CN111139730A - Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap - Google Patents
Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap Download PDFInfo
- Publication number
- CN111139730A CN111139730A CN202010086393.8A CN202010086393A CN111139730A CN 111139730 A CN111139730 A CN 111139730A CN 202010086393 A CN202010086393 A CN 202010086393A CN 111139730 A CN111139730 A CN 111139730A
- Authority
- CN
- China
- Prior art keywords
- permanent magnet
- magnet group
- fixed
- mass block
- mass
- 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
Links
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01D—CONSTRUCTION OF BRIDGES, ELEVATED ROADWAYS OR VIADUCTS; ASSEMBLY OF BRIDGES
- E01D19/00—Structural or constructional details of bridges
Landscapes
- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a low-frequency vertical tuned mass damper with a negative-stiffness nonlinear energy trap, which belongs to the technical field of structural vibration control, and comprises a bottom plate, a thrust bearing, a spiral spring, a ball screw, a ball nut, a mass block, a moving permanent magnet group, a fixed permanent magnet group, a sliding bearing and a copper flywheel; the device has the characteristics of a negative-rigidity nonlinear energy trap by utilizing the nonlinearity of attraction between the moving permanent magnet group and the fixed permanent magnet group; the ball screw type inerter-damper mechanism is adopted to amplify the equivalent vibration mass of the tuned mass damper, so that the vibration attenuation effect of the tuned mass damper is improved, and the problem of overlarge net extension of a spring of the ultra-low frequency vertical tuned mass damper is solved; the device integrates the advantages of the nonlinear energy trap and the tuned mass damper, and widens the control frequency band of the tuned mass damper; meanwhile, the electric eddy current damping technology is adopted, so that the durability of the device is improved.
Description
Technical Field
The invention belongs to the technical field of structural vibration control, and particularly relates to a low-frequency vertical tuned mass damper with a negative-stiffness nonlinear energy trap.
Background
In recent decades, bridge construction in China has undergone crossing development, and a series of bridges crossing rivers and sea by kilometers are built. With the continuous increase of bridge span, large-span bridges are easy to vibrate greatly under the load action of strong/typhoon, earthquake, vehicles and the like. The vibration of the bridge not only causes the fatigue damage of the bridge structure and increases the maintenance cost of the bridge, but also reduces the driving safety and comfort of the bridge, and leads drivers and passengers and public media to doubtful the safety of the bridge. Therefore, the effective bridge vibration reduction technology is of great importance to the safe operation of the bridge.
Tuned Mass Dampers (TMDs), which are the most widely used passive vibration dampers, have been successfully applied to vibration damping control of large-span bridges, such as great britain bridges, tokyo bay sea bridges in japan, chongqi bridges in our country, and the like. However, in the long-term working process of the TMD, the rigidity degradation of the TMD or the bridge structure, the multi-order modal vibration control requirement of the bridge structure and the vehicle-bridge coupling effect enable the bridge frequency to have the time-varying characteristic, so that the frequency detuning problem of the TMD is easily caused; because the TMD is very sensitive to the vibration frequency of the control structure, when the vibration frequency of the TMD is detuned from the vibration frequency of the main structure, the damping effect of the TMD is obviously reduced;
in order to avoid the reduction of the damping effect of the TMD caused by the detuning of the TMD frequency, the invention provides a tuned mass damper frequency adjusting device and an implementation method thereof, and realizes the frequency adjustment of the vertical TMD based on the mass amplification effect of an inertial volume mechanism; the article "Perform of tuned mass dampers with wires" proposes to arrange a passive pendulum length adjustment mechanism to achieve frequency adjustment of a pendulum TMD; the thesis 'novel method for adjusting the frequency of the pendulum tuned mass damper' realizes the frequency adjustment of the pendulum TMD by utilizing the characteristics of like-pole repulsion and opposite-pole attraction of magnetic field acting force; the application of a tuned mass damper in the wind vibration control of the Hangzhou gulf bridge sightseeing tower realizes the frequency adjustment of TMD by adding a frequency modulation spring, but the frequency adjustment method can only realize the adjustment of the TMD to specific vibration frequency and cannot play a good damping effect on a time-varying structure caused by the coupling effect of a vehicle and a bridge; in addition, in order to ensure the damping effect of the TMD, the on-site debugging of the TMD is required to be carried out regularly.
The nonlinear energy trap (NES) is a novel vibration damping device, consists of nonlinear rigidity and damping, and can capture resonance energy in a wider frequency range and realize energy target transfer when the structure is excited externally. The patent 'a tuned mass damper damping system incorporating a nonlinear energy trap' widens the control frequency band towards the TMD, however, no report about blending a negative-stiffness nonlinear energy trap with the TMD, which has better damping performance, is found at present.
Furthermore, when the vertical TMD is used for controlling the vertical vibration of a large-span bridge, the TMD has the problem that the static elongation of the spring element is too large, and the working frequency of the TMD is 0.33Hz and the static elongation of the TMD spring element reaches 2.27m in the case of a Tokyo Bay bridge in Japan. The design and installation of the spring presents significant difficulties. In order to solve the problem, the lever mechanism formed by the main and auxiliary frame structures of the TMD bridge effectively reduces the static compression amount (only 0.45 m) of the spring, but the frame type mechanical device also causes the problems that the proportion of the TMD motion mass block to the whole mass is reduced, and the like.
Disclosure of Invention
In order to solve the problems, the invention discloses a low-frequency vertical tuned mass damper with a negative-stiffness nonlinear energy trap, which utilizes the characteristics of nonlinearity and opposite attraction of acting force between permanent magnets to ensure that the device has the characteristics of the negative-stiffness nonlinear energy trap through structural design, thereby widening the vibration frequency of TMD; the ball screw type inertial container mechanism is adopted, so that the equivalent motion quality of the TMD is improved, the physical quality of a TMD quality element is reduced, the TMD vibration reduction effect is improved, and the static elongation of a spring element of the TMD is reduced; the durability of the TMD is improved by combining the rotary eddy current damper technology.
In order to achieve the purpose, the invention adopts the following technical scheme:
a low-frequency vertical tuned mass damper with a negative-stiffness nonlinear energy trap comprises a bottom plate, a thrust bearing, a spiral spring, a ball screw, a ball nut, a mass block, a first moving permanent magnet group, a first fixed permanent magnet group, an immovable steel plate, a second fixed permanent magnet group, a second moving permanent magnet group, a mass block cover plate, a sliding bearing, a copper flywheel and a connecting key; the bottom plate is disc-shaped, the upper part of the mass block is hollow cylinder-shaped, and the thrust bearing is embedded in the center of the bottom plate; the spiral spring and the thrust bearing are coaxial, the lower end of the spiral spring is fixed with the bottom plate, and the upper end of the spiral spring is fixed with the bottom of the mass block; a through hole is formed in the center of the mass block; the ball nut is embedded at the lower part of the center hole of the mass block, the ball screw and the ball nut are sleeved together and sequentially pass through the thrust bearing, the ball nut, the center hole of the mass block, the fixed steel plate and the sliding bearing from bottom to top; the upper part of the mass block is provided with a groove, a guide shaft hole is formed in the position of the smooth guide shaft, and the first moving permanent magnet group is placed at the bottom of the groove; the smooth guide shaft penetrates through the lower end of the guide shaft hole to be fixed with the bottom plate, and the upper end of the smooth guide shaft is fixed with the fixed steel plate; the first fixed permanent magnet group and the second fixed permanent magnet group are respectively arranged on the lower side and the upper side of the fixed steel plate; the second moving permanent magnet group is arranged at the lower part of the mass block cover plate, and the mass block cover plate is fixed with the groove edge at the upper part of the mass block; the sliding bearing is embedded in the center of the mass block cover plate; the copper flywheel is installed at the top end of the ball screw through a connecting key.
Furthermore, the number of the permanent magnets of the moving permanent magnet group is the same as that of the permanent magnets of the fixed permanent magnet group, the centers of the moving permanent magnets are collinear with those of the fixed permanent magnets, the magnetic poles of the permanent magnets of the moving permanent magnet group are arranged in the same way, and the magnetic poles of the permanent magnets opposite to the first moving permanent magnet group and the first fixed permanent magnet group are arranged oppositely; the permanent magnet poles of the second moving permanent magnet group and the second fixed permanent magnet group which are opposite are also oppositely arranged.
Furthermore, the sliding bearing is sleeved outside the smooth guide shaft and is placed at the center of the guide shaft hole, and the center line of the smooth guide shaft and the center line of the through hole are coaxial.
Furthermore, the net distance between the fixed steel plate and the first moving permanent magnet group is equal to the net distance between the fixed steel plate and the second moving permanent magnet group at a balance position; the net separation of the moving permanent magnet set and the fixed permanent magnet set should be greater than the vibration amplitude of the tuned mass damper mass.
Furthermore, the damping coefficient of the device is adjusted by changing the net distance between the copper flywheel and the mass block cover plate or adjusting the number of permanent magnets in the second moving permanent magnet group; the equivalent vibrating mass can be adjusted by the diameter or thickness of the copper flywheel.
Further, the vibration frequency of the device can be adjusted by adjusting the number of permanent magnets in the moving permanent magnet group and the fixed permanent magnet group or the diameter of the copper flywheel.
The invention has the beneficial effects that:
1. the invention adopts the permanent magnet type negative stiffness nonlinear energy trap technology, obviously widens the control frequency band of TMD, improves the robustness of TMD, and has the advantage that the vibration energy absorbed by the nonlinear energy trap from the main structure is not returned to the main structure;
2. the ball screw inertial volume mechanism is adopted, so that the equivalent vibration mass of the TMD is improved, the actual physical mass of the TMD is effectively reduced, and the problem of overlarge static extension of an ultralow-frequency vertical TMD spring element is solved by combining the ball screw inertial volume mechanism with the negative stiffness of the permanent magnet;
3. by adopting the rotary eddy current damping, the eddy current damping energy consumption efficiency is remarkably improved, and the net distance between the copper plate and the permanent magnet is changed in real time, so that the eddy current damping has the nonlinear characteristic.
Drawings
FIG. 1 is a partial cross-sectional view of a low frequency vertically tuned mass damper with a negative stiffness nonlinear energy trap in accordance with the present invention;
FIG. 2 is an isometric view of a low frequency vertically tuned mass damper with a negative stiffness nonlinear energy trap in accordance with the present invention;
FIG. 3 is a front view of a low frequency vertically tuned mass damper with negative stiffness nonlinear energy trap in accordance with the present invention;
FIG. 4 is a top view of a low frequency vertically tuned mass damper with negative stiffness nonlinear energy traps in accordance with the present invention;
FIG. 5 is a cross-sectional elevation view B-B of a low frequency vertically tuned mass damper with a negative stiffness nonlinear energy trap in accordance with the present invention;
figure 6 is a force-displacement relationship curve for a low frequency vertically tuned mass damper with a negative stiffness nonlinear energy trap in accordance with the present invention.
List of reference numerals:
the device comprises a base plate 1, a thrust bearing 2, a spiral spring 3, a ball screw 4, a smooth guide shaft 5, a ball nut 6, a mass block 7, a first moving permanent magnet group 8, a first fixed permanent magnet group 9, a fixed steel plate 10, a first fixed permanent magnet 11, a second moving permanent magnet group 12, a mass block cover plate 13, a sliding bearing 14, a copper flywheel 15 and a connecting key 16.
Detailed Description
The present invention will be further illustrated with reference to the accompanying drawings and specific embodiments, which are to be understood as merely illustrative of the invention and not as limiting the scope of the invention. It should be noted that the terms "front," "back," "left," "right," "upper" and "lower" used in the following description refer to directions in the drawings, and the terms "inner" and "outer" refer to directions toward and away from, respectively, the geometric center of a particular component.
As shown in fig. 1 to 5, the adjustable low-frequency vertical eddy current tuned mass damper of the present embodiment includes a bottom plate 1, a thrust bearing 2, a helical spring 3, a ball screw 4, a smooth guide shaft 5, a ball nut 6, a mass block 7, a first moving permanent magnet group 8, a first fixed permanent magnet group 9, an immovable steel plate 10, a second fixed permanent magnet group 11, a second moving permanent magnet group 12, a mass block cover plate 13, a sliding bearing 14, a copper flywheel 15, and a connecting key 16.
The bottom plate 1 is disc-shaped, the upper part of the mass block 7 is hollow cylinder-shaped, the mass block cover plate 13 is arranged above the mass block, the thrust bearing 2 is embedded and fixed at the center of the bottom plate 1, the spiral spring 3 and the thrust bearing 2 are coaxial, the lower end of the spiral spring 3 is fixed with the bottom plate 1, and the upper end of the spiral spring is fixed with the bottom of the mass block 7; a through hole is formed in the center of the mass block 7; the ball nut 6 is embedded at the lower part of the central hole of the mass block 7, the ball screw 4 and the ball nut 6 are sleeved together and sequentially pass through the thrust bearing 2, the ball nut 6, the central hole of the mass block 7, the fixed steel plate 10 and the sliding bearing 14 from bottom to top; the upper part of the mass block 7 is grooved, a guide shaft hole is formed in the position of the smooth guide shaft 5, and the first moving permanent magnet group is placed at the bottom of the groove; the smooth guide shaft 5 passes through the lower end of the guide shaft hole and is fixed with the bottom plate 1, and the upper end of the smooth guide shaft is fixed with the fixed steel plate 10; the first fixed permanent magnet group 9 and the second fixed permanent magnet group 11 are respectively arranged on the lower side and the upper side of the fixed steel plate 10; the second moving permanent magnet group is arranged at the lower part of the mass block cover plate 13, and the mass block cover plate 13 is fixed with the groove edge at the upper part of the mass block 7; the sliding bearing 14 is embedded in the center of the mass block cover plate; the mass block 7 is arranged on the outer side of the permanent magnet group and above the spiral spring 3, and the copper flywheel 15 is installed at the top end of the ball screw through a key 16.
The number of permanent magnets contained in the moving permanent magnet groups 8 and 12 and the fixed permanent magnet groups 9 and 11 is the same, the centers of the moving permanent magnets and the centers of the fixed permanent magnets are collinear, the permanent magnet poles of the first moving permanent magnet group and the second moving permanent magnet group are arranged in the same way, the permanent magnet poles of the first moving permanent magnet group and the first fixed permanent magnet group which are opposite are arranged in an opposite way, and the permanent magnet poles of the second moving permanent magnet group and the second fixed permanent magnet group which are opposite are also arranged in an opposite way.
The net distance between the fixed steel plate 10 and the first moving permanent magnet group 8 is equal to the net distance between the fixed steel plate and the second moving permanent magnet group 12 at a balance position; the net separation of the moving permanent magnet set and the fixed permanent magnet set should be greater than the vibration amplitude of the tuned mass damper mass.
The copper flywheel 15 of the embodiment can cut the magnetic induction lines of the second moving permanent magnet group 12 to generate an eddy current damping effect while rotating at a high speed to generate an inertial mass effect, and the damping coefficient can be adjusted by changing the net distance between the copper flywheel and the mass block cover plate or adjusting the number of permanent magnets in the second moving permanent magnet group; the equivalent vibrating mass can be adjusted by the diameter or thickness of the copper flywheel.
The vibration frequency of the present embodiment can be adjusted by adjusting the number of permanent magnets in the moving permanent magnet group and the fixed permanent magnet group or the diameter of the copper flywheel 15.
Fig. 6 is a force-displacement relationship curve of the negative-stiffness nonlinear energy trap generated by the moving permanent magnet group and the fixed permanent magnet group of the device, and the nonlinear stiffness of the nonlinear energy trap can be adjusted by the net spacing between the moving permanent magnet group and the fixed permanent magnet group or the number of permanent magnets contained in the moving permanent magnet group and the fixed permanent magnet group.
The working principle of the embodiment is as follows:
when the device is arranged at a position with larger amplitude of a controlled structure through the bottom plate 1, and the main vibration frequency of the device is adjusted to be close to the vibration frequency of the controlled structure, the vibration energy of the controlled structure is transmitted to the device to cause the up-and-down vibration of the mass block 7, a ball screw transmission system consisting of a ball nut 6 embedded in the mass block and a ball screw 4 sleeved in the ball nut converts the linear motion of the mass block into the high-speed rotation motion of the copper flywheel 15, the high-speed rotation motion of the copper flywheel 15 is further amplified by the ball screw transmission system to generate an inertial mass effect far greater than the self physical mass, so that the actual physical mass of the device is reduced, the mass ratio of the device is improved, and the net elongation of a spring of the device control ultralow frequency; in addition, the high-speed rotation of the copper flywheel cuts the magnetic induction lines of the second moving permanent magnet group to form an eddy current damping effect; in another aspect; the moving permanent magnet group moves synchronously along with the mass block, the difference value of the permanent magnet attraction force between the moving permanent magnet group and the fixed permanent magnet group is always the same as the moving direction of the mass block, the nonlinearity of the attraction force enables the device to have the characteristic of a negative-stiffness nonlinear energy trap, the nonlinear stiffness of the nonlinear energy trap can be adjusted by adjusting the distance between the moving permanent magnet group and the fixed permanent magnet group or the number of the permanent magnet groups, the targeted transmission of the vibration energy of the passive structure is realized, and the control frequency band of the tuned mass damping is improved.
The following aspects need to be noted in this embodiment:
firstly, the mass of the mass block 7, the lead of the ball screw 4, the size of the copper flywheel 15 and the rigidity of the spiral spring 3 are determined according to the modal mass of the controlled structure and the controlled main frequency;
secondly, a groove matched with the permanent magnet in size is arranged at the mounting position of the permanent magnet, so that the permanent magnet is convenient to mount;
and thirdly, the static spacing between the moving permanent magnet group and the fixed permanent magnet group is larger than the vibration amplitude of the tuned mass damper mass block.
The technical means disclosed in the invention scheme are not limited to the technical means disclosed in the above embodiments, but also include the technical scheme formed by any combination of the above technical features.
Claims (5)
1. A low frequency vertical tuned mass damper with negative stiffness nonlinear mass traps, characterized by: the device comprises a bottom plate (1), a thrust bearing (2), a spiral spring (3), a ball screw (4), a smooth guide shaft (5), a ball nut (6), a mass block (7), a first moving permanent magnet group (8), a first fixed permanent magnet group (9), an immovable steel plate (10), a second fixed permanent magnet group (11), a second moving permanent magnet group (12), a mass block cover plate (13), a sliding bearing (14), a copper flywheel (15) and a connecting key (16); the bottom plate (1) is disc-shaped, the upper part of the mass block (7) is hollow and cylindrical, a mass block cover plate (13) is arranged above the mass block (7), and the thrust bearing (2) is embedded in the center of the bottom plate (1); the spiral spring (3) and the thrust bearing (2) are coaxial, the lower end of the spiral spring (3) is fixed with the bottom plate (1), and the upper end of the spiral spring is fixed with the bottom of the mass block (7); a through hole is formed in the center of the mass block (7); the ball nut (6) is embedded and fixed at the lower part of the central hole of the mass block (7), and the ball screw (4) and the ball nut (6) are sleeved together; the ball screw (4) sequentially penetrates through the thrust bearing (2), the ball nut (6), the center hole of the mass block (7), the fixed steel plate (10) and the sliding bearing (14) from bottom to top; the upper part of the mass block (7) is provided with a groove, a guide shaft hole is formed in the position of the smooth guide shaft (5), and the first moving permanent magnet group (8) is placed at the bottom of the groove; the smooth guide shaft (5) passes through the lower end of the guide shaft hole and is fixed with the bottom plate (1), and the upper end of the smooth guide shaft is fixed with the fixed steel plate (10); the first fixed permanent magnet group (9) and the second fixed permanent magnet group (11) are respectively arranged on the lower side and the upper side of the fixed steel plate (10); the second moving permanent magnet group (12) is arranged at the lower part of the mass block cover plate (13); the mass block cover plate (13) is fixed with the groove edge at the upper part of the mass block (7); the sliding bearing (14) is embedded in the center of the mass block cover plate; the mass block (7) is arranged on the outer side of the permanent magnet group and above the spiral spring (3), and the copper flywheel (15) is installed on the top end of the ball screw through a connecting key (16).
2. A low frequency vertically tuned mass damper with negative stiffness nonlinear energy trap as in claim 1 wherein: the number of permanent magnets contained in the moving permanent magnet groups (8) and (12) and the fixed permanent magnet groups (9) and (11) is the same, the centers of the moving permanent magnets and the centers of the fixed permanent magnets are collinear, the permanent magnet poles of the first moving permanent magnet group (8) and the second moving permanent magnet group (12) are arranged in the same way, the permanent magnet poles opposite to the first moving permanent magnet group (8) and the first fixed permanent magnet group (9) are arranged in an opposite way, and the permanent magnet poles opposite to the second moving permanent magnet group (12) and the second fixed permanent magnet group (11) are also arranged in an opposite way.
3. A low frequency vertically tuned mass damper with negative stiffness nonlinear energy trap as in claim 1 wherein: the net distance between the fixed steel plate (10) and the first moving permanent magnet group (8) is equal to the net distance between the fixed steel plate and the second moving permanent magnet group (12) at a balance position; the net spacing of the moving permanent magnet set and the fixed permanent magnet set is greater than the vibration amplitude of the tuned mass damper mass.
4. A low frequency vertically tuned mass damper with negative stiffness nonlinear energy trap as in claim 1 wherein: the damping coefficient of the device is adjusted by changing the net distance between the copper flywheel (16) and the mass block cover plate (13) or adjusting the number of permanent magnets in the second moving permanent magnet group (12); the equivalent oscillating mass is adjusted by the diameter or thickness of the copper flywheel (16).
5. A low frequency vertically tuned mass damper with negative stiffness nonlinear energy trap as in claim 1 wherein: the vibration frequency of the device is adjusted by adjusting the number of permanent magnets in the moving permanent magnet groups (8) and (12) and the fixed permanent magnet groups (9) and (11) or the diameter of the copper flywheel (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010086393.8A CN111139730B (en) | 2020-02-11 | 2020-02-11 | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010086393.8A CN111139730B (en) | 2020-02-11 | 2020-02-11 | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111139730A true CN111139730A (en) | 2020-05-12 |
| CN111139730B CN111139730B (en) | 2021-06-15 |
Family
ID=70527299
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010086393.8A Active CN111139730B (en) | 2020-02-11 | 2020-02-11 | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111139730B (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111809508A (en) * | 2020-07-29 | 2020-10-23 | 广州大学 | Low-frequency lever type tuned mass damper |
| CN112127496A (en) * | 2020-09-24 | 2020-12-25 | 湖南大学 | Ball screw type eddy current damper with negative-stiffness nonlinear energy trap |
| CN112128286A (en) * | 2020-09-14 | 2020-12-25 | 湖南大学 | Vertical tuned mass ball screw type inertial capacitance eddy current damper |
| CN112128285A (en) * | 2020-09-14 | 2020-12-25 | 湖南大学 | Vertical tuned mass magnetic screw type inertial capacitance eddy current damper |
| CN112160438A (en) * | 2020-09-24 | 2021-01-01 | 湖南大学 | Magnetic screw type eddy current damper with negative-stiffness nonlinear energy trap |
| CN112302196A (en) * | 2020-11-11 | 2021-02-02 | 广州大学 | Rotary eddy current tuned low-frequency mass damper |
| CN112411782A (en) * | 2020-10-21 | 2021-02-26 | 北京工业大学 | Balance weight lever type negative stiffness friction damper |
| CN112942104A (en) * | 2021-04-21 | 2021-06-11 | 华北水利水电大学 | Stay cable vibration reduction device of magneto negative stiffness damper and design method |
| CN113048191A (en) * | 2021-03-11 | 2021-06-29 | 哈尔滨工程大学 | Three-dimensional low-frequency broadband seismic metamaterial tree based on tree bionics |
| CN115637638A (en) * | 2022-10-26 | 2023-01-24 | 哈尔滨工业大学 | Variable inertial mass semi-active tuned mass damper inertial container and frequency tuning method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012184816A (en) * | 2011-03-07 | 2012-09-27 | Kozo Keikaku Engineering Inc | Damping device and vibration control device of structure |
| EP3196505A1 (en) * | 2014-09-15 | 2017-07-26 | Zhengqing Chen | Outer cup rotary axial eddy current damper |
| CN206368451U (en) * | 2016-12-30 | 2017-08-01 | 同济大学 | A kind of eddy current tuned damping unit of inertia |
| CN206368322U (en) * | 2016-12-16 | 2017-08-01 | 同济大学 | A kind of acceleration type current vortex inertia sinker |
| CN107022955A (en) * | 2017-02-27 | 2017-08-08 | 华北水利水电大学 | Apparent mass rotary electric magnetic damper vibration absorbing device for staying cables of bridge and design method |
| CN109163047A (en) * | 2018-10-25 | 2019-01-08 | 华北水利水电大学 | A kind of non-linear current vortex is used to matter damper and design method |
| CN209067730U (en) * | 2018-10-25 | 2019-07-05 | 华北水利水电大学 | The ternary vibration absorber of parallel connection damping and used matter unit |
| JP2019173933A (en) * | 2018-03-29 | 2019-10-10 | 株式会社免制震ディバイス | Mass damper |
-
2020
- 2020-02-11 CN CN202010086393.8A patent/CN111139730B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012184816A (en) * | 2011-03-07 | 2012-09-27 | Kozo Keikaku Engineering Inc | Damping device and vibration control device of structure |
| EP3196505A1 (en) * | 2014-09-15 | 2017-07-26 | Zhengqing Chen | Outer cup rotary axial eddy current damper |
| CN206368322U (en) * | 2016-12-16 | 2017-08-01 | 同济大学 | A kind of acceleration type current vortex inertia sinker |
| CN206368451U (en) * | 2016-12-30 | 2017-08-01 | 同济大学 | A kind of eddy current tuned damping unit of inertia |
| CN107022955A (en) * | 2017-02-27 | 2017-08-08 | 华北水利水电大学 | Apparent mass rotary electric magnetic damper vibration absorbing device for staying cables of bridge and design method |
| JP2019173933A (en) * | 2018-03-29 | 2019-10-10 | 株式会社免制震ディバイス | Mass damper |
| CN109163047A (en) * | 2018-10-25 | 2019-01-08 | 华北水利水电大学 | A kind of non-linear current vortex is used to matter damper and design method |
| CN209067730U (en) * | 2018-10-25 | 2019-07-05 | 华北水利水电大学 | The ternary vibration absorber of parallel connection damping and used matter unit |
Non-Patent Citations (2)
| Title |
|---|
| 汪志昊等: "基于表观质量负刚度效应的调谐质量阻尼器频率调节", 《科学技术与工程》 * |
| 汪志昊等: "非线性电涡流惯质阻尼器力学性能仿真与试验", 《哈尔滨工业大学学报》 * |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111809508A (en) * | 2020-07-29 | 2020-10-23 | 广州大学 | Low-frequency lever type tuned mass damper |
| CN112128286A (en) * | 2020-09-14 | 2020-12-25 | 湖南大学 | Vertical tuned mass ball screw type inertial capacitance eddy current damper |
| CN112128285A (en) * | 2020-09-14 | 2020-12-25 | 湖南大学 | Vertical tuned mass magnetic screw type inertial capacitance eddy current damper |
| CN112128286B (en) * | 2020-09-14 | 2021-09-24 | 湖南大学 | Vertical tuned mass ball screw type inertial capacitance eddy current damper |
| CN112127496A (en) * | 2020-09-24 | 2020-12-25 | 湖南大学 | Ball screw type eddy current damper with negative-stiffness nonlinear energy trap |
| CN112160438A (en) * | 2020-09-24 | 2021-01-01 | 湖南大学 | Magnetic screw type eddy current damper with negative-stiffness nonlinear energy trap |
| CN112127496B (en) * | 2020-09-24 | 2022-02-08 | 湖南大学 | Ball screw type eddy current damper with negative-stiffness nonlinear energy trap |
| CN112411782B (en) * | 2020-10-21 | 2021-10-26 | 北京工业大学 | Balance weight lever type negative stiffness friction damper |
| CN112411782A (en) * | 2020-10-21 | 2021-02-26 | 北京工业大学 | Balance weight lever type negative stiffness friction damper |
| CN112302196A (en) * | 2020-11-11 | 2021-02-02 | 广州大学 | Rotary eddy current tuned low-frequency mass damper |
| CN113048191A (en) * | 2021-03-11 | 2021-06-29 | 哈尔滨工程大学 | Three-dimensional low-frequency broadband seismic metamaterial tree based on tree bionics |
| CN113048191B (en) * | 2021-03-11 | 2022-07-15 | 哈尔滨工程大学 | Three-dimensional low-frequency broadband seismic metamaterial tree based on tree bionics |
| CN112942104A (en) * | 2021-04-21 | 2021-06-11 | 华北水利水电大学 | Stay cable vibration reduction device of magneto negative stiffness damper and design method |
| CN112942104B (en) * | 2021-04-21 | 2023-03-03 | 华北水利水电大学 | Stay cable vibration reduction device of magneto negative stiffness damper and design method |
| CN115637638A (en) * | 2022-10-26 | 2023-01-24 | 哈尔滨工业大学 | Variable inertial mass semi-active tuned mass damper inertial container and frequency tuning method |
| CN115637638B (en) * | 2022-10-26 | 2024-01-12 | 哈尔滨工业大学 | Inertial container of variable inertial semi-active tuning mass damper and frequency tuning method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111139730B (en) | 2021-06-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111139730B (en) | Low-frequency vertical tuned mass damper with negative-stiffness nonlinear energy trap | |
| CN110984418B (en) | Adjustable ultra-low frequency vertical eddy current tuned mass damper | |
| CN109163047B (en) | Nonlinear eddy current inerter damper and design method | |
| CN107228147B (en) | A kind of vertical tuned mass damper of magneto ultralow frequency | |
| US20070051576A1 (en) | Dynamic vibration absorber and dynamic vibration absorbing device using the same | |
| CN112128285B (en) | Vertical tuned mass magnetic screw type inertial capacitance eddy current damper | |
| CN108350969A (en) | The vibration damper of quality with rotation | |
| US11181165B2 (en) | Vibration mitigation device | |
| CN112219043A (en) | Damping gimbal suspension for pendulum absorber | |
| CN112283285B (en) | Horizontal tuning cantilever type eddy current damper | |
| KR101892874B1 (en) | seismic retrofitting structure of concrete structure | |
| CN109630601B (en) | Drum-type damping device | |
| CN113136767B (en) | Multi-frequency resonance eccentric road roller for road roller | |
| CN112127496B (en) | Ball screw type eddy current damper with negative-stiffness nonlinear energy trap | |
| CN108425986B (en) | Cylindrical eddy current damping device, damping adjustment method and bridge vibration reduction structure | |
| CN112302196A (en) | Rotary eddy current tuned low-frequency mass damper | |
| CN101067434A (en) | Magnetic vibration reducing method and vibration dampener | |
| CN109356426B (en) | Tuned mass damper | |
| CN112160438B (en) | Magnetic screw type eddy current damper with negative-stiffness nonlinear energy trap | |
| KR101672653B1 (en) | Resonance Avoidance Apparatus of Wind Turbine Tower using Magneto-Rheological fluid, and Tower using thereof | |
| CN112411785A (en) | Tunable mass-inertial mass damper capable of adjusting electromagnetic damping | |
| CN1291175C (en) | Magnetorheological fluid damp type dynamic vibration absorber and method of mounting thereof | |
| CN114135635A (en) | Electromagnetic tuning inertial volume vibration damper | |
| CN214117074U (en) | Rotary eddy current tuned mass damper | |
| CN111022544A (en) | Eddy current damping device using lever mechanism |
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 |