CN204456498U - Ultralow frequency pendulum-type tuned mass damper - Google Patents

Abstract

The utility model belongs to structural vibration control technical field.A kind of ultralow frequency pendulum-type tuned mass damper, comprise the pendulum chamber be arranged in structure, the hoist cable be connected with the structure of pendulum top of chamber, the mass of hanging in hoist cable bottom, be arranged on the viscous damper between mass and structure and negative stiffness adjusting device, the quantity of described viscous damper and negative stiffness adjusting device is two and all arranges in the bilateral symmetry that mass is corresponding, described negative stiffness adjusting device comprises n block and is arranged on the permanent magnet that the polarity of mass wherein on a side is N pole/S pole, with the permanent magnet that the n block polarity be arranged on structure corresponding to this side is S pole/N pole.The utility model effectively can shorten the pendulum length of ultralow frequency pendulum-type TMD by the negative stiffness adjusting device of particular design, reduces the installing space of TMD, expands the engineer applied scope of ultralow frequency pendulum-type TMD.

Description

Ultralow frequency pendulum-type tuned mass damper

Technical field

The utility model belongs to structural vibration control technical field, is specifically related to a kind of ultralow frequency pendulum-type tuned mass damper.

Background technology

Easily there is low frequency and significantly vibrate in high-rise buildings, in order to suppress this kind of structural vibration, a lot of super highrise building is all provided with huge pendulum-type tuned mass damper (TMD) under wind action.According to the frequency computation part formula of pendulum-type TMD known, for meeting ultralow frequency (the 1st rank beam frequency is generally at the 0.1 ~ 0.2Hz) damping requirements of Super High vibration damping, pendulum-type TMD often needs larger pendulum length.Shake and the TMD of seismic response control as mansion, Taiwan 101 is used for wind, adopt the high-strength steel cable of 8 group leader 11.5m, diameter 90mm to hang to weigh the mass of 660 tons.

Publication No. is that " the pendulum-type eddy current tuned mass damper device " of CN 103132628 A patent discloses a kind of tuned mass damper for high-rise buildings, long hoist cable makes it have lower natural frequency, though can reach the low frequency vibration damping needs of high-rise buildings, its structure is larger.The stiffness elements being used for the TMD of center, Shanghai wind dynamic control according to this Patent design adopts the cable wire of 12, long 25 meters, takes up room huge.

Notification number is the frequency adjusting device that " frequency regulation arrangement of pendulum-type tuned mass damper " of CN 203499048 U patent discloses a kind of pendulum-type tuned mass damper, and the vibration damping for high-rise buildings structure etc. controls.Adopt frequency modulation spring, between the mass that frequency modulation spring horizontal is arranged on pendulum-type tuned mass damper and agent structure, frequency modulation spring is arranged symmetrically in the both sides of mass or is evenly distributed on the surrounding of mass, frequency modulation spring one end quality of connection block, the other end connects agent structure, and frequency modulation spring is in pre-tensioned state.But this patent can only realize the increase of mass restoring force in TMD, namely increases system stiffness, natural frequency becomes large, cannot realize the reduction of pendulum-type TMD pendulum length.

Notification number is that " a kind of ultralow frequency tuned mass damper, TMD " of CN 203626078 U patent discloses the vertical TMD of a kind of ultralow frequency based on law of buoyancy.The mass (hollow metal sphere) of TMD is suspended in airtight oil-filled container by this patent, thus realizes the reduction that TMD spring element extends only.But this patent is only applicable to vertical TMD vibration absorber, the pendulum-type TMD suppressing tall and slender structure horizontal vibration cannot be applied to, and the adjustment of its damping size is realized by the profile of change ball, is difficult to accomplish quantitative adjustment.

In summary it can be seen: the pendulum-type TMD needed for high-rise buildings vibration damping, all need larger pendulum length, required installing space is huge.

Utility model content

The object of the invention is for the long problem and shortage of the low frequency pendulum-type TMD pendulum length of above-mentioned existence, a kind of ultralow frequency pendulum-type tuned mass damper of additional installation negative stiffness adjusting device is provided.

For solving the problem and deficiency, the technical scheme taked is:

A kind of ultralow frequency pendulum-type tuned mass damper, comprise the pendulum chamber be arranged in structure, the hoist cable be connected with the structure of pendulum top of chamber, the mass of hanging in hoist cable bottom, be arranged on the viscous damper between mass and structure and negative stiffness adjusting device, the quantity of described viscous damper and negative stiffness adjusting device is two and all arranges in the bilateral symmetry that mass is corresponding, described negative stiffness adjusting device comprises n block and is arranged on the permanent magnet that the polarity of mass wherein on a side is N pole/S pole, with the permanent magnet that the n block polarity be arranged on structure corresponding to this side is S pole/N pole.

Described permanent magnet is cylindrical magnet iron.

Adopt technique scheme, acquired beneficial effect is:

1, the present invention effectively can shorten the pendulum length of ultralow frequency pendulum-type TMD by the negative stiffness adjusting device of particular design, reduces the installing space of TMD, expands the engineer applied scope of ultralow frequency pendulum-type TMD.

2, negative stiffness adjusting device adopts the contactless permanent magnet composition attracted each other, and stiffness equivalent is simple, quick, and has very high durability.

3, ultralow frequency pendulum-type tuned mass damper of the present invention is with the size of mass vibration amplitude, and frequency presents small change, and TMD can well realize vibration damping target, automatically can also realize spacing, promote durability simultaneously.When main structure vibration is less, because the vibration frequency at ultralow frequency pendulum-type tuned mass damper (TMD) equilbrium position place of the present invention is a bit larger tham agent structure, make TMD almost motionless, avoid the TMD fatigue damage that small size Long-term Vibration brings, thus improve the durability of TMD system; When main structure vibration is larger, TMD of the present invention just has suitable vibration displacement, now because amplitude increases, the negative stiffness that negative stiffness adjusting device provides is also increasing, namely TMD and the frequency both main structure also more and more close, TMD starts to give full play to tunning effect, thus embodies good effectiveness in vibration suppression; When the amplitude of TMD continues to increase to a certain degree, the negative stiffness provided due to negative stiffness adjusting device is excessive, make the vibration frequency of TMD start become be slightly less than main structure, TMD is under the acting in conjunction of damping and frequency detuning, the amplitude of TMD starts to reduce, thus play the effect of automatic spacing, when being reduced to a certain degree, TMD starts again the tunning effect giving full play to a new round.Through above-mentioned loop cycle, the vibrational energy of main structure is absorbed by TMD gradually, dissipates.

Accompanying drawing explanation

Fig. 1 is the structural representation of ultralow frequency pendulum-type tuned mass damper of the present invention.

Fig. 2 be in Fig. 1 A-A to structural representation.

Fig. 3 is the stressed sketch of TMD mass when being in equilibrium state.

Fig. 4 is the stressed sketch of TMD mass when swinging left from equilbrium position.

Fig. 5 is the stressed sketch of TMD mass when swinging to the right from equilbrium position.

Fig. 6 is the model testing structural representation made for the present invention.

Fig. 7 is that mass both sides are without TMD mass time of vibration course curve during permanent magnet.

Fig. 8 is that mass both sides are without the TMD mass vibration local time course figure designing peak swing place during permanent magnet.

Fig. 9 is mass both sides is the TMD mass vibration local time course figure at design peak swing 50% place without vibration amplitude during permanent magnet.

Figure 10 is mass both sides is the TMD mass vibration local time course figure at design peak swing 20% place without vibration amplitude during permanent magnet.

Figure 11 is the TMD mass time of vibration course curves of mass both sides when respectively placing one group of permanent magnet.

Figure 12 is the TMD mass vibration local time course figure at design peak swing place when respectively placing one group of permanent magnet, mass both sides.

Figure 13 be mass both sides when respectively placing one group of permanent magnet vibration amplitude be the TMD mass vibration local time course figure at design peak swing 50% place.

Figure 14 be mass both sides when respectively placing one group of permanent magnet vibration amplitude be the TMD mass vibration local time course figure at design peak swing 20% place.

Figure 15 is the TMD mass time of vibration course curves of mass both sides when respectively placing two groups of permanent magnets.

Figure 16 is the TMD mass vibration local time course figure at design peak swing place when respectively placing two groups of permanent magnets, mass both sides.

Figure 17 be mass both sides when respectively placing two groups of permanent magnets vibration amplitude be the TMD mass vibration local time course figure at design peak swing 50% place.

Figure 18 be mass both sides when respectively placing two groups of permanent magnets vibration amplitude be the TMD mass vibration local time course figure at design peak swing 20% place.

Sequence number in figure: 1 be hoist cable, 2 for mass, 3 for permanent magnet, 4 for viscous damper, 5 for support, 6 for bearing, 7 for top board, 8 for base plate, 9 for pendulum chamber.

Detailed description of the invention

Embodiment one: see Fig. 1, a kind of ultralow frequency pendulum-type tuned mass damper, comprise the pendulum chamber 9 be arranged in structure, the hoist cable 1 be connected with the structure at pendulum top, chamber 9, the mass 2 of hanging in hoist cable 1 bottom, be arranged on the viscous damper 4 between mass 2 and structure and negative stiffness adjusting device, described viscous damper 4 and the quantity of negative stiffness adjusting device are two and all arrange in the bilateral symmetry of mass 2 correspondence, described negative stiffness adjusting device comprises n block and is arranged on the permanent magnet 3 that the polarity of mass 2 wherein on a side is N pole/S pole, with the permanent magnet 3 that the n block polarity be arranged on structure corresponding to this side is S pole/N pole, the permanent magnet 3 of described mass 2 both sides is cylindrical magnet iron.

Operating principle of the present utility model is:

(1) by shown in Fig. 1-Fig. 3, when structure is static, the negative stiffness adjusting device of the mass left and right sides of tuned mass damper balances mutually, and mass is in equilibrium state;

(2) when structure vibrates, the pendulum of tuned mass damper also swings thereupon, and as shown in Figure 4, when being flapped toward left pendulum angle θ (θ < 5 °), the attraction now between the permanent magnet of both sides is F ₁>=F ₂, differential equation of motion ml θ " and+p (θ)=0, p (θ) is the restoring force depending on pivot angle θ:

p(θ)＝mgsinθ-(F ₁cosθ-F ₂cosθ)

Because angle θ very little (within 5 degree), approximate gets sin θ ≈ θ, cos θ ≈ 1, can obtain:

p(θ)≈mgθ-(F ₁-F ₂) ①

Wherein

$F_1=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0-\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0-\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0-\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

$F_2=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0+\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0+\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0+\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

(3) as shown in Figure 5, when right swinging θ (within 5 degree), restoring force has:

p(θ)≈mgθ-(F ₂-F ₁) ②

Wherein

$F_1=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0+\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0+\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0+\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

$F_2=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0-\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0-\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0-\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

Comprehensive 1. 2. formula, obtains the Uniform Formula of restoring force:

p(θ)≈mgθ-(F _n-F _p)

Wherein

$F_n=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0-\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0-\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0-\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

$F_p=\left[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\right][\frac{1}{{(d_0+\mathrm{l\&theta;})}^2}+\frac{1}{{(d_0+\mathrm{l\&theta;}+2\mathrm{\&delta;})}^2}-\frac{2}{{(d_0+\mathrm{l\&theta;}+\mathrm{\&delta;})}^2}]$

System effective rigidity

k _e＝k _l-k _mag③

Wherein $k_l=\frac{\mathrm{mg}}{l}$ ④

k _mag＝k _n-k _p⑤

$\begin{array}{c}{k}_p=\left|\frac{{\mathrm{\&delta;F}}_p}{\mathrm{\&delta;}(d_0-\mathrm{l\&theta;})}\right|=\left|\frac{{\&PartialD;F}_p}{\&PartialD;(d_0-\mathrm{l\&theta;})}\right|=\left|\frac{{\&PartialD;F}_p}{\&PartialD;\mathrm{\&theta;}}\frac{\mathrm{d\&theta;}}{d(d_0-\mathrm{l\&theta;})}\right|\\ =\left|\right[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\left]\right[-\frac{2}{{(d_0+\mathrm{l\&theta;})}^3}-\frac{2}{{(d_0+\mathrm{l\&theta;}+2\mathrm{\&delta;})}^3}+\frac{4}{{(d_0+\mathrm{l\&theta;}+\mathrm{\&delta;})}^3}\left]\right|\end{array}$

$\begin{array}{c}{k}_n=\left|\frac{{\mathrm{\&delta;F}}_n}{\mathrm{\&delta;}(d_0-\mathrm{l\&theta;})}\right|=\left|\frac{{\&PartialD;F}_n}{\&PartialD;(d_0-\mathrm{l\&theta;})}\right|=\left|\frac{{\&PartialD;F}_n}{\&PartialD;\mathrm{\&theta;}}\frac{\mathrm{d\&theta;}}{d(d_0-\mathrm{l\&theta;})}\right|\\ =\left|\right[\frac{B_r^2{A}_m^2{(\mathrm{\&delta;}+r)}^2}{{\mathrm{\&pi;\&mu;}}_0{\mathrm{\&delta;}}^2}\left]\right[-\frac{2}{{(d_0-\mathrm{l\&theta;})}^3}-\frac{2}{{(d_0-\mathrm{l\&theta;}+2\mathrm{\&delta;})}^3}+\frac{4}{{(d_0-\mathrm{l\&theta;}+\mathrm{\&delta;})}^3}\left]\right|\end{array}$

All there is k obvious corresponding TMD mass optional position _mag> 0, therefore k _e< k _l, namely original system rigidity reduces, now TMD natural frequency decline, thus realize lower vibration frequency with shorter pendulum length.

Embodiment two: the test model see Fig. 6-Figure 18, Fig. 6 being making, form the chamber that shakes between its medium-height trestle 5, top board 7, base plate 8, bearing 6 is arranged on both sides corresponding to mass, and for fixing permanent magnet.Wherein, pendulum length l=1.9m, mass quality m=10kg, the design maximum pendulum angle θ of pendulum _max=3 °.Distance d during this experiment permanent magnet equilbrium position ₀=18cm, Circular permanent magnet swage N38, dimension D 150 × 10mm.Experimental result sees attached list 1.

Experimental result as can be seen from subordinate list 1, adopt the inventive method to reducing the frequency effects of pendulum-type TMD clearly, when pendulum reaches its design amplitude, 1 group of permanent magnet is placed in mass both sides can make TMD frequency reduce by 5.7%, and 2 groups of permanent magnets are placed in mass both sides can make TMD frequency reduce by 11.9%.

Subordinate list 1:

Claims (2)

1. a ultralow frequency pendulum-type tuned mass damper, it is characterized in that, comprise the pendulum chamber be arranged in structure, the hoist cable be connected with the structure of pendulum top of chamber, the mass of hanging in hoist cable bottom, be arranged on the viscous damper between mass and structure and negative stiffness adjusting device, the quantity of described viscous damper and negative stiffness adjusting device is two and all arranges in the bilateral symmetry that mass is corresponding, described negative stiffness adjusting device comprises n block and is arranged on the permanent magnet that the polarity of mass wherein on a side is N pole/S pole, with the permanent magnet that the n block polarity be arranged on structure corresponding to this side is S pole/N pole.

2. ultralow frequency pendulum-type tuned mass damper according to claim 1, is characterized in that, described permanent magnet is cylindrical magnet iron.