bracket and is fixedly connected with the side edge of the vibrator through a screw rod; the screw rod is arranged in parallel to the motion direction of the vibrator. Compared with the prior art, after the vibration reduction system is arranged on the main body structure, the nonlinear stiffness of the system can be adaptively regulated and controlled or regulated and controlled in real time through the control unit, so that the optimal working frequency of the system is consistent with the excitation frequency, and the vibration control effect of the system is further improved.

Description

Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity
Technical Field
The invention relates to a vibration reduction system, in particular to an inertial capacity type nonlinear energy trap vibration reduction system with adjustable nonlinear rigidity.
Background
The energy-dissipating and vibration-damping technology for the structure is to arrange energy-dissipating (damping) devices (or elements) at certain parts of the main structure (such as supports, shear walls, connecting joints or connecting component lamps). And then before the main body enters the inelastic state, the device (or element) can firstly enter the energy consumption working state, and the energy dissipation or absorption is realized by generating friction, bending (or shearing, torsion) elastoplasticity (or viscoelasticity) hysteresis deformation so as to reduce the reaction of the main body structure, thereby ensuring the safety and normal use of the main body structure.
As an emerging structural vibration control technology, the restoring force of the nonlinear energy trap is in a nonlinear relation with the system displacement, so that the nonlinear energy trap has a wider vibration reduction frequency band compared with a tuned mass damper. In addition, the nonlinear energy trap has a targeted energy transfer mechanism due to the non-constant nonlinear stiffness, so that structural vibration energy can be captured into a vibration damping system and dissipated, and the nonlinear energy trap is a vibration control technology with high robustness. However, the oscillator mass adopted by the nonlinear energy trap is usually much larger than that of the traditional passive damper, so that the practical application of the technology is limited.
Inerters typically mechanically convert linear motion applied to their ends into rotational motion of a mass or flow of liquid, thereby creating a large apparent mass. At present, the most commonly used inertial container mainly utilizes a ball screw to be matched with a rotating nut, and radial motion at two ends of the inertial container is converted into high-speed rotating motion of a mass block, so that larger apparent mass is generated.
Disclosure of Invention
The invention aims to solve at least one of the problems and provides an inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness, the control excitation frequency band of the vibration damping system is greatly widened by adjusting and controlling the nonlinear stiffness of a gas spring, meanwhile, the vibration energy of a main structure is transmitted to a damping system by the nonlinear energy trap technology, and further, the energy dissipation is realized by utilizing mechanical damping, so that the additional mass required by the vibration damping system is favorably reduced.
The purpose of the invention is realized by the following technical scheme:
an inerter type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness comprises a bottom plate used for mounting the vibration damping system on a main body structure, and the vibration damping system further comprises a vibrator, a slide rail, an air spring and an inerter;
the sliding rail is fixedly arranged on the bottom plate, and the oscillator is arranged on the sliding rail in a sliding manner along the sliding rail;
the pair of gas springs is arranged and is arranged symmetrically to the vibrator, one end of each gas spring is fixed on the bottom plate through a supporting platform, and the other end of each gas spring is hinged with the side edge of the vibrator;
the inertial container is fixed on the bottom plate through a bracket and is fixedly connected with the side edge of the vibrator through a screw rod; the screw rod is arranged in parallel to the motion direction of the vibrator;
the vibrator slides along the slide rail, and the inertia container is driven to move through the screw rod, so that a mass amplification effect is generated; meanwhile, the vibrator slides along the slide rail to drive the air spring to move, so that the internal pressure of the air spring is changed, and the nonlinearity of the system is improved.
Preferably, the vibrator comprises a mass block box body and a mass block arranged in the mass block box body, and the mass block box body are fixedly connected through bolt holes arranged at the bottom of the inner side of the mass block box body; and the bottom of the mass block box body is provided with a convex block matched with the slide rail. The mass block is fixed in the mass block box body, so that the mass block can not move when the vibrator moves, and the mass of the vibrator can be accurately controlled. Meanwhile, the bottom of the lug matched with the slide rail can effectively limit the movement of the vibrator on the slide rail, so that the vibrator stably slides on the slide rail.
Preferably, the gas spring comprises an air hole, a cylinder, a piston rod and a hinged plate; the air hole is formed in the side wall of the air spring and communicated with the air cylinder; the piston rod extends out of one end of the gas spring, and the extending end is hinged with the side edge of the vibrator through a pin shaft; the hinged plate is fixed at the other end of the gas spring and is hinged with the supporting platform. When the oscillator slides along the slide rail, the air spring can rotate by taking the supporting platform as the center, and the piston rod of the air spring is ensured to be always kept parallel to the air spring to perform radial motion.
The gas spring is a sealed container filled with gas, the nonlinear restoring force of the gas spring can be changed by changing the pressure inside the gas spring, and the nonlinear restoring force of the gas spring and the axial displacement of the gas spring are in a cubic relation, so that the stroke of the system can be effectively reduced. The internal pressure of the gas spring can be deduced through the displacement of the vibrator.
During operation, the oscillator slides back and forth along the slide rail and drives the piston rod of the air spring to move so as to change the internal pressure of the air cylinder of the air spring, thereby obtaining stronger system nonlinear characteristics, further widening the vibration control frequency band of the vibration reduction system, reducing the sensitivity to external excitation frequency and avoiding the condition that the suppression effect is obviously reduced when the excitation frequency is not close to the fixed frequency.
Preferably, the vibration damping system further comprises an air pump, and the air pump is connected with the air hole through an air passage. The internal pressure of the air spring is controlled by the gas transmission and the gas discharge of the gas pump, so that the vibration reduction system can always work in the optimal control frequency band.
Preferably, the air passage is provided with a pipeline connecting piece connected with air holes of a plurality of air springs. The arrangement of the pipeline connecting piece can realize that the internal air pressure of a plurality of air springs can be controlled through one air pump, and further the internal air pressure of the air springs connected to the air pump can be ensured to be equal, so that the air springs cannot generate additional acting force on the oscillator, and the balance of the oscillator cannot be damaged.
Preferably, the vibration damping system further comprises a control unit, and the control unit is electrically connected with the air pump through a signal output line. The control unit is used for controlling the working state of the air pump when the air pump is installed, the system works and after the system works, so that the internal pressure of the air spring can be increased, maintained or reduced according to requirements, and the nonlinear stiffness of the vibration damping system can be regulated and controlled.
Preferably, the supporting platform is fixed on the bottom plate through bolts, the front surface of the supporting platform is provided with a hinge lug plate matched with a hinge plate of the gas spring, and the back surface of the supporting platform is fixed with a stiffening rib for enhancing the lateral stiffness.
Preferably, the inertia container comprises a flywheel, the screw rod penetrates through the center of the flywheel, the inertia container further comprises a nut arranged between the flywheel and the screw rod, the vibrator slides along the slide rail, the nut is driven to rotate through the screw rod, and then the flywheel is driven to rotate, so that a mass amplification effect is generated. The mass synergy of the inerter can be obtained by calculating the acceleration of the vibrator.
Preferably, the inerter further comprises a protective shell covering the inerter. The arrangement of the protective shell can prevent dust from falling into the inertial container to influence the matching among the flywheel, the lead screw and the nut.
Preferably, the screw is a ball screw. The ball arranged between the nut and the screw rod can enable the ball screw rod to smoothly rotate with the nut, and long-term use of the inerter can be guaranteed.
The working principle of the invention is as follows:
under the excitation of earthquake and wind load, the vibration reduction system starts to work, the vibrator can slide on the slide rail in the radial direction, and the inertia container is driven to enter a working state through the screw rod, so that a mass amplification effect is generated, and the additional mass (namely the mass of the vibrator) required by overcoming the excitation of the vibration reduction system is reduced; meanwhile, the vibrator can drive a piston rod of the air spring to move on the sliding rail, so that the pressure intensity inside the air spring is changed, the nonlinear characteristic of a strong vibration damping system can be obtained, the vibration control frequency band of the vibration damping system can be widened, and the sensitivity to external excitation frequency is reduced; in addition, the control unit can regulate and control the air pressure of the air spring at any time when the vibration reduction system works, so that the optimal vibration reduction frequency is regulated and controlled when the vibration reduction system works, and the vibration control effect of the vibration reduction system under the specific excitation frequency is further improved.
Compared with the prior art, the invention has the following beneficial effects:
the invention provides an inertial capacity type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity, aiming at the problems that the nonlinear rigidity of a nonlinear energy trap is difficult to regulate and control and the additional mass is large. By properly regulating and controlling the nonlinear stiffness of the gas spring, and using the gas spring as a stiffness unit of a nonlinear energy trap, the nonlinear degree of the nonlinear energy trap can be further improved by adding the mechanical property of the gas spring, namely strong nonlinearity, so that the inertia capacity type nonlinear energy trap vibration reduction system with adjustable nonlinear stiffness provided by the invention has the beneficial effects that the system mainly comprises the following three points:
(1) Through the use of the air spring, the internal pressure of the air spring can be changed when the vibration damping system works, and then stronger nonlinear characteristics of the vibration damping system can be obtained, so that the vibration damping system has wider vibration control frequency band, and meanwhile, the sensitivity to external excitation frequency can be reduced. The vibration reduction effect generated by the radial movement of the mass block can be amplified through mass synergy by matching with the use of the inertial container, so that the additional mass required by a vibration reduction system can be greatly reduced.
(2) Cooperate the use of cylinder and control unit in the use of gas spring, can: 1) The control unit is used for controlling the air pressure of the air spring, so that the control frequency of the vibration damping system installed on site is consistent with that in design, and the influence on the vibration damping frequency band caused by the fact that the nonlinear rigidity of the nonlinear energy trap is inconsistent with the design is avoided; 2) The control unit is used for regulating and controlling the air pressure of the air spring at any time when the vibration reduction system works, so that the optimal vibration reduction frequency is regulated and controlled when the vibration reduction system works, and the vibration control effect of the vibration reduction system under the specific excitation frequency is improved.
(3) The pipeline connecting piece is arranged on the air channel between the air cylinder and the air springs, so that one air cylinder corresponds to a plurality of air springs, and further, when each air spring acts, the air pressure in the air cylinder is equal, and the phenomenon that extra pressure is applied to the vibrator by the individual air springs to damage the balance of the vibrator and further damage the operation of the vibration damping system is avoided.
(4) The vibration damping system has adjustable non-constant natural frequency, so that the vibration damping system can resonate with a series of modes of the structure, thereby greatly widening the control frequency band of the vibration damping system, simultaneously, the vibration damping system has smaller additional mass, has smaller mass compared with the traditional tuned mass damper, and makes up the defects of the traditional TMD (frequency modulation mass damper) in additional mass and space limitation.
(5) The vibration reduction system adopts the nonlinear energy trap, and has wider vibration reduction frequency band and higher robustness; meanwhile, an inertial container is combined, the radial motion of the mass block is converted into the high-speed rotation of the flywheel to generate larger apparent mass, and the defect of large vibrator mass required by the nonlinear energy trap can be effectively overcome; and the non-linear degree of the non-linear energy trap can be improved by adding the gas spring as a rigidity unit of the vibration damping system, so that the vibration damping frequency band of the vibration damping system can be further expanded, the sensitivity of the vibration damping system to external excitation frequency is reduced, and meanwhile, the working stroke can be obviously reduced. After the inertial capacity type nonlinear energy trap vibration attenuation system with the adjustable nonlinear rigidity is arranged on a main body structure, the nonlinear rigidity of the system can be adaptively regulated and controlled or regulated in real time through the control unit, so that the optimal working frequency of the system is consistent with the excitation frequency, and the vibration control effect of the system is further improved.
Drawings
FIG. 1 is a schematic structural diagram of an inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 2 is a schematic diagram of an elevational structure of a vibrator in the inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 3 is a schematic diagram of a side view structure of a vibrator in the inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 4 is a schematic top view of a vibrator in the inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 5 is a schematic top view of a sliding rail in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 6 is a schematic front view of a slide rail in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 7 is a schematic side view of a slide rail in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 8 is a schematic structural diagram of a gas spring in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 9 is a schematic diagram of a front view structure of a support platform in the inerter-type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 10 is a schematic side view of a support platform in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 11 is a schematic top view of a supporting platform in the inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 12 is a schematic structural diagram of an air pump in an inertial volume type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 13 is a schematic structural diagram of an inerter in the inerter-type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
FIG. 14 isbase:Sub>A schematic cross-sectional view ofbase:Sub>A section A-A (section A-A in FIG. 13) of an inerter in the inerter-type nonlinear energy trap damping system with adjustable nonlinear stiffness according to the present invention;
in the figure: 1-a vibrator; 101-a mass box; 102-bolt hole; 103-a mass block; 2-a slide rail; 3-a bottom plate; 4-a gas spring; 401-air holes; 402-a cylinder; 403-a piston rod; 404-hinged plate; 5-a pin shaft; 6-a support platform; 601-articulating ear plates; 602-a stiffener; 7-bolt; 8-the airway; 9-an air pump; 901-gas transmission port; 902-relief port; 10-a pipe connection; 11-a control unit; 12-a signal output line; 13-inerter; 1301-a flywheel; 1302-a lead screw; 1303-nut; 1304-a ball bearing; 1305-protective shell; 14-bracket.
Detailed Description
The invention is described in detail below with reference to the figures and the specific embodiments.
Examples
An inerter-type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness is shown in figures 1-14 and comprises a bottom plate 3 used for mounting the vibration damping system on a main body structure, a vibrator 1, a slide rail 2, a gas spring 4 and an inerter 13; the sliding rail 2 is fixedly arranged on the bottom plate 3, and the oscillator 1 is arranged on the sliding rail 2 in a sliding manner along the sliding rail 2; the gas springs 4 are provided with a pair and are arranged symmetrically to the vibrator 1, one end of each gas spring 4 is fixed on the bottom plate 3 through a supporting platform 6, and the other end of each gas spring is hinged with the side edge of the vibrator 1; the inertial container 13 is fixed on the bottom plate 3 through a protective shell 1305 and is fixedly connected with the side edge of the vibrator 1 through a screw rod 1302; the screw rod 1302 is arranged in parallel to the motion direction of the vibrator 1; the vibrator 1 slides along the slide rail 2, and the inertia container 13 is driven to move through the lead screw 1302, so that a mass amplification effect is generated; meanwhile, the vibrator 1 slides along the slide rail 2 to drive the air spring 4 to move, so that the internal pressure of the air spring 4 is changed, and the nonlinearity of the system is improved.
More specifically, in the present embodiment:
as shown in fig. 1, the vibration damping system of the present embodiment is integrally divided into three parts, in which a vibrator 1 and a slide rail 2 are provided at a central position and extend in the front-rear direction. The vibrator 1 is divided into a mass block box body 101 and a mass block 103, as shown in fig. 2, the mass block 103 is fixed in a bolt hole 102 at the bottom of the inner side of the mass block box body 101 through a bolt 7, so that the precise control of the mass of the vibrator 1 is realized; the shape of the lower part of the mass block box 101 is matched with the slide rail 2, as shown in fig. 2-7, the convex bumps are arranged in bilateral symmetry, so that the vibrator 1 can keep stable and stable when moving on the slide rail 2.
The left side and the right side of the sliding rail 2 are respectively provided with a gas spring 4, the sliding rail 2 is symmetrical, and the gas springs 4 are vertical to the sliding rail 2 in an initial state (in a non-working state). The gas spring 4 is composed of an air hole 401, an air cylinder 402, a piston rod 403 and a hinge plate 404, as shown in fig. 8, wherein the air hole 401 communicates the air cylinder 402 with the air pump 9 to adjust the internal pressure of the gas spring 4. A piston rod 403 extending from the inside of the gas spring 4, wherein the extending end (i.e. the extending end of the gas spring 4) is hinged with the left side and the right side of the vibrator 1 through a pin 5; the hinged plate 404 at the fixed end of the gas spring 4 is in hinged engagement with the hinged ear plate 601 of the support platform 6 to enable the gas spring 4 to be fixed to the base plate 3 via the support platform 6. When the vibrator 1 slides along the slide rail 2, the gas spring 4 rotates about the support platform 6. To ensure the stability of the support platform 6, the support platform 6 is fixed to the base plate 3 by bolts 7, and a stiffening rib 602 capable of enhancing the lateral stiffness of the support platform 6 is further provided on the back surface thereof, as shown in fig. 9 to 11.
The air pump 9 communicating with the air spring 4 only needs to be provided with one, as shown in fig. 12, having a gas transmission port 901 and a gas release port 902, and communicating with the air spring 4 through the gas passage 8, respectively. The air passage 8 is also provided with a pipeline connecting piece 10, so that one air pump 9 can simultaneously control the internal pressure of the pair of air springs 4, the internal pressure of the left air spring 4 and the internal pressure of the right air spring 4 are equal when the vibration damping system operates, and the oscillator 1 is prevented from losing balance due to asymmetrical pressure. The air pump 9 is also electrically connected with the control unit 11 through a signal output line 12, and is used for controlling the working state of the air pump 9 when being installed, when the system works and after the system works, so that the internal pressure of the air spring 4 can be increased, maintained or reduced according to requirements, and the nonlinear stiffness of the vibration damping system can be regulated and controlled.
At the end of the slide rail 2 is provided an inerter 13, and the inerter 13 is mounted on a bracket 14 and fixed on the bottom plate 3 through the bracket 14. The inertia container 13 is composed of a flywheel 1301, a lead screw 1302 and a nut 1303, as shown in fig. 13 and fig. 14, the lead screw 1302 passes through the center position of the flywheel 1301 and is arranged in parallel to the moving direction of the vibrator 1, and one end of the lead screw is fixed on the side edge of the vibrator 1; the nut 1303 is disposed between the lead screw 1302 and the flywheel 1301. In the embodiment, a ball screw is used, so that the arranged balls 1304 are filled between the nut 1303 and the screw 1302, so that the nut 1303 can rotate smoothly. When the device is operated, the vibrator 1 slides along the slide rail 2, and pushes and pulls the ball screw to drive the nut 1303 to rotate, so as to drive the flywheel 1301 to rotate, thereby generating a mass amplification effect. A protective shell 1305 is also arranged above the inertial container 13 and can prevent dust from falling into the inertial container 13 so as not to influence the operation.
Firstly, the slide rail 2 and the supporting platform 6 are assembled on the bottom plate 3, then the vibrator 1 is clamped into the slide rail 2 and is moved to a preset balance position of the gas spring 4, after the gas spring 4 is assembled, the control unit 11 is started to regulate and control the internal pressure of the gas spring 4, and finally the inertial container 13 is installed at a specified position, so that the installation of the vibration damping system of the embodiment is completed. After the vibration reduction system is installed, the control unit is used for regulating and controlling the internal pressure of the gas spring 4 to a preset value, and the vibration frequency band of the vibration reduction system is ensured to be consistent with a design value.
Under the excitation of earthquake and wind load, the vibration damping system starts to work, and the energy of the main body structure is captured to the damping system and dissipated in the system. The radial motion of the vibrator 1 on the slide rail 2 can drive the screw rod 1302 of the inertial container 13 to rotate, so as to drive the flywheel 1301 to rotate at a high speed, thereby generating a mass amplification effect and reducing the additional mass required by the system. Meanwhile, the vibrator 1 slides back and forth along the slide rail 2 and drives the piston rod 403 of the gas spring 4 to move, so that the internal pressure of the gas spring 4 is changed, the strong system nonlinear characteristic is obtained, the vibration control frequency band of the vibration damping system is widened, and the sensitivity to the external excitation frequency is reduced. Because the internal pressure of the gas spring 4 can be derived through the displacement of the vibrator 1, and the mass efficiency increase of the inerter 13 can be derived through the acceleration of the vibrator 1, after the nonlinear rigidity of the vibration damping system and the total mass of the system are obtained, the internal pressure of the gas spring 4 can be adaptively regulated and controlled by using the control unit, so that the external excitation frequency falls within the control frequency band range of the vibration damping system; or the internal pressure of the gas spring 4 can be regulated and controlled in real time by using the control unit, so that the vibration reduction system always works in the optimal control frequency band.
In conclusion, after the inertial capacity type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity is arranged on the main body structure, the additional mass required by the vibration damping system can be effectively reduced; the non-linearity degree and the non-constant natural frequency of the non-linear energy trap system can be further improved through the gas spring 4, so that the vibration reduction system obtains a wider vibration reduction frequency band and the working stroke of the vibrator 1 is obviously reduced; in addition, the nonlinear stiffness of the system can be adaptively regulated and controlled or regulated and controlled at any time through the control unit 11, so that the optimal working frequency of the system is consistent with the excitation frequency, and the vibration control effect of the system is further improved.
The working principle of the invention is as follows:
under the excitation of earthquake and wind load, the vibration damping system starts to work, the vibrator 1 can slide on the slide rail 2 in the radial direction, and the inertia container 13 is driven to enter a working state through the screw rod 1302, so that a mass amplification effect is generated, and the additional mass (namely the mass of the vibrator 1) required by the vibration damping system to overcome the excitation is reduced; meanwhile, the vibrator 1 can drive a piston rod 403 of the gas spring 4 to move on the slide rail 2, so that the pressure intensity inside the gas spring 4 is changed, stronger nonlinear characteristics of a vibration damping system can be obtained, the vibration control frequency band of the vibration damping system can be widened, and the sensitivity to external excitation frequency is reduced; in addition, the control unit 11 can regulate and control the air pressure of the air spring 4 at any time when the vibration damping system works, so that the optimal vibration damping frequency is regulated and controlled when the vibration damping system works, and the vibration control effect of the vibration damping system under a specific excitation frequency is further improved.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.

Claims (10)

1. An inerter type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity comprises a bottom plate (3) used for installing the vibration damping system on a main body structure, and is characterized by further comprising a vibrator (1), a slide rail (2), an air spring (4) and an inerter (13);
the sliding rail (2) is fixedly arranged on the bottom plate (3), and the vibrator (1) slides along the sliding rail (2) and is arranged on the sliding rail (2);
the pair of gas springs (4) is arranged symmetrically to the vibrator (1), one end of each gas spring (4) is fixed on the bottom plate (3) through a supporting platform (6), and the other end of each gas spring is hinged with the side edge of the vibrator (1); in the initial state, the gas spring (4) is vertical to the slide rail (2);
the inertial container (13) is fixed on the bottom plate (3) through a bracket (14) and is fixedly connected with the side edge of the vibrator (1) through a screw rod (1302); the screw rod (1302) is arranged in parallel to the motion direction of the vibrator (1);
the vibrator (1) slides along the slide rail (2), and the inertia container (13) is driven to move through the screw rod (1302), so that a mass amplification effect is generated; meanwhile, the vibrator (1) slides along the slide rail (2) to drive the gas spring (4) to rotate around the supporting platform (6), so that the internal pressure of the gas spring (4) is changed, and the nonlinearity of the system is improved.
2. The inerter-type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness as claimed in claim 1, wherein the vibrator (1) comprises a mass block box body (101) and a mass block (103) arranged inside the mass block box body (101), the mass block (103) is fixedly connected with the mass block box body (101) through a bolt hole (102) arranged at the bottom of the inner side of the mass block box body (101); the bottom of the mass block box body (101) is provided with a convex block matched with the sliding rail (2).
3. The adjustable nonlinear stiffness inerter-type nonlinear energy trap damping system according to claim 1, wherein the gas spring (4) comprises an air hole (401), a cylinder (402), a piston rod (403) and a hinged plate (404); the air hole (401) is arranged on the side wall of the air spring (4) and is communicated with the air cylinder (402); the piston rod (403) extends out of one end of the gas spring (4), and the extending end is hinged with the side edge of the vibrator (1) through a pin shaft (5); the hinged plate (404) is fixed at the other end of the gas spring (4) and is hinged with the supporting platform (6).
4. The inertial container type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness as claimed in claim 3, characterized in that the vibration damping system further comprises an air pump (9), and the air pump (9) is connected with the air hole (401) through an air passage (8).
5. The inerter-type nonlinear energy trap damping system with adjustable nonlinear stiffness according to claim 4, characterized in that the air passage (8) is provided with a pipe connection piece (10) connected with air holes (401) of a plurality of air springs (4).
6. The inerter-type nonlinear energy trap damping system with adjustable nonlinear stiffness as claimed in claim 4, wherein the damping system further comprises a control unit (11), and the control unit (11) is electrically connected with the air pump (9) through a signal output line (12).
7. The inertial container type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness is characterized in that the supporting platform (6) is fixed on the bottom plate (3) through bolts (7), the front surface of the supporting platform (6) is provided with a hinge lug plate (601) matched with a hinge plate (404) of the gas spring (4), and the back surface of the supporting platform is fixed with a stiffening rib (602) for enhancing the lateral stiffness.
8. The inerter-type nonlinear energy trap vibration damping system with the adjustable nonlinear stiffness as claimed in claim 1, wherein the inerter (13) comprises a flywheel (1301), the lead screw (1302) penetrates through the center of the flywheel (1301), the inerter (13) further comprises a nut (1303) arranged between the flywheel (1301) and the lead screw (1302), the vibrator (1) slides along the slide rail (2), the nut (1303) is driven to rotate through the lead screw (1302), and the flywheel (1301) is driven to rotate, so that a mass amplification effect is generated.
9. The inerter-based nonlinear energy trap vibration reduction system of claim 8, wherein the inerter (13) further comprises a protective shell (1305) covering the inerter (13).
10. The inertance-type nonlinear energy trap vibration damping system with adjustable nonlinear stiffness of claim 1 or 8, characterized in that the lead screw (1302) is a ball screw.
CN202111632050.8A 2021-12-29 2021-12-29 Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity Active CN114370478B (en)

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TW200918788A (en) * 2007-10-26 2009-05-01 Univ Nat Taiwan Screw-type inerter mechanism
CN109653080B (en) * 2018-12-05 2020-06-30 江苏科技大学 Liquid mass double-tuned shock absorber and assembling method thereof
CN109780130B (en) * 2019-02-28 2021-01-15 西安理工大学 Nonlinear energy trap vibration absorption device for whole-satellite vibration suppression
CN111395846A (en) * 2020-05-08 2020-07-10 东南大学 Damping-adjustable energy trap device of magnetorheological damper
CN214195050U (en) * 2020-11-12 2021-09-14 广州大学 Inertial-capacitance type asymmetric nonlinear energy trap device
CN113027970A (en) * 2021-02-26 2021-06-25 同济大学 Air spring device with adjustable damping rigidity

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