“…When the primary system comprises several polynomial nonlinearities, we demonstrate that the NLTVA obeys a principle of additivity, i.e., each nonlinear coefficient can be calculated independently of the other nonlinear coefficients using the proposed formula.damper of the absorber, it is possible to approximately obtain H ∞ optimization of the frequency response in the vicinity of the target resonant frequency.Thanks to its simplicity, effectiveness, low cost and small requirements for maintenance [7], the passive vibration absorber (often referred to as tuned mass damper, tuned vibration absorber or dynamic vibration absorber) was extensively studied and implemented in real-life structures. Its main applications include structures subject to human-induced vibrations, such as spectator stands and pedestrian bridges (the most famous example is the Millenium bridge in London [8]), steel structures excited by machines such as centrifuges and fans, aircraft engines [9], helicopter rotors [10], tall and slender structures subject to wind-induced vibrations, but also power lines [11] and long-span suspended bridges [12,13]. For a list of installations of vibration absorbers in civil structures the interested reader can refer to [14,15].An overview of existing designs for passive vibration absorbers is given in [7].…”
This paper develops a principle of similarity for the design of a nonlinear
absorber, the nonlinear tuned vibration absorber (NLTVA), attached to a
nonlinear primary system. Specifically, for effective vibration mitigation, we
show that the NLTVA should feature a nonlinearity possessing the same
mathematical form as that of the primary system. A compact analytical formula
for the nonlinear coefficient of the absorber is then derived. The formula,
valid for any polynomial nonlinearity in the primary system, is found to depend
only on the mass ratio and on the nonlinear coefficient of the primary system.
When the primary system comprises several polynomial nonlinearities, we
demonstrate that the NLTVA obeys a principle of additivity, i.e., each
nonlinear coefficient can be calculated independently of the other nonlinear
coefficients using the proposed formula
“…When the primary system comprises several polynomial nonlinearities, we demonstrate that the NLTVA obeys a principle of additivity, i.e., each nonlinear coefficient can be calculated independently of the other nonlinear coefficients using the proposed formula.damper of the absorber, it is possible to approximately obtain H ∞ optimization of the frequency response in the vicinity of the target resonant frequency.Thanks to its simplicity, effectiveness, low cost and small requirements for maintenance [7], the passive vibration absorber (often referred to as tuned mass damper, tuned vibration absorber or dynamic vibration absorber) was extensively studied and implemented in real-life structures. Its main applications include structures subject to human-induced vibrations, such as spectator stands and pedestrian bridges (the most famous example is the Millenium bridge in London [8]), steel structures excited by machines such as centrifuges and fans, aircraft engines [9], helicopter rotors [10], tall and slender structures subject to wind-induced vibrations, but also power lines [11] and long-span suspended bridges [12,13]. For a list of installations of vibration absorbers in civil structures the interested reader can refer to [14,15].An overview of existing designs for passive vibration absorbers is given in [7].…”
This paper develops a principle of similarity for the design of a nonlinear
absorber, the nonlinear tuned vibration absorber (NLTVA), attached to a
nonlinear primary system. Specifically, for effective vibration mitigation, we
show that the NLTVA should feature a nonlinearity possessing the same
mathematical form as that of the primary system. A compact analytical formula
for the nonlinear coefficient of the absorber is then derived. The formula,
valid for any polynomial nonlinearity in the primary system, is found to depend
only on the mass ratio and on the nonlinear coefficient of the primary system.
When the primary system comprises several polynomial nonlinearities, we
demonstrate that the NLTVA obeys a principle of additivity, i.e., each
nonlinear coefficient can be calculated independently of the other nonlinear
coefficients using the proposed formula
“…where C2 can be obtained from the definition of the state given by Equation (14) and the matrices D21 = 0 and D22 = 0. Equations (15), (17), and (21) cast the design of the two 2DOFs TMDs system as a decentralized control problem in the block diagram of Figure 2.…”
Section: Of 21mentioning
confidence: 99%
“…The MTMDs is used to damp suspension bridges for several purposes. In some studies, the MTMDs are used to the suppression of buffeting, flutter or increasing the critical flutter wind speed [17,18]. Other studies consider MTMDs for alleviating pedestrian-and jogger-induced vibration [19][20][21][22] or traffic-induced vibration [23][24][25][26].Generally, the weight of a TMD is limited to 1-3% of the structure weight.…”
This paper proposes a synthetic approach to design and implement a two-degree of freedom tuned mass damper (2DOFs TMD), aimed at damping bending and torsional modes of bridge decks (it can also be applied to other types of bridges like cable-stayed bridges to realize the energy dissipation). For verifying the effectiveness of the concept model, we cast the parameter optimization of the 2DOFs TMDs conceptual model as a control problem with decentralized static output feedback for minimizing the response of the bridge deck. For designing the expected modes of the 2DOFs TMDs, the graphical approach was introduced to arrange flexible beams properly according to the exact constraints. Based on the optimized frequency ratios, the dimensions of 2DOF TMDs are determined by the compliance matrix method. Finally, the mitigation effect was illustrated and verified by an experimental test on the suspension bridge mock-up. The results showed that the 2DOFs TMD is an effective structural response mitigation device used to mitigate the response of suspension bridges. It was also observed that based on the proposed synthetic approach, 2DOFs TMD parameters can be effectively designed to realize the target modes control.
“…For each value of a, only a specific frequency should be considered, as expressed by Eq. (8). This means that specific points of the frequency response curve should be selected, as those marked by red dots in Fig.…”
Section: Analytical Investigation Of the Transient Dynamicsmentioning
confidence: 99%
“…Thanks to its simplicity, effectiveness and fully passive mode of operation, the TMD is today extensively used in real-life applications. Its main fields of applica-tion include civil structures, such as long-span bridges [8,9], skyscrapers [10] and slender towers [11], aircraft engines [12] and helicopter rotors [13,14], structures subject to human-induced vibrations [15] and production machines [16]. Several different designs for the TMD exist, as detailed in [17].…”
The dynamics of a nonlinear passive vibration absorber conceived to mitigate vibrations of a nonlinear host structure is considered in this paper.The system under study is composed of a primary system, consisting of an undamped nonlinear oscillator of Duffing type, and a nonlinear dynamic vibration absorber, denominated nonlinear tuned vibration absorber (NLTVA). The NLTVA consists of a small mass, attached to the host structure through a linear damper, a linear and a cubic spring. The host structure is subject to free vibrations and the performance of the NLTVA is evaluated with respect to the minimal time required to dissipate a specific amount of the mechanical energy of the system. In order to characterize the dynamics of the system, a combination of numerical and analytical techniques is implemented. In particular, on the basis of the first-order reduced model, slow invariant manifolds of the transient dynamics are identified, which enable to estimate the absorber performance. Results illustrate that two different dynamical paths exist and the system can undergo either of them, depending on the initial conditions and on the value of the absorber nonlinear stiffness coefficient. One path leads to a very fast vibration mitigation, and therefore to a favorable behavior, while the other one causes a very slow energy dissipation.
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