DOUBLE-RING SHAPED STRONG MAGNET ARRAY NONLINEAR DYNAMIC VIBRATION ABSORBER FOR VIBRATION MITIGATION OF SUSPENDER CABLES AND DESIGN METHOD THEREOF

Abstract

A double-ring shaped strong magnet array nonlinear dynamic vibration absorber for vibration mitigation of suspender cables and design method thereof, which belongs to the field of structural vibration control. The installation positions and number are designed according to the demand of vibration mitigation, and usually one is installed at the midpoint of the suspender cable. The vibration absorber consists of the inner and outer magnet ring arrays, the additional weights, the universal wheels and a base. It feeds back the control force in the opposite direction of the motion of the suspender cable during the movement, so that the vibration energy of the suspender cable is transferred to the vibration absorber and thus less is returned to the suspender cable, and the energy dissipated through the friction between the universal wheels and the base, adding air dampers and other measures, etc.

Claims

1. A double-ring shaped strong magnet array nonlinear dynamic vibration absorber for vibration mitigation of suspender cables, including an inner magnet ring array, an outer magnet ring array, additional weights, universal wheels and a base; wherein, when used for in-service suspender cables, the inner magnet ring array is made of two inner ring subdivisions, and each inner ring subdivision having a designed number of slots, then an inner ring magnet shoe is put in each slot, and inner ring steel limiters are fixed to the corresponding inner ring subdivision by bolts, then non-slip gaskets are added to inside of the inner ring subdivision, and then the inner magnet ring array is fixed at installation position of the suspender cable; the outer magnet ring array is similar in construction to the inner magnet ring array, and each outer ring magnet shoe is placed in a designed slot and fixed to an outer ring subdivision I and an outer ring subdivision II by outer ring steel limiters, and the outer magnet ring array is connected to the additional weights and the universal wheels respectively by bolts, and the additional weights are installed on periphery of the outer magnet ring array and fixed together with the outer magnet ring array; the additional weight is a square-shaped body which is put four cuboid mass blocks together by bolts; the base is made of two identical base subdivisions, with non-slip gaskets on inside of the base, and the two identical base subdivisions are fixed to the installation position of the suspender cable by bolts to support the outer magnet ring array, the additional weights and the universal wheels; the universal wheels are in direct touch with the base, rotate in any direction, and provide damping by friction with the base, and the damping provided is adjusted by changing coefficient of friction between the universal wheels and the base; dissipation of energy is through damping provided by friction, or by adding several air dampers between the inner magnet ring array and the outer magnet ring array; dimensions of the additional weights, the inner ring magnet shoe and the outer ring magnet shoe are designed according to basic parameters of the suspender cable to be controlled, and magnetic force between the inner magnet ring array and the outer magnet ring array ensures that the outer magnet ring array does not collide with the inner magnet ring array during movement; installation positions and number of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber on the suspender cable are designed according to dynamic characteristics and demand of vibration mitigation of the suspender cable to be controlled, with at least one installed at midpoint position of the suspender cable.

2. A design method of a double-ring shaped strong magnet array nonlinear dynamic vibration absorber for vibration mitigation of suspender cables, comprising steps of: step 1, obtaining basic characteristics of a suspender cable to be controlled by field survey or looking over design parameters: outer diameter of sheath for the suspender cable, and natural frequencies; step 2, determining basic design parameters of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber to be designed: ratio of sum of masses of an outer magnet ring array and additional weights to modal mass of the suspender cable: 1% to 5%, and within which the larger the mass ratio, the better the vibration mitigation effect, and the ratio should be determined according to demand of vibration mitigation for the suspender cable; damping ratio of the vibration absorber: design damping ratio of the vibration absorber is taken as design damping ratio of optimal tuned mass damper under the same mass ratio; linear and cubic stiffness values of the vibration absorber: numerical model of cable-absorber system is established as shown in equation: $\begin{array}{cc}\{\begin{array}{c}M\stackrel{\mathrm{.Math.}}{w}\left(t\right)+C\stackrel{.}{w}\left(t\right)+\mathrm{Kw}\left(t\right)=F\left(t\right)\\ m\stackrel{\mathrm{.Math.}}{v}+c\left[\stackrel{.}{v}-\stackrel{.}{w}\delta \left(x-d\right)\right]+k_1\left[v-w\delta \left(x-d\right)\right]+{k_2\left[v-w\delta \left(x-d\right)\right]}^3=0\end{array}& \left(1\right)\end{array}$ where, w(t) denotes vector of displacements corresponding to each degree of freedom of the suspender cable, {dot over (w)}(t) and {dot over (w)}(t) correspond to velocity and acceleration of the suspender cable, respectively; M is mass matrix of the suspender cable; C is damping matrix of the suspender cable using Rayleigh damping; K is stiffness matrix of the suspender cable; F(t) is sum of external loads on the suspender cable and reaction of the vibration absorber to the suspender cable; m, c, k.sub.1, k.sub.2 denote mass, damping, linear stiffness and nonlinear stiffness of the vibration absorber, respectively; ν denotes displacement of the vibration absorber, {dot over (ν)} and {umlaut over (ν)} denote velocity and acceleration of the vibration absorber, respectively; one end of the suspender cable is starting point of x-axis, x is x-axis coordinate of point on the suspender cable, d is installation location of the vibration absorber on x-axis, and δ(x−d) is Dirac function; equation (2) is objective function for parameter optimization, $\begin{array}{cc}J=\min \left(\frac{{\Delta }_{\mathrm{con}}}{\Delta }\right)& \left(2\right)\end{array}$ where Δ and Δ.sub.con denote root-mean-square value, variance or other vibration mitigation effect evaluation indices of time-history responses of displacement or velocity at a point on the suspender cable under the same white noise load without and with vibration control, respectively, and they are selected or established according to the demand of vibration mitigation; based on optimal linear stiffness of TMD, optimal parameters ranges of the linear stiffness and nonlinear stiffness of nonlinear absorber are determined, dynamic responses of the suspender cable are calculated by using the numerical model of the cable-absorber system under the white noise loads at multiple points, and the optimal linear stiffness and the optimal nonlinear stiffness are obtained by automatic optimization; 4) geometric parameters of the inner and outer magnet ring arrays: with overall consideration of cost of the vibration absorber and section size of the suspender cable to be controlled, number, radius angle and inner diameter of magnet shoes in the inner magnet ring array and the outer magnet ring array can be determined; a parametric electromagnetic field numerical model of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber system is established, and by adjusting thickness and height of the magnet shoe, combination of inner and outer magnet ring arrays composed of the inner magnet ring array and the outer magnet ring array achieves designed linear stiffness and designed cubic stiffness; 5) geometric parameters of additional weights for the vibration absorber: total mass of the vibration absorber minus mass of the outer magnet ring array is the mass of additional weights, and then length, width and height of the additional weights are designed according to density of additional weight block; step 3, machining and fabricating the double-ring shaped strong magnet array nonlinear dynamic vibration absorber according to the design parameters obtained from step 2; step 4, installing the manufactured double-ring shaped strong magnet array nonlinear dynamic vibration absorber on the suspender cable in the laboratory, and measuring the force-displacement relationship of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber with a dynamometer and a ruler to ensure the linear stiffness and the cubic stiffness to be the design values; letting the vibration absorber move freely, then measuring the displacement signal, and determining the damping ratio by free vibration attenuation method etc., and then adjusting the damping ratio by adjusting the friction force between universal wheels and a base or by setting other damping to make that the damping ratio reaches or approaches the optimal damping ratio.

Description

DESCRIPTION OF DRAWINGS

[0022] FIG. 1 is a schematic diagram of the invented double-ring shaped strong magnet array nonlinear dynamic vibration absorber for the suspender cable.

[0023] FIG. 2 is a schematic diagram of an inner magnet ring array.

[0024] FIG. 3 is a schematic diagram of an outer magnet ring array.

[0025] FIG. 4 is a schematic diagram of an additional weight subdivision.

[0026] FIG. 5 is a schematic diagram of a base subdivision.

[0027] Where: 1 suspender cable; 2 inner magnet ring array; 3 outer magnet ring array; 4 additional weight; 5 universal wheel; 6 base; 7 inner ring subdivision; 8 inner ring magnet shoe; 9 inner ring steel limiter; 10 first kind of bolt hole; 11 second kind of bolt hole; 12 third kind of bolt hole; 13 fourth kind of bolt hole; 14 fifth kind of bolt hole; 15 outer ring steel limiter; 16 outer ring magnet shoe; 17 outer ring subdivision I; 18 outer ring subdivision II; 19 sixth kind of bolt hole; 20 seventh kind of bolt hole; 21 base subdivision.

DETAILED DESCRIPTION

[0028] Combining the attached drawings and technical solutions, the detailed implementation method of the invention is further explained in the following parts. Taking one suspender cable of a suspension bridge as an example, the design method of the dimensional parameters and the installation process of the invented absorber are introduced in detail, and the numerical results are combined to illustrate the vibration mitigation effect of the invention for the suspender cable.

[0029] A suspension bridge suspender cable is selected, which has an effective calculated length of 60.954 m and a mass of 2961 Kg, and the first order natural frequency of the suspender cable is 1.952 Hz based on the finite element modeling and analysis. According to the steps proposed by the invention, the dimensions of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber are designed: the sum of the outer magnet ring array and the additional weights is 39.09 kg, the mass ratio to the suspender cable to be controlled is set to 1.32%, the optimal damping value of the vibration absorber is calculated to be 70N/(m/s), the optimal linear stiffness value is 4438 N/m, and the optimal cubic stiffness value is 1.511×10.sup.6 N/m.sup.3. Based on the finite element analysis software MAXWELL in the electromagnetic field, the parametric electromagnetic-field numerical model of the double-ring shaped strong magnet array is established, and parameters of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber are calculated as follows: the number of magnet shoes for both inner and outer magnet ring arrays is 9, the thickness of such magnet shoes is 0.018 m, the height of such magnet shoes is 0.1 m, the radius angle of such magnet shoes is 30 degrees, the inner radius of magnet shoes in the inner magnet ring array is 61.5 mm, and the inner radius of magnet shoes in the outer magnet ring array is 129.5 mm; four additional weights are the same, and each has a height of 0.1 m, thickness of 0.04 m and length of 0.36 m. These parameters change as the mass ratio changes.

[0030] In order to examine the vibration mitigation effect of this vibration absorber, the finite element model of the suspender cable to be controlled is established based on the SIMULINK software, the dynamic responses of the suspender cable before and after the installation of the double-ring shaped strong magnet array nonlinear dynamic vibration absorber are obtained using the transient analysis method, and the results of displacement and velocity dynamic responses before and after the installation of the damper at the midpoint of the suspender cable are shown in FIG. 6 and FIG. 7, respectively. It can be seen that under the same excitation, the displacement and velocity responses of the midpoint of the suspender cable decrease significantly after the installation of the vibration absorber.

[0031] Table 1 shows the comparison results of dynamic responses at the midpoint of the suspender cable with and without a double-ring shaped strong magnet array nonlinear dynamic vibration absorber under the same band-limited white noise excitation, these results are the average values of the dynamic response calculated results under 20 sets of random white noise excitation, and it can be seen that: after the installation of the invented vibration absorber, the displacement and velocity vibration responses at the midpoint of the suspender cable are significantly reduced, and the vibration mitigation effect becomes better with the increase of the mass ratio; the double-ring shaped strong magnet array nonlinear dynamic vibration absorber has significant effect on suppressing the vibration of the suspender cable.

TABLE-US-00001 TABLE 1 Reduction values of the vibration responses indices of the midpoint at a suspender cable after the installation of the invented nonlinear dynamic vibration absorber Reduction ratio of displacement Reduction ratio of velocity vibration response index vibration response index Root mean Root mean Variance square Peak Variance square Peak 1.32% mass ratio 52.75% 30.83% 20.59% 40.70% 22.45% 16.62% 2.00% mass ratio 67.69% 41.67% 33.82% 54.17% 31.78% 24.83%