CN113638515A - Variable-rigidity variable-mass variable-damping tuned mass damper and design method thereof - Google Patents
Variable-rigidity variable-mass variable-damping tuned mass damper and design method thereof Download PDFInfo
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- CN113638515A CN113638515A CN202110983156.6A CN202110983156A CN113638515A CN 113638515 A CN113638515 A CN 113638515A CN 202110983156 A CN202110983156 A CN 202110983156A CN 113638515 A CN113638515 A CN 113638515A
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
- E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
- E04B1/62—Insulation or other protection; Elements or use of specified material therefor
- E04B1/92—Protection against other undesired influences or dangers
- E04B1/98—Protection against other undesired influences or dangers against vibrations or shocks; against mechanical destruction, e.g. by air-raids
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
- E04H9/0215—Bearing, supporting or connecting constructions specially adapted for such buildings involving active or passive dynamic mass damping systems
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
- E04H9/0235—Anti-seismic devices with hydraulic or pneumatic damping
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Abstract
The invention discloses a variable-stiffness variable-mass variable-damping tuned mass damper and a design method thereof, wherein the damper comprises a mass system, a support and a damping system, and the mass system comprises a mass block; the support is further provided with a plurality of second springs, the second springs are connected with sliding blocks, locking structures are connected between the mass system and the sliding blocks, and the sliding blocks can be connected with or disconnected from the mass system by locking or disconnecting the locking structures. The device can control the multistage vibration of the structure, can adapt to the natural vibration frequency in a wide range, can set corresponding optimal damping according to the vibration of different states of the main structure, greatly improves the adaptability and the suppression effect, and has wide application prospect.
Description
Technical Field
The invention relates to the technical field of vibration control, in particular to a variable-stiffness variable-mass variable-damping tuned mass damper and a design method thereof.
Background
When the structure is excited by external excitation close to a certain self-oscillation frequency of the structure, a resonance phenomenon is easily caused, so that the structure is damaged. The tuned mass damper has a good suppression effect on the vibration of a controlled structure with the frequency equivalent to the natural vibration frequency of the tuned mass damper, and is widely applied to the field of engineering structure vibration control.
The existing tuned mass damper can only restrain the vibration of the order with the structure close to the natural vibration frequency of the tuned mass damper, and in the actual engineering, the multi-order vibration of the structure is often required to be controlled. If the natural vibration frequency of the tuned mass damper is adjusted, the problem can be solved only by adjusting the rigidity of a spring and the mass of a mass block; in addition, the vibration of the main structure at different stages corresponds to different optimal damping respectively; most of the traditional tuned mass dampers change the natural vibration frequency or damping thereof by replacing parts, which is often impossible to realize in practical application, especially when the structure is continuously excited in multiple stages in a certain time period. In addition, many engineering application environments are severe, and personnel are difficult to go to the site for adjustment, which also causes inconvenience.
Disclosure of Invention
The invention aims to overcome the defects that most of the existing tuned mass dampers can only inhibit vibration of a certain order, the self-vibration frequency or damping needs to be adjusted by replacing parts, the adaptability is poor, the adjustment difficulty is high and the like, and provides a tuned mass damper with variable rigidity and variable mass and variable damping and a design method thereof.
In order to achieve the purpose, the invention provides the following technical scheme:
a variable-stiffness variable-mass variable-damping tuned mass damper comprises a mass system, a support and a damping system, wherein the mass system comprises a mass block, and the variable-stiffness variable-mass variable-damping tuned mass damper is characterized in that a plurality of guide rods are arranged on the support, the mass system can slide along the guide rods, first springs are sleeved on the guide rods, one ends of the first springs are connected with the mass system, and the other ends of the first springs are connected with the support;
the damping system is positioned between the mass system and the support and comprises an adjustable axial damper;
the support is further provided with a plurality of second springs, the second springs are connected with sliding blocks, locking structures are connected between the mass system and the sliding blocks, and the sliding blocks can be connected with or disconnected from the mass system by locking or disconnecting the locking structures.
According to the rigidity of the second spring, a guiding telescopic rod can be arranged in the second spring and is used for supporting the sliding block in a matched mode and further ensuring that the second spring is stretched and deformed along the axial direction, and the consistency of the rigidity of each second spring is not limited.
By adopting the tuned mass damper with variable stiffness, variable mass and variable damping, the guide rod is matched with the first spring to support the mass system and enable the mass system to move axially along the guide rod, the first spring is used for providing basic stiffness of the structure, the damping system is used for providing damping, the number, the type and the variation range of the damping coefficient are set according to design requirements, the damping coefficient of the damping system can be adjusted, such as the existing magneto-rheological damper, the adjustable eddy current damper and the like, so that the corresponding optimal damping coefficient can be provided according to the vibration of different states of the controlled structure, and the sliding block and the mass system can be connected or disconnected by the locking structure through the plurality of second springs, namely the stiffness of the structure is changed by adjusting the second springs connected with the mass system by the device, and then adjust the natural frequency that shakes of this structure, it is convenient to adjust, and the degree of difficulty is low, can be applicable to the control multistage vibration, and extensive applicability is extensive, through part or whole the second spring add or withdraw from, can carry out the regulation on a relatively large scale to the rigidity of tuned mass damper, realize the broadband and adjust. The device can control the multistage vibration of the structure, can adapt to the natural vibration frequency in a wide range, can set corresponding optimal damping according to the vibration of different states of the main structure, greatly improves the adaptability and the suppression effect of the tuned mass damper, and has wide application prospect.
Preferably, the locking structure comprises a magnetic part and a coil structure, and the on-off state of the locking structure can be adjusted by electrifying or cutting off the coil structure and matching with the magnetic part.
Preferably, the magnetic part includes a magnetic connecting block, the locking structure further includes a mounting seat, the mounting seat is connected to the mass block, the magnetic connecting block includes a first clamping groove and a second clamping groove, the depth of the first clamping groove is greater than that of the second clamping groove, the first clamping groove is used for clamping the mounting seat, the second clamping groove is used for clamping the slider, the coil structure includes a first coil and a second coil, the first coil is located in the mounting seat, and the second coil is located in the slider;
the first coil is electrified, the second coil is electrified, the magnetic connecting block is magnetically attracted by the mounting base to disconnect the locking structure, and the first coil can be electrified after disconnection; the second coil is electrified, the first coil is powered off, the sliding block is magnetically attracted by the magnetic connecting block, the locking structure is locked, and the second coil can be powered off after locking.
Further preferably, the mass system is connected with a sleeve, and the inner wall of the sleeve is connected with at least two mounting seats which are uniformly distributed along the circumferential direction of the sleeve. A gap is formed between the sleeve and the second spring.
By adopting the arrangement mode, the second spring can be effectively added or withdrawn, and the adjustment is convenient.
Preferably, the mass system further comprises a mass adjustment mechanism.
For adjusting the mass of the mass system.
Further preferably, the mass adjusting mechanism comprises an upper box body and a lower box body, the upper box body is connected to the mass block, the lower box body is connected to the support, the upper box body and the lower box body are used for containing liquid, and the upper box body and the lower box body are communicated through a pipe body. Liquid can flow between the upper tank and the lower tank through the pipe.
The liquid can be water or organic liquid with high density, non-flammability, non-volatility and non-corrosiveness, such as perfluorosilicone oil.
Considering along with the change of the controlled structure natural vibration frequency, the mass adjustment of the tuned mass damper is large, the structure natural vibration frequency can change along with time or the self vibration frequency analysis of the structure has deviation and other problems, in order to cause the tuned mass damper to be disordered, the mass of the tuned mass damper can be adjusted in a small range by the mass adjusting mechanism in the setting mode, meanwhile, liquid is adopted for fine adjustment of the mass, the frequency is adjusted more continuously, the frequency close to the controlled structure is further guaranteed, and the suppression effect is improved.
Further preferably, the damping system further comprises an eddy current damper.
By adopting the arrangement mode, one damper can be additionally arranged for providing a basic damping coefficient, and compared with other dampers, the eddy current damper is more convenient to maintain and has longer service life.
Further preferably, the mass system further comprises an upper mounting seat, the mass block is connected with the guide rod, the first spring, the locking structure and the damping system through the upper mounting seat, the mass block is arranged on the bottom surface of the upper mounting seat, the eddy current damper comprises a permanent magnet and a conductor plate, the conductor plate is connected onto the support, and the permanent magnet is arranged on the corresponding side surface of the mass block.
The structural shape of the upper mounting seat can be set according to design and processing requirements.
Preferably, the locking device further comprises a driving system and a control system, the control system is in communication connection with the displacement sensor, the acceleration sensor and the strain sensor, the displacement sensor is used for acquiring displacement of the controlled structure moving along the axial direction of the guide rod, the acceleration sensor is used for acquiring acceleration of the controlled structure moving along the axial direction of the guide rod, the strain sensor is used for acquiring excitation characteristics of the controlled structure, and the control system can control the driving system to adjust a damping coefficient of the damping system, adjust an on-off state of the locking structure and adjust the mass of the mass system according to data of the displacement sensor, the acceleration sensor and the strain sensor.
The control system can collect and identify vibration signals of the controlled structure in real time through each sensor, calculate the optimal control frequency and damping system required by the controlled structure in different vibration states by combining the existing program, and adjust the frequency and damping coefficient of the tuned mass damper. The whole process does not need external intervention, can realize automatic adjustment, can be designed independently aiming at different controlled structures or control purposes, and has high stability and reliability, high frequency adjustment precision and more convenient adjustment.
A design method of a tuned mass damper with variable rigidity, variable mass and variable damping comprises the following steps:
a. determining an optimal value M' of a mass system comprising the mass of the mass, the mass of the upper mounting, the mass of the upper tank and the mass M of the liquid in said upper tank, according to the excitation to which the structure to be controlled is subjected, the vibration characteristics of the structure itself and the vibration control requirements1；
b. And determining the optimal control frequency ratio alpha of the front n-order vibration of the mass system and the controlled structure under the assumption that the front n-order vibration of the controlled structure in the motion direction of the mass system needs to be controlled1、α2……αn；
c. Determining the total stiffness K of all first springs1And the stiffness K of the respective second spring2、K3……KnAnd determining the damping coefficient c required by the front n-order vibration of the controlled structure1、c2……cn；
d. Determining the minimum damping coefficient c of an adjustable axial damperAxle minAnd maximum damping coefficient cAxis maxAnd the damping coefficient c of the eddy current damperBoardMinimum of said adjustable axial damperDamping coefficient cAxle minAnd damping coefficient c of eddy current damperBoardThe sum of the damping coefficients c required by the front n-order vibration of the controlled structure1、c2……cnIs determined, the maximum damping coefficient c of the adjustable axial damperAxis maxAccording to c1、c2……cnAnd the minimum damping coefficient c of the adjustable axial damperAxle minDetermining;
wherein, the mass m of the liquid in the upper box body1Minimum value of (d) and mass m of liquid in the lower tank2Is respectively based on the frequency ratio of the tuned mass damper to the front n-order vibration of the controlled structure and the optimal control frequency ratio alpha of the front n-order vibration1、α2……αnThe allowable error range of the ratio of (a) to (b).
The design method of the tuned mass damper with variable rigidity, variable mass and variable damping is adopted, and the fact that the actual value and the design value of each self-oscillation frequency of the structure possibly have deviation or each self-oscillation frequency of the structure possibly changes along with time is fully considered; but because the change range is not large, the order of the change of the natural vibration frequency to the maximum change of the mass of the tuned mass damper is selected as the selection standard of the mass of the liquid, so that the stability and controllability of the structure even if the structure is changed are ensured, the mass of the liquid can be reduced to the maximum extent, and the reduction of the mass of the liquid can avoid the difference of the motion of the liquid and the solid mass part caused by the self mobility of the liquid in the vibration process of the structure; but also can avoid the quality error caused by liquid leakage, volatilization and the like to the maximum extent.
In summary, compared with the prior art, the invention has the beneficial effects that:
1. by adopting the variable-rigidity variable-mass variable-damping tuned mass damper, the multi-stage vibration of the structure can be controlled, the device can adapt to the natural vibration frequency in a wider range, the corresponding optimal damping can be set according to the vibration of the main structure in different states, the adaptability and the suppression effect are greatly improved, and the application prospect is wide.
2. The vibration signals of the controlled structure can be collected and identified in real time, the optimal control frequency and damping system required by the controlled structure in different vibration states can be calculated by combining the existing program, and the frequency and damping coefficient of the tuned mass damper can be adjusted. The whole process does not need external intervention, can realize automatic adjustment, can be designed independently aiming at different controlled structures or control purposes, and has high stability and reliability, high frequency adjustment precision and more convenient adjustment.
3. The frequency of the spring participating in vibration in the tuned mass damper is adjusted in a large range, so that broadband coarse adjustment is realized, the frequency of the liquid participating in vibration is adjusted in a small range, continuous fine adjustment is realized, the number of devices consumed by frequency adjustment can be reduced to the maximum extent, and the adjustment precision and stability are ensured.
4. By adopting the design method of the variable-stiffness variable-mass variable-damping tuned mass damper, the deviation of the actual value and the design value of each self-vibration frequency of the structure per se is fully considered, or the self-vibration frequency of each self-vibration frequency of the structure per se can change along with the time; but because the change range is not large, the order of the change of the natural vibration frequency to the maximum change of the mass of the tuned mass damper is selected as the selection standard of the mass of the liquid, so that the stability and controllability of the structure even if the structure is changed are ensured, the mass of the liquid can be reduced to the maximum extent, and the reduction of the mass of the liquid can avoid the difference of the motion of the liquid and the solid mass part caused by the self mobility of the liquid in the vibration process of the structure; but also can avoid the quality error caused by liquid leakage, volatilization and the like to the maximum extent.
Description of the drawings:
FIG. 1 is a schematic structural diagram of a variable stiffness, variable mass, and variable damping tuned mass damper of embodiment 1;
FIG. 2 is a schematic view of a part of the structure of a tuned mass damper with variable stiffness, variable mass and variable damping of embodiment 1;
FIG. 3 is a schematic view of a second spring and its accompanying structures according to embodiment 1;
fig. 4 is a schematic view of a lock structure of embodiment 1;
FIG. 5 is a longitudinal section of FIG. 4;
FIG. 6 is a schematic structural diagram of a variable stiffness, variable mass, and variable damping tuned mass damper of embodiment 2;
FIG. 7 is a schematic view of a part of the structure of a tuned mass damper with variable stiffness, variable mass and variable damping of embodiment 2;
FIG. 8 is a front view of the structure of FIG. 7;
fig. 9 is a structural sectional view of a-a in fig. 8.
The labels in the figure are: 1-mass block, 11-permanent magnet, 21-upper box, 22-lower box, 23-tube, 24-sleeve, 3-support, 31-conductor plate, 4-first spring, 5-adjustable axial damper, 51-pin; 52-ear plate, 6-guide rod, 7-second spring, 71-sliding block, 72-magnetic connecting block, 73-mounting seat and 74-guide telescopic rod.
Detailed Description
The invention is described in further detail below with reference to the figures and the embodiments. It should be understood that the scope of the above-described subject matter is not limited to the following examples, and any techniques implemented based on the disclosure of the present invention are within the scope of the present invention.
Example 1
As shown in fig. 1-5, the variable-stiffness variable-mass variable-damping tuned mass damper of the present invention comprises a mass system, a support 3 and a damping system, wherein the mass system comprises a mass block 1, and is characterized in that a plurality of guide rods 6 are arranged on the support 3, the mass system can slide along the guide rods 6, a first spring 4 is sleeved on each guide rod 6, one end of the first spring 4 is connected to the mass system, and the other end of the first spring 4 is connected to the support 3;
the damping system is positioned between the mass system and the support 3 and comprises an adjustable axial damper 5;
the support 3 is further provided with a plurality of second springs 7, the second springs 7 are connected with sliding blocks 71, locking structures are connected between the mass system and the sliding blocks 71, and the sliding blocks 71 can be connected with or disconnected from the mass system by locking or disconnecting the locking structures.
Specifically, as shown in fig. 1-2, the mass system further includes an upper mounting base 2, in this embodiment, the upper mounting base 2 is a rectangular mounting plate, but may also be in other shapes, such as a circle, an ellipse, etc., the mass block 1 is a rectangular block, the number and positions of the guide rods 6 are set according to design requirements, the guide rods 6 are preferably uniformly distributed, which is beneficial for the smooth movement of the mass system, for example, the guide rods 6 are distributed at four corners of the rectangular mounting plate in this embodiment, the guide rods 6 extend out of the rectangular mounting plate, which is convenient for the movement of the rectangular mounting plate, the mass block 1 is located at the center below the upper mounting base 2 and is fixedly connected by welding or screwing, the mass block 1 is connected with the guide rods 6, the first spring 4, the locking structure and the damping system through the upper mounting base 2, the first spring 4 is fixed between the upper mounting base 2 and the support plate 3 through welding, the adjustable axial damper 5 is respectively connected to the upper mounting seat 2 and the support 3 through a pin shaft 51 and an ear plate 52, and if the adjustable axial damper 5 can be an existing current variable damper, the current passing through the damper is adjusted through a control circuit, so that the damping coefficient of the damper is adjusted. Preferably, the damping system further comprises an eddy current damper comprising a permanent magnet 11 and a conductor plate 31, the device is used for providing basic damping coefficient, if the requirement of minimum damping coefficient is met, the device is beneficial to energy conservation, compared with other dampers, the eddy current damper is more convenient to maintain and longer in service life, in this embodiment, the conductor plate 31 is welded to the support 3, the permanent magnet 11 is bolted to the corresponding side of the mass 1, as shown in fig. 2 (the second spring 7 and its auxiliary structure and the adjustable axial damper 5 are not shown), the number of the eddy current dampers may be set as required, for example, the eddy current dampers may be respectively disposed on two opposite sides of the mass block 1, and the adjustable axial damper 5 is disposed in a direction in which the eddy current dampers are not disposed, which is beneficial to compact arrangement.
The plurality of second springs 7 are preferably uniformly and symmetrically distributed, each group of the second springs 7 is preferably opened or withdrawn in pairs, one end of each second spring 7 is welded to the support 3, the other end of each second spring 7 is welded to the corresponding sliding block 71, and according to the rigidity of each second spring 7, a guiding telescopic rod 74 is arranged in each second spring 7, as shown in fig. 3, one end of each guiding telescopic rod 74 is welded to the corresponding support 3, and the other end of each guiding telescopic rod 74 is welded to the corresponding sliding block 71 and is used for supporting the corresponding sliding block 71 in a matched manner and further ensuring that the corresponding second spring 7 is axially stretched and deformed. A plurality of second spring 7 passes through the locking structure can make slider 71 with mass system connects or breaks off, makes the rigidity of this structure change through the second spring 7 that this device of adjustment and quality piece 1 are connected promptly, and then adjusts the natural frequency of vibration of this structure, and it is convenient to adjust, and the difficulty is low, can be applicable to the multistage vibration of control, and extensive applicability is general, through making part or whole second spring 7 adds or withdraws from mass system, can carry out the regulation on a large scale to the rigidity of tuning mass damper, realizes that the broadband is adjusted.
Specifically, if the locking structure comprises a magnetic part and a coil structure, the on-off state of the locking structure can be adjusted by electrifying or cutting off the coil structure and matching with the magnetic part. As shown in fig. 4 to 5, the magnetic member includes magnetic connection blocks 72, the locking structure further includes a mounting seat 73, a sleeve 24 is correspondingly disposed on the upper mounting seat 2, at least two mounting seats 73 uniformly distributed along the circumferential direction of the sleeve 24 are connected to the inner wall of the sleeve 24, a gap is formed between the sleeve 24 and the second spring 7, a cover plate may be disposed on the top surface of the sleeve 24 to prevent impurities from falling into the sleeve, in this embodiment, only two mounting seats 73 are disposed in an example and are oppositely disposed, and each mounting seat 73 is correspondingly connected to one magnetic connection block 72. Magnetic connecting block 72 contains first draw-in groove and second draw-in groove, the degree of depth of first draw-in groove is greater than the degree of depth of second draw-in groove, first draw-in groove is used for the joint mount pad 73, the second draw-in groove is used for the joint slider 71, the coil structure contains first coil and second coil, first coil is located in the mount pad 73, the second coil is located in the slider 71. As shown in fig. 5, when the first coil is powered on and the second coil is powered off, the mounting base 73 magnetically attracts the magnetic connecting block 72 to disconnect the locking structure, and the first coil can be powered off after disconnection; because the depth of the first clamping groove is greater than that of the second clamping groove, the second coil is electrified, the first coil is powered off, the slider 71 can be magnetically attracted to the magnetic connecting block 72, but the magnetic connecting block 72 and the mounting seat 73 are kept, so that the locking structure can be locked, the second coil can be powered off after locking, and the corresponding second spring 7 is driven to be connected with the quality system. The S and N poles shown in fig. 5 can be correspondingly interchanged.
Of course, this device joinable actuating system and control system, control system contains the singlechip, control system and displacement sensor, acceleration sensor and strain sensor communication are connected, displacement sensor is used for acquireing controlled structure and follows the displacement of 6 axial motion of guide bar, acceleration sensor is used for acquireing controlled structure follows the acceleration of 6 axial motion of guide bar, strain sensor is used for acquireing the excitation characteristic that controlled structure received, control system can be according to the data control that displacement sensor, acceleration sensor and strain sensor acquireed drive system adjusts damping coefficient, regulation of damping system the locking structure open and close state and regulation the quality of quality system.
The control system can collect and identify vibration signals of the controlled structure in real time through each sensor and calculate the optimal control frequency and damping system required by the controlled structure in different vibration states by combining with the existing program, and the second springs 7 of the corresponding group can be added or withdrawn by controlling the electrification and the outage of the coil structure, so that the rigidity of the tuned mass damper can be adjusted in a larger range, and the broadband adjustment of the tuned mass damper can be realized; the damping coefficient of the tuned mass damper is adjusted by controlling the damping coefficient of the adjustable axial damper 5. The whole process does not need external intervention, can realize automatic adjustment, can be designed independently aiming at different controlled structures or control purposes, and has high stability and reliability, high frequency adjustment precision and more convenient adjustment.
Example 2
On the basis of embodiment 1, the mass system further comprises a mass adjusting mechanism for adjusting the mass of the mass system, and the mass of the mass system can be adjusted in a small range by increasing or decreasing solids or liquids.
Specifically, if the mass of the mass system is adjusted by increasing or decreasing the liquid, the frequency can be finely adjusted, and the adjustment of the frequency can be more continuous. As shown in fig. 6, the mass adjusting mechanism includes an upper box 21 and a lower box 22, the upper box 21 is located on the top surface of the upper mounting seat 2, and may also be located inside the mass block 1, the lower box 22 is connected to the support 3, and is beneficial to lowering the height of the device, if the lower box 22 is arranged in the support 3, the upper box 21 and the lower box 22 are used for containing liquid, and the upper box 21 and the lower box 22 are communicated with each other through a pipe 23, as shown in fig. 7-9, in this embodiment, an upper water pipe and a drain pipe are provided, or only one pipe may be provided. Liquid can flow between the upper box body 21 and the lower box body 22 through the pipe body 23, the flow of the liquid between the upper box body 21 and the lower box body 22 is adjusted through the pump body, and the quality of the liquid in the upper box body 21 is further adjusted. The liquid can be water or organic liquid with high density, non-flammability, non-volatility and non-corrosiveness, such as perfluorosilicone oil.
The design method of the tuned mass damper with variable rigidity, variable mass and variable damping comprises the following steps:
a. determining an optimal value M' of the mass system comprising the mass of the mass 1, the mass of the upper mounting 2, the mass of the upper tank 21 and the mass M of the liquid inside said upper tank 21, according to the excitation to which the structure to be controlled is subjected, the vibration characteristics of the structure itself and the vibration control requirements1The mass of the tube 23 is negligible;
b. and determining the optimal control frequency ratio alpha of the front n-order vibration of the mass system and the controlled structure under the assumption that the front n-order vibration of the controlled structure in the motion direction of the mass system needs to be controlled1、α2……αn；
c. Determining the total stiffness K of all the first springs 40And the stiffness K of each second spring 71、K2……KnAnd determining the damping coefficient c required by the front n-order vibration of the controlled structure1、c2……cn；
d. Determining the minimum damping coefficient c of the adjustable axial damper 5Axle minAnd maximum damping coefficient cAxis maxAnd the damping coefficient c of the eddy current damperBoardMinimum damping coefficient c of said adjustable axial damper 5Axle minAnd damping coefficient c of eddy current damperBoardThe sum of the damping coefficients c required by the front n-order vibration of the controlled structure1、c2……cnIs determined, the maximum damping coefficient c of the adjustable axial damper 5Axis maxAccording to c1、c2……cnAnd the minimum damping coefficient c of the adjustable axial damper 5Axle minDetermining;
wherein the mass m of the liquid in the upper tank 211Minimum value of (d) and mass m of liquid in lower tank 222Is respectively based on the frequency ratio of the tuned mass damper to the front n-order vibration of the controlled structure and the optimal control frequency ratio alpha of the front n-order vibration1、α2……αnThe allowable error range of the ratio of (a) to (b).
Specifically, assuming that the first n-order vibration of the controlled structure in the motion direction of the guide rod 6 needs to be controlled, the vibration direction of the controlled structure to be controlled and the vibration parameters of corresponding different orders are determined, and the vibration parameters include the frequency (ω)1、ω2……ωn) Vibration shape participating in mass (M)1、M2……Mn) Damping, etc. And determining the installation positions of sensing devices such as a displacement sensor, an acceleration sensor, a strain sensor and the like according to the characteristics and the control requirements of the structure.
According to the characteristics and the control requirements of the structure, the mass block 1, the upper mounting seat 2 and the upper box body are determined21 and the optimal value M' of the sum of the mass of the liquid therein and the optimal control frequency ratio alpha of the first n-order vibration1、α2……αn；
According to the mass optimal value M' and the optimal control frequency ratio alpha of the previous n-order vibration1、α2……αnDetermining the total stiffness K of the fixation spring1And the stiffness K of the groups of switching springs2、K3……KnDetermining the damping coefficient c of the tuned mass damper required for each order of vibration1、c2……cn；
Determining the damping coefficient c of an eddy current damperBoardAnd the maximum value c of the damping coefficient of the adjustable axial damper 5Axis maxAnd minimum value cAxle minWherein c isBoard+cAxis max＝max{c1、c2……cn}，cBoard+cAxle min＝min{c1、c2……cn}；
Wherein the mass m of the liquid in the upper tank 21 is determined1And the mass m of the liquid in the lower tank 222According to the frequency ratio of the tuned mass damper to the first n-th order vibration of the controlled structure and the optimal control frequency ratio alpha of the first n-th order vibration1、α2……αnThe allowable error range of the ratio therebetween is determined, for example, the allowable error range is ± 5%, and can also be set to 8%, 10%, etc. as required:
suppose m10.1M 'and the mass participating in the vibration of the tuned mass damper is then M' -M1That is, the upper case 21 is empty of liquid, and the frequency ratio α 'of the front n-order vibration of the tuned mass damper and the controlled structure at that time is determined'1、α'2……α'nAnd tuning the optimal control frequency ratio alpha of the front n-order vibration of the mass damper to the controlled structure1、α2……αnThe ratio of the two is
Selecting
Order to
Back out m1Minimum value of (d);
suppose m20.1M 'and the mass of the tuned mass damper participating in the vibration at this time is M' + M2And obtaining the frequency ratio alpha' of the first n-order vibration of the tuned mass damper and the controlled structure at the moment1、α″2……α″nAnd tuning the optimal control frequency ratio alpha of the front n-order vibration of the mass damper to the controlled structure1、α2……αnThe ratio of the two is
Selecting
Order to
Back out m2Minimum value of (d);
with this method it is also possible to design a tuned mass damper as in example 1 without considering the mass of the mass adjustment mechanism.
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 and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.
Claims (10)
1. A variable-stiffness variable-mass variable-damping tuned mass damper comprises a mass system, a support (3) and a damping system, wherein the mass system comprises a mass block (1), and is characterized in that a plurality of guide rods (6) are arranged on the support (3), the mass system can slide along the guide rods (6), a first spring (4) is sleeved on each guide rod (6), one end of each first spring (4) is connected with the mass system, and the other end of each first spring is connected with the support (3);
the damping system is positioned between the mass system and the support (3), and comprises an adjustable axial damper (5);
the support (3) is further provided with a plurality of second springs (7), the second springs (7) are connected with a sliding block (71), a locking structure is connected between the mass system and the sliding block (71), and the sliding block (71) can be connected with or disconnected from the mass system by locking or disconnecting the locking structure.
2. The tuned mass damper with variable stiffness, variable mass and variable damping according to claim 1, wherein the locking structure comprises a magnetic part and a coil structure, and the on-off state of the locking structure can be adjusted by powering on or powering off the coil structure and matching with the magnetic part.
3. A tuned mass damper with variable stiffness, variable mass and variable damping according to claim 2, wherein the magnetic member comprises a magnetic connection block (72), the locking structure further comprises a mounting seat (73), the mounting seat (73) is connected to the mass block (1), the magnetic connection block (72) comprises a first clamping groove and a second clamping groove, the depth of the first clamping groove is larger than that of the second clamping groove, the first clamping groove is used for clamping the mounting seat (73), the second clamping groove is used for clamping the sliding block (71), the coil structure comprises a first coil and a second coil, the first coil is located in the mounting seat (73), and the second coil is located in the sliding block (71);
the first coil is electrified, and the second coil is electrified, so that the mounting base (73) can magnetically attract the magnetic connecting block (72) to disconnect the locking structure; the second coil is electrified, and the first coil is electrified, so that the sliding block (71) can be magnetically attracted to the magnetic connecting block (72) to lock the locking structure.
4. A tuned mass damper with variable stiffness, mass and damping according to claim 3, characterized in that the mass system is connected with a sleeve (24), and the inner wall of the sleeve (24) is connected with at least two mounting seats (73) which are evenly distributed along the circumference of the sleeve (24).
5. A tuned mass damper with variable stiffness, mass and damping according to any of claims 1 to 4, wherein the mass system further comprises a mass adjustment mechanism.
6. A tuned mass damper with variable stiffness, mass and damping according to claim 5, characterized in that the mass adjusting mechanism comprises an upper box (21) and a lower box (22), the upper box (21) is connected to the mass block (1), the lower box (22) is connected to the support (3), the upper box (21) and the lower box (22) are used for containing liquid, and the upper box (21) and the lower box (22) are communicated through a pipe body (23). Liquid can flow between the upper tank (21) and the lower tank (22) through the pipe body (23).
7. A tuned mass damper with variable stiffness, mass and damping according to claim 6, wherein the damping system further comprises an eddy current damper.
8. A tuned mass damper with variable stiffness, variable mass and variable damping according to claim 7, characterized in that the mass system further comprises an upper mounting seat (2), the mass block (1) is connected with the guide rod (6), the first spring (4), the locking structure and the damping system through the upper mounting seat (2), the mass block (1) is arranged on the bottom surface of the upper mounting seat (2), the eddy current damper comprises a permanent magnet (11) and a conductor plate (31), the conductor plate (31) is connected to the support (3), and the permanent magnet (11) is arranged on the corresponding side surface of the mass block (1).
9. A tuned mass damper of variable stiffness, variable mass and variable damping according to claim 8, it is characterized by also comprising a driving system and a control system, wherein the control system is in communication connection with the displacement sensor, the acceleration sensor and the strain sensor, the displacement sensor is used for acquiring the displacement of the controlled structure along the axial movement of the guide rod (6), the acceleration sensor is used for acquiring the acceleration of the controlled structure moving along the axial direction of the guide rod (6), the strain sensor is used for acquiring the excitation characteristics of the controlled structure, and the control system can control the driving system to adjust the damping coefficient of the damping system, adjust the on-off state of the locking structure and adjust the mass of the mass system according to the data of the displacement sensor, the acceleration sensor and the strain sensor.
10. A method of designing a tuned mass damper with variable stiffness, variable mass and variable damping according to any of claims 8 to 9, comprising the steps of:
a. determining an optimal value M' of the mass system comprising the mass of the mass (1), the mass of the upper mounting (2), the mass of the upper tank (21) and the mass M of the liquid inside said upper tank (21), according to the excitation to which the structure to be controlled is subjected, the vibration characteristics of the structure itself and the vibration control requirements1；
b. And determining the optimal control frequency ratio alpha of the front n-order vibration of the mass system and the controlled structure under the assumption that the front n-order vibration of the controlled structure in the motion direction of the mass system needs to be controlled1、α2……αn；
c. Determining the total stiffness K of all the first springs (4)1And the stiffness K of the individual second springs (7)2、K3……KnAnd determining the damping coefficient c required by the front n-order vibration of the controlled structure1、c2……cn；
d. Determining the minimum damping coefficient c of the adjustable axial damper (5)Axle minAnd maximum damping coefficient cAxis maxAnd the damping coefficient c of the eddy current damperBoardSaid canMinimum damping coefficient c of adjustable axial damper (5)Axle minAnd damping coefficient c of eddy current damperBoardThe sum of the damping coefficients c required by the front n-order vibration of the controlled structure1、c2……cnIs determined, the maximum damping coefficient c of the adjustable axial damper (5)Axis maxAccording to c1、c2……cnAnd the minimum damping coefficient c of the adjustable axial damper (5)Axle minDetermining;
wherein the mass m of the liquid in the upper box body (21)1And the mass m of the liquid in the lower tank (22)2Is respectively based on the frequency ratio of the tuned mass damper to the front n-order vibration of the controlled structure and the optimal control frequency ratio alpha of the front n-order vibration1、α2……αnThe allowable error range of the ratio of (a) to (b).
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