CN204456498U - Ultralow frequency pendulum-type tuned mass damper - Google Patents
Ultralow frequency pendulum-type tuned mass damper Download PDFInfo
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Abstract
本实用新型属于结构振动控制技术领域。一种超低频摆式调谐质量阻尼器,包括设置在结构体内的摆腔、与摆腔顶部的结构体连接的吊索、吊挂在吊索下端部的质量块、设置在质量块与结构体之间的粘滞阻尼器和负刚度调节装置,所述的粘滞阻尼器和负刚度调节装置的数量均为两个且均在质量块对应的两侧对称布置,所述的负刚度调节装置包括n块设置在质量块其中一侧面上的极性为N极/S极的永磁铁、和n块设置在该侧面对应的结构体上的极性为S极/N极的永磁铁。本实用新型通过特殊设计的负刚度调节装置能够有效减短超低频摆式TMD的摆长,减小TMD的安装空间,扩大了超低频摆式TMD的工程应用范围。
The utility model belongs to the technical field of structural vibration control. An ultra-low frequency pendulum tuned mass damper, comprising a pendulum cavity arranged in a structure, a sling connected to the structure at the top of the pendulum cavity, a mass block suspended at the lower end of the sling, a mass block and the structure body Between the viscous damper and the negative stiffness adjustment device, the number of the viscous damper and the negative stiffness adjustment device are two and are arranged symmetrically on both sides corresponding to the mass block, and the negative stiffness adjustment device It includes n pieces of permanent magnets arranged on one side of the mass block with the polarity of N pole/S pole, and n pieces of permanent magnets arranged on the corresponding structure of the side surface with the polarity of S pole/N pole. The utility model can effectively shorten the pendulum length of the ultra-low frequency pendulum TMD through the specially designed negative stiffness adjusting device, reduce the installation space of the TMD, and expand the engineering application range of the ultra-low frequency pendulum TMD.
Description
技术领域technical field
本实用新型属于结构振动控制技术领域,具体涉及一种超低频摆式调谐质量阻尼器。The utility model belongs to the technical field of structural vibration control, in particular to an ultra-low frequency pendulum type tuned mass damper.
背景技术Background technique
高耸建筑在风荷载作用下容易发生低频大幅振动,为了抑制这类结构振动,很多超高层建筑都设有巨型的摆式调谐质量阻尼器(TMD)。根据摆式TMD的频率计算公式可知,为满足超高层减振的超低频(第1阶弯曲振动频率一般在0.1~0.2Hz)减振要求,摆式TMD往往需要较大的摆长。如台湾101大厦用于风振与地震响应控制的TMD,采用8组长11.5m、直径90mm的高强度钢索悬挂重达660吨的质量块。Tall buildings are prone to low-frequency and large-scale vibrations under wind loads. In order to suppress such structural vibrations, many super high-rise buildings are equipped with giant pendulum-type tuned mass dampers (TMD). According to the frequency calculation formula of pendulum TMD It can be seen that in order to meet the ultra-low frequency (the first-order bending vibration frequency is generally 0.1-0.2 Hz) vibration reduction requirements for super high-rise vibration reduction, the pendulum TMD often needs a larger pendulum length. For example, the TMD used in the Taiwan 101 Building for wind vibration and seismic response control uses 8 sets of high-strength steel cables with a length of 11.5m and a diameter of 90mm to suspend a mass block weighing 660 tons.
公布号为CN 103132628 A的“摆式电涡流调谐质量阻尼器装置”专利公开了一种用于高耸建筑的调谐质量阻尼器,长吊索使其具有较低的自振频率,虽能达到高耸建筑的低频减振需要,但其结构较大。根据该专利设计用于上海中心风振控制的TMD的刚度元件采用12根、长25米的钢索,占用空间巨大。The publication number is CN 103132628 A "pendulum type eddy current tuned mass damper device" patent discloses a tuned mass damper for high-rise buildings, the long sling makes it have a lower natural frequency, although it can reach the The low frequency vibration damping of the building is required, but its structure is larger. According to this patent, the stiffness element of the TMD designed for the wind vibration control of Shanghai Center uses 12 steel cables with a length of 25 meters, which takes up a huge space.
公告号为CN 203499048 U的“摆式调谐质量阻尼器的频率调节装置”专利公开了一种摆式调谐质量阻尼器的频率调整装置,用于高耸建筑结构等的减振控制。采用调频弹簧,调频弹簧水平设置在摆式调谐质量阻尼器的质量块与主体结构之间,调频弹簧对称布置在质量块的两侧或者均匀分布在质量块的四周,调频弹簧一端连接质量块,另一端连接主体结构,调频弹簧处于预拉紧状态。但该专利只能实现TMD中质量块回复力的增加,即增加系统刚度,自振频率变大,无法实现摆式TMD摆长的降低。The patent "Frequency Adjustment Device for Pendulum Tuned Mass Damper" with the notification number CN 203499048 U discloses a frequency adjustment device for pendulum tuned mass damper, which is used for vibration reduction control of high-rise building structures. The frequency modulation spring is adopted, and the frequency modulation spring is horizontally arranged between the mass block and the main structure of the pendulum tuning mass damper. The frequency modulation spring is symmetrically arranged on both sides of the mass block or evenly distributed around the mass block. One end of the frequency modulation spring is connected to the mass block The other end is connected to the main structure, and the FM spring is in a pre-tensioned state. However, this patent can only increase the restoring force of the mass block in the TMD, that is, increase the stiffness of the system, increase the natural frequency, and cannot reduce the pendulum length of the pendulum TMD.
公告号为CN 203626078 U的“一种超低频调频质量阻尼器”专利公开了一种基于浮力原理的超低频竖向TMD。该专利将TMD的质量块(空心金属球)悬浮于密闭的充油容器,从而实现TMD弹簧元件净伸长的减小。但该专利只适用于竖向TMD减振装置,无法应用于抑制高耸结构水平振动的摆式TMD,且其阻尼大小的调节是通过改变球的外形来实现,难以做到定量调节。The patent "A Ultra-low Frequency FM Mass Damper" with the notification number CN 203626078 U discloses an ultra-low frequency vertical TMD based on the principle of buoyancy. This patent suspends the TMD mass (hollow metal ball) in a closed oil-filled container, thereby reducing the net elongation of the TMD spring element. However, this patent is only applicable to the vertical TMD vibration damping device, and cannot be applied to the pendulum TMD that suppresses the horizontal vibration of towering structures, and the adjustment of the damping size is realized by changing the shape of the ball, which is difficult to achieve quantitative adjustment.
综上可以看出:高耸建筑减振所需的摆式TMD,均需要较大的摆长,所需安装空间巨大。In summary, it can be seen that the pendulum TMD required for vibration reduction of tall buildings requires a relatively large pendulum length and requires a huge installation space.
实用新型内容Utility model content
本发明的目的是针对上述存在的低频摆式TMD摆长过长的问题和不足,提供一种附加安装负刚度调节装置的超低频摆式调谐质量阻尼器。The object of the present invention is to provide an ultra-low frequency pendulum tuned mass damper additionally equipped with a negative stiffness adjustment device for the above-mentioned problems and shortcomings of the low frequency pendulum TMD pendulum length being too long.
为解决上述问题和不足,所采取的技术方案是:In order to solve the above problems and deficiencies, the technical solutions adopted are:
一种超低频摆式调谐质量阻尼器,包括设置在结构体内的摆腔、与摆腔顶部的结构体连接的吊索、吊挂在吊索下端部的质量块、设置在质量块与结构体之间的粘滞阻尼器和负刚度调节装置,所述的粘滞阻尼器和负刚度调节装置的数量均为两个且均在质量块对应的两侧对称布置,所述的负刚度调节装置包括n块设置在质量块其中一侧面上的极性为N极/S极的永磁铁、和n块设置在该侧面对应的结构体上的极性为S极/N极的永磁铁。An ultra-low frequency pendulum tuned mass damper, comprising a pendulum cavity arranged in a structure, a sling connected to the structure at the top of the pendulum cavity, a mass block suspended at the lower end of the sling, a mass block and the structure body Between the viscous damper and the negative stiffness adjustment device, the number of the viscous damper and the negative stiffness adjustment device are two and are arranged symmetrically on both sides corresponding to the mass block, and the negative stiffness adjustment device It includes n pieces of permanent magnets arranged on one side of the mass block with the polarity of N pole/S pole, and n pieces of permanent magnets arranged on the corresponding structure of the side surface with the polarity of S pole/N pole.
所述的永磁铁为圆柱形永磁铁。The permanent magnet is a cylindrical permanent magnet.
采用上述技术方案,所取得的有益效果是:Adopt above-mentioned technical scheme, the beneficial effect that obtains is:
1、本发明通过特殊设计的负刚度调节装置能够有效减短超低频摆式TMD的摆长,减小TMD的安装空间,扩大了超低频摆式TMD的工程应用范围。1. The invention can effectively shorten the pendulum length of the ultra-low frequency pendulum TMD through the specially designed negative stiffness adjustment device, reduce the installation space of the TMD, and expand the engineering application scope of the ultra-low frequency pendulum TMD.
2、负刚度调节装置采用无接触的相互吸引的永磁铁组成,刚度调整简单、快捷,且具有很高的耐久性。2. The negative stiffness adjustment device is composed of non-contact permanent magnets that attract each other. The stiffness adjustment is simple, fast, and has high durability.
3、本发明的超低频摆式调谐质量阻尼器随质量块振动幅值的大小,频率呈现微小的变化,TMD既能很好的实现减振目标,还能自动实现限位,同时提升耐久性。当主结构振动较小时,由于本发明的超低频摆式调谐质量阻尼器(TMD)平衡位置处的振动频率稍大于主体结构,使得TMD几乎不动,避免了小幅长期振动带来的TMD疲劳损伤,从而提高了TMD系统的耐久性;当主结构振动较大时,本发明的TMD才会有相当的振动位移,此时由于振幅增大,负刚度调节装置提供的负刚度也越来越大,即TMD与主结构二者的频率也越来越接近,TMD开始充分发挥调谐作用,从而体现出较好的减振效果;当TMD的振幅持续增大到一定程度后,由于负刚度调节装置提供的负刚度过大,使得TMD的振动频率开始变的略小于主结构,TMD在阻尼与频率失谐的共同作用下,TMD的振幅开始减小,从而起到自动限位的作用,当减小到一定程度后,TMD又开始充分发挥新一轮的调谐作用。经过上述周期循环,主结构的振动能量逐渐被TMD吸收、耗散。3. The frequency of the ultra-low frequency pendulum tuned mass damper of the present invention varies slightly with the vibration amplitude of the mass block. The TMD can not only achieve the vibration reduction target well, but also automatically realize the limit position, and at the same time improve the durability . When the vibration of the main structure is small, since the vibration frequency at the balance position of the ultra-low frequency pendulum type tuned mass damper (TMD) of the present invention is slightly higher than that of the main structure, the TMD hardly moves, avoiding the TMD fatigue damage caused by the small long-term vibration, Thereby the durability of the TMD system is improved; when the vibration of the main structure is relatively large, the TMD of the present invention will have a considerable vibration displacement. At this time, due to the increase of the amplitude, the negative stiffness provided by the negative stiffness adjusting device is also increasing, namely The frequencies of the TMD and the main structure are getting closer and closer, and the TMD begins to play a full role in tuning, thus showing a better damping effect; when the amplitude of the TMD continues to increase to a certain extent, due to the negative stiffness adjustment device provided The negative stiffness is too large, so that the vibration frequency of TMD becomes slightly smaller than that of the main structure. Under the joint action of damping and frequency detuning of TMD, the amplitude of TMD begins to decrease, thus playing the role of automatic limit. After a certain level, TMD began to give full play to a new round of tuning. After the above cycle, the vibration energy of the main structure is gradually absorbed and dissipated by the TMD.
附图说明Description of drawings
图1为本发明超低频摆式调谐质量阻尼器的结构示意图。Fig. 1 is a schematic structural diagram of the ultra-low frequency pendulum tuned mass damper of the present invention.
图2为图1中A-A向结构示意图。Fig. 2 is a schematic diagram of the structure along the direction A-A in Fig. 1 .
图3为TMD质量块处于平衡状态时的受力简图。Figure 3 is a schematic diagram of the force of the TMD mass when it is in a balanced state.
图4为TMD质量块从平衡位置向左摆动时的受力简图。Figure 4 is a schematic diagram of the force on the TMD mass when it swings to the left from the equilibrium position.
图5为TMD质量块从平衡位置向右摆动时的受力简图。Figure 5 is a schematic diagram of the force on the TMD mass when it swings from the equilibrium position to the right.
图6为针对本发明制作的模型试验结构示意图。Fig. 6 is a schematic structural diagram of a model test made for the present invention.
图7为质量块两侧无永磁铁时的TMD质量块振动时间历程曲线。Fig. 7 is the vibration time history curve of the TMD mass block when there are no permanent magnets on both sides of the mass block.
图8为质量块两侧无永磁铁时设计最大振幅处的TMD质量块振动局部时间历程图。Fig. 8 is a local time history diagram of the vibration of the TMD mass block at the design maximum amplitude when there are no permanent magnets on both sides of the mass block.
图9为质量块两侧无永磁铁时振动幅值为设计最大振幅50%处的TMD质量块振动局部时间历程图。Fig. 9 is a local time history diagram of the vibration of the TMD mass block at the place where the vibration amplitude is 50% of the design maximum amplitude when there are no permanent magnets on both sides of the mass block.
图10为质量块两侧无永磁铁时振动幅值为设计最大振幅20%处的TMD质量块振动局部时间历程图。Fig. 10 is a local time history diagram of the vibration of the TMD mass block at the place where the vibration amplitude is 20% of the design maximum amplitude when there are no permanent magnets on both sides of the mass block.
图11为质量块两侧各放置一组永磁铁时的TMD质量块振动时间历程曲线。Fig. 11 is the vibration time history curve of the TMD mass block when a set of permanent magnets are placed on both sides of the mass block.
图12为质量块两侧各放置一组永磁铁时设计最大振幅处的TMD质量块振动局部时间历程图。Fig. 12 is a local time history diagram of the vibration of the TMD mass at the design maximum amplitude when a set of permanent magnets are placed on both sides of the mass.
图13为质量块两侧各放置一组永磁铁时振动幅值为设计最大振幅50%处的TMD质量块振动局部时间历程图。Fig. 13 is a partial time history diagram of the vibration of the TMD mass block at the place where a set of permanent magnets are placed on both sides of the mass block and the vibration amplitude is 50% of the design maximum amplitude.
图14为质量块两侧各放置一组永磁铁时振动幅值为设计最大振幅20%处的TMD质量块振动局部时间历程图。Fig. 14 is a partial time history diagram of the vibration of the TMD mass block at the place where a set of permanent magnets are placed on both sides of the mass block and the vibration amplitude is 20% of the design maximum amplitude.
图15为质量块两侧各放置两组永磁铁时的TMD质量块振动时间历程曲线。Fig. 15 is the vibration time history curve of the TMD mass block when two sets of permanent magnets are placed on both sides of the mass block.
图16为质量块两侧各放置两组永磁铁时设计最大振幅处的TMD质量块振动局部时间历程图。Fig. 16 is a local time history diagram of the vibration of the TMD mass at the design maximum amplitude when two sets of permanent magnets are placed on both sides of the mass.
图17为质量块两侧各放置两组永磁铁时振动幅值为设计最大振幅50%处的TMD质量块振动局部时间历程图。Fig. 17 is a partial time history diagram of the vibration of the TMD mass block at the point where the vibration amplitude is 50% of the design maximum amplitude when two sets of permanent magnets are placed on both sides of the mass block.
图18为质量块两侧各放置两组永磁铁时振动幅值为设计最大振幅20%处的TMD质量块振动局部时间历程图。Fig. 18 is a local time history diagram of the vibration of the TMD mass block at the position where the vibration amplitude is 20% of the design maximum amplitude when two sets of permanent magnets are placed on both sides of the mass block.
图中序号:1为吊索、2为质量块、3为永磁铁、4为粘滞阻尼器、5为支架、6为支座、7为顶板、8为底板、9为摆腔。Serial numbers in the figure: 1 is a sling, 2 is a mass block, 3 is a permanent magnet, 4 is a viscous damper, 5 is a bracket, 6 is a support, 7 is a top plate, 8 is a bottom plate, and 9 is a swing chamber.
具体实施方式Detailed ways
实施例一:参见图1,一种超低频摆式调谐质量阻尼器,包括设置在结构体内的摆腔9、与摆腔9顶部的结构体连接的吊索1、吊挂在吊索1下端部的质量块2、设置在质量块2与结构体之间的粘滞阻尼器4和负刚度调节装置,所述的粘滞阻尼器4和负刚度调节装置的数量均为两个且均在质量块2对应的两侧对称布置,所述的负刚度调节装置包括n块设置在质量块2其中一侧面上的极性为N极/S极的永磁铁3、和n块设置在该侧面对应的结构体上的极性为S极/N极的永磁铁3,所述的质量块2两侧的永磁铁3为圆柱形永磁铁。Embodiment 1: Referring to Fig. 1, an ultra-low frequency pendulum-type tuned mass damper includes a pendulum chamber 9 disposed in the structure, a sling 1 connected to the structure at the top of the pendulum chamber 9, and hung on the lower end of the sling 1 The mass block 2 of the part, the viscous damper 4 and the negative stiffness adjustment device arranged between the mass block 2 and the structure, the number of the viscous damper 4 and the negative stiffness adjustment device are two and are in The two sides corresponding to the mass block 2 are symmetrically arranged, and the negative stiffness adjustment device includes n pieces of permanent magnets 3 with N pole/S pole polarity arranged on one side of the mass block 2, and n pieces are arranged on the side surface The polarity of the corresponding structure is the permanent magnet 3 of S pole/N pole, and the permanent magnets 3 on both sides of the mass block 2 are cylindrical permanent magnets.
本实用新型的的工作原理是:The working principle of the present utility model is:
(1)由图1-图3所示,当结构体静止时,调谐质量阻尼器的质量块左右两侧的负刚度调节装置相互平衡,质量块处于平衡状态;(1) As shown in Figures 1-3, when the structure is stationary, the negative stiffness adjustment devices on the left and right sides of the mass block of the tuned mass damper balance each other, and the mass block is in a balanced state;
(2)当结构体振动时,调谐质量阻尼器的摆也随之摆动,如图4所示,当摆向左摆动角度θ(θ<5°)时,此时两侧永磁铁之间的吸引力为F1≥F2,运动微分方程mlθ″+p(θ)=0,p(θ)是依赖于摆角θ的回复力:(2) When the structure vibrates, the pendulum of the tuned mass damper also swings accordingly, as shown in Figure 4, when the pendulum swings to the left at an angle θ (θ<5°), the permanent magnets on both sides at this time The attractive force is F 1 ≥ F 2 , the motion differential equation mlθ″+p(θ)=0, p(θ) is the restoring force dependent on the swing angle θ:
p(θ)=mgsinθ-(F1cosθ-F2cosθ)p(θ)=mgsinθ-(F 1 cosθ-F 2 cosθ)
因为角度θ很小(在5度以内),近似的取sinθ≈θ、cosθ≈1,可得:Because the angle θ is very small (within 5 degrees), approximately taking sinθ≈θ and cosθ≈1, we can get:
p(θ)≈mgθ-(F1-F2) ①p(θ)≈mgθ-(F 1 -F 2 ) ①
其中in
(3)如图5所示,当右摆角度θ(在5度以内)时,回复力有:(3) As shown in Figure 5, when the right swing angle θ (within 5 degrees), the restoring force is:
p(θ)≈mgθ-(F2-F1) ②p(θ)≈mgθ-(F 2 -F 1 ) ②
其中in
综合①②式,得到回复力的统一公式:Combining formulas ① and ②, the unified formula of restoring force is obtained:
p(θ)≈mgθ-(Fn-Fp)p(θ)≈mgθ-(F n -F p )
其中in
系统有效刚度System Effective Stiffness
ke=kl-kmag ③k e =k l -k mag ③
其中
kmag=kn-kp ⑤k mag =k n -k p ⑤
显然对应TMD质量块任意位置均有kmag>0,故ke<kl,即原系统刚度降低,此时TMD自振频率下降,从而以较短的摆长实现更低的振动频率。Obviously, k mag >0 corresponds to any position of the TMD mass block, so k e <k l , that is, the stiffness of the original system decreases. At this time, the TMD natural frequency down, resulting in a lower vibration frequency with a shorter pendulum length.
实施例二:参见图6-图18,图6为制作的试验模型,其中支架5、顶板7、底板8之间形成振腔,支座6设置在质量块对应的两侧,并用于固定永磁铁。其中,摆长l=1.9m,质量块质量m=10kg,摆的设计最大摆角θmax=3°。本实验永磁铁平衡位置时的距离d0=18cm,圆形永磁铁型号N38,尺寸D150×10mm。实验结果见附表1。Embodiment two: referring to Fig. 6-Fig. 18, Fig. 6 is the test model of making, wherein forms vibration chamber between support 5, top plate 7, base plate 8, and support 6 is arranged on the both sides corresponding to mass block, and is used for fixing permanent magnet. Wherein, the length of the pendulum is l=1.9m, the mass of the mass block is m=10kg, and the design maximum swing angle of the pendulum is θ max =3°. In this experiment, the distance d 0 at the equilibrium position of the permanent magnet is 18cm, the circular permanent magnet is model N38, and the size is D150×10mm. The experimental results are shown in Table 1.
从附表1中的实验结果可以看出,采用本发明方法对降低摆式TMD的频率效果非常明显,当摆达到其设计振幅时,质量块两侧放置1组永磁铁可以使TMD频率降低5.7%,质量块两侧放置2组永磁铁可以使TMD频率降低11.9%。As can be seen from the experimental results in attached table 1, the method of the present invention has a very obvious effect on reducing the frequency of the pendulum TMD. When the pendulum reaches its design amplitude, placing a group of permanent magnets on both sides of the mass can reduce the TMD frequency by 5.7 %, placing 2 sets of permanent magnets on both sides of the mass can reduce the TMD frequency by 11.9%.
附表1:Schedule 1:
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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CN104612279A (en) * | 2015-02-05 | 2015-05-13 | 华北水利水电大学 | Ultralow frequency swinging type tuning mass damper and achieving method thereof |
CN104989005A (en) * | 2015-07-21 | 2015-10-21 | 中国建筑设计院有限公司 | Double-folded-line type TMD control system |
CN109537968A (en) * | 2018-11-07 | 2019-03-29 | 上海思纳建筑规划设计股份有限公司 | Super high-rise building limits sidesway damping unit |
CN111926681A (en) * | 2020-07-31 | 2020-11-13 | 中铁大桥局集团有限公司 | Pendulum-type tuned mass damping device and vibration damping bridge |
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2015
- 2015-02-05 CN CN201520084020.1U patent/CN204456498U/en not_active Withdrawn - After Issue
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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CN104612279A (en) * | 2015-02-05 | 2015-05-13 | 华北水利水电大学 | Ultralow frequency swinging type tuning mass damper and achieving method thereof |
CN104612279B (en) * | 2015-02-05 | 2016-02-17 | 华北水利水电大学 | Ultra-low frequency pendulum tuned mass damper and its realization method |
CN104989005A (en) * | 2015-07-21 | 2015-10-21 | 中国建筑设计院有限公司 | Double-folded-line type TMD control system |
CN109537968A (en) * | 2018-11-07 | 2019-03-29 | 上海思纳建筑规划设计股份有限公司 | Super high-rise building limits sidesway damping unit |
CN111926681A (en) * | 2020-07-31 | 2020-11-13 | 中铁大桥局集团有限公司 | Pendulum-type tuned mass damping device and vibration damping bridge |
CN111926681B (en) * | 2020-07-31 | 2022-03-18 | 中铁大桥局集团有限公司 | Pendulum-type tuned mass damping device and vibration damping bridge |
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