Abstract
This chapter is concerned with the problem of analysis and optimization of the inerter-based isolators based on a “uni-axial” single-degree-of-freedom isolation system. In the first part, in order to gain an in-depth understanding of inerter from the prospective of vibration, the frequency responses of both parallel-connected and series-connected inerters are analyzed. In the second part, three other inerter-based isolators are introduced and the tuning procedures in both the \(H_\infty \) optimization and the \(H_2\) optimization are proposed in an analytical manner. The achieved \(H_2\) and \(H_\infty \) performance of the inerter-based isolators is superior to that achieved by the traditional dynamic vibration absorber (DVA) when the same inertance-to-mass (or mass) ratio is considered. Moreover, the inerter-based isolators have two unique properties, which are more attractive than the traditional DVA: first, the inertance-to-mass ratio of the inerter-based isolators can easily be larger than the mass ratio of the traditional DVA without increasing the physical mass of the whole system; second, there is no need to mount an additional mass on the object to be isolated.
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References
Asami, T., Wakasono, T., Kameoka, K., Hasegawa, M., & Sekiguchi, H. (1991). Optimum design of dynamic absorbers for a system subjected to random excitation. JSME International Journal Series III, 34(2), 218–226.
Carrella, A., Brennan, M. J., Waters, T. P., & Lopes, V, Jr. (2012). Force and displacment transimissibility of a nonlinear isolator with high-static-low-dynamic-stiffness. International Journal of Mechanical Sciences, 55(1), 22–29.
Chen, M. Z. Q., Papageorgiou, C., Scheibe, F., Wang, F. C., & Smith, M. C. (2009). The missing mechanical circuit element. IEEE Circuits and Systems Magazine, 9(1), 10–26.
Chen, M. Z. Q., Hu, Y., Li, C., & Chen, G. (2015). Performance benefits of using inerter in semiactive suspensions. IEEE Transactions on Control System Technology, 23(4), 1571–1577.
Chen, M. Z. Q., Hu, Y., Huang, L., & Chen, G. (2014). Influence of inerter on natural frequencies of vibration systems. Journal of Sound and Vibration, 333(7), 1874–1887.
Cheung, Y. L., & Wong, W. O. (2011a). H-infinity optimization of a variant design of the dynamic vibration absorber-Revisited and new results. Journal of Sound and Vibration, 330(16), 3901–3912.
Cheung, Y. L., & Wong, W. O. (2011b). \({H_{2}}\) optimization of a non-traditional dynamic vibration abosorber for vibration control of structures under random force excitation. Journal of Sound and Vibration, 330(6), 1039–1044.
Den Hartog, J. P. (1985). Mechanical Vibrations. New York: Dover Publications, INC.
Doyle, J. C., Francis, B. A., & Tannenbaum, A. R., et al. (1992). Feedback Control Theory. Oxford: Maxwell Macmillan Int.
Dylejko, P. G., & MacGillivray, I. R. (2014). On the concept of a transmission absorber to suppress internal resonance. Journal of Sound and Vibration, 333, 2719–2734.
Hu, Y., Chen, M. Z. Q., & Shu, Z. (2014). Passive vehicle suspensions employing inerters with multiple performance requirements. Journal of Sound and Vibration, 333(8), 2212–2225.
Hu, Y., Chen, M. Z. Q., Shu, Z., & Huang, L. (2014). Vibration analysis for isolation system with inerter. In Proceedings of the 33rd Chinese Control Conference (pp. 6687–6692). China: Nanjing.
Inman, D. J. (2008). Engineering Vibration (3rd ed.). Upper Saddle River: Prentice-Hall Inc.
Lazar, I. F., Neild, S. A., & Wagg, D. J. (2014). Using an inerter-based device for structural vibration suppression. Earthquake Engineering and Structure Dynamics, 43(8), 1129–1147.
Marian, L., & Giaralis, A. (2014). Optimal design of a novel tuned mass-damper-inerter (TMDI) passive vibration control configuration for stochastically support-excited structural systems. Probabilistic Engineering Mechanics, 38, 156–164.
Nishihara, O., & Asami, T. (2002). Closed-form solutions to the exact optimizations of dynamic vibration absorbers (minimizations of the maximum amplitude magnification factors). Journal of Vibration and Acoustics, 124(4), 576–582.
Ren, M. Z. (2001). A variant design of the dynamic vibration absorber. Journal of Sound and Vibration, 245(4), 762–770.
Rivin, E. I. (2003). Passive Vibration Isolation. New York: ASME Press.
Piersol, A. G., & Paez, T. L. (2010). Harris’ Shock and Vibration Handbook (6th ed.). New York: McGraw-Hill.
Scheibe, F., & Smith, M. C. (2009). Analytical solutions for optimal ride comfort and tyre grip for passive vehicle suspensions. Vehile System Dynamics, 47(10), 1229–1252.
Smith, M. C. (2002). Synthesis of mechanical networks: The inerter. IEEE Transaction on Automatic Control, 47(1), 1648–1662.
Smith, M. C., & Wang, F. C. (2004). Performance benefits in passive vehicle suspensions employing inerters. Vehicle System Dynamics, 42(4), 235–257.
Wang, F.-C., & Chan, H. A. (2011). Vehicle suspensions with a mechatronic network strut. Vehicle System Dynamics, 49(5), 811–830.
Wang, F.-C., Hsieh, M.-R., & Chen, H.-J. (2012). Stability and performance analysis of a full-train system with inerters. Vehicle System Dynamics, 50(4), 545–571.
Wang, K., Chen, M. Z. Q., & Hu, Y. (2014). Synthesis of biquadratic impedances with at most four passive elements. Journal of the Franklin Institute, 351(3), 1251–1267.
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Appendix
Appendix
Proof of Proposition 3.1
Observing Fig. 3.6, it is shown that the curve horizontally passing through P indicates the optimal damping. This optimal damping can be obtained by solving the following equation:
Denote \(\mu =\sqrt{\frac{n}{m}}\), where \(n=\delta ^2q^2+4(1-\delta q^2)^2\zeta ^2\), \(m=\delta ^2(1-q^2)^2q^2+4(1-(1+\delta )q^2)^2\zeta ^2\). Equation (3.46) can be written in another form as
where \(n^\prime =\mathrm {\partial } n/ \mathrm {\partial } q^2\) and \(m^\prime =\mathrm {\partial } m/ \mathrm {\partial } q^2\). For the invariant point P,
therefore,
Since
after substituting \(q_P\) into (3.14), one obtains
Proof of Proposition 3.2
Denote
Then, \(\mu \) in (3.17) can be rewritten as
To find the invariant points which are independent of damping, it requires
that is,
With the plus sign, after cross-multiplication, one obtains \( \delta ^2 \lambda q^6=0, \) which leads to the trivial solution \(q=0\). With the minus sign, after simple calculation, one obtains
which is a cubic form in \(q^2\). Therefore, there are three invariant points for the configuration C3.
Denoting these three invariant points as P, Q, and R (\(q_P<q_Q<q_R\)), separately, one obtains
Since at points P and Q, the values of \(\mu \) are independent of \(\zeta \), then in the case of \(\zeta =\infty \), one obtains
It can be checked that
Then, one obtains
After cross-multiplication and simplification, one obtains
Substituting (3.50) and (3.51) into (3.52), one can obtain a quadratic equation with respect to \(q^2_R\) as
Note that \(q_R\) is the same solution as both (3.48) and (3.53) for the same \(\delta \) and \(\lambda \). Solving \(\lambda \) from (3.48) and (3.53), separately, one obtains
Equating the solutions and simplifying the results, one obtains
Then, one obtains \(q^2_R\) as shown in (3.18).
From (3.18), it is easy to show that \(q^2_R\ge 3\), which is relatively large compared with the natural frequency. This can explain why only invariant points P and Q are involved in the \(H_\infty \) tuning of C3.
In this way, the optimal \(\lambda \) can be obtained by substituting \(q^2_R\) in (3.18) into (3.54) or (3.55). After obtaining \(\lambda \), all the three invariant points can be obtained by solving
which is obtained from (3.50) and (3.51).
The procedure of calculating the optimal damping ratio \(\zeta \) is similar to the procedure in appendix, where the optimal \(\zeta \) makes the gradients at invariant points P and Q zero. After calculation and simplification, one obtains (3.21). Taking an average of \(\zeta ^2_P\) and \(\zeta ^2_Q\), one obtains the optimal \(\zeta _{opt}\) as in (3.20).
Proof of Proposition 3.3
Denote
and \(\mu \) in (3.23) can be rewritten as
To find the invariant points which are independent of damping, it requires
that is,
Again, with the plus sign, one obtains the trivial solution zero, and with the minus sign, one obtains
Then, one obtains the two invariant points P and Q (\(q_P<q_Q\)) as
Letting the ordinates at invariant points P and Q equal, one has
It can be checked that \(\frac{1}{1-q^2_P}>0\) and \(\frac{1}{1-q^2_Q}<0\). Then, one obtains
After cross-multiplication and simplification, one has
Considering (3.58), one obtains
which leads to (3.24).
Similar to the method in appendix, the optimal \(\zeta \) can be obtained by making \(\mu \) to have zero gradients at invariant points P and Q. After calculation and simplification, one obtains
After substituting (3.59) and (3.24), one obtains (3.26) and (3.27).
Taking an average of \(\zeta ^2_p\) and \(\zeta ^2_Q\), one obtains the optimal \(\zeta _{opt}\) as in (3.25).
Proof of Proposition 3.4
Denote
Then, \(\mu \) in (3.28) can be rewritten as
To find the invariant points which are independent of damping, it requires
that is,
Similarly, with plus sign, one obtains the trivial solution zero, and with minus sign, one obtains
Thus, one obtains the two invariant points P and Q (\(q_P<q_Q\)) as in (3.32).
Letting the ordinates at invariant points P and Q equal, one has
It can be checked that \(\frac{\lambda +1}{\lambda +1-\lambda q^2_P}>0\) and \(\frac{\lambda +1}{\lambda +1-\lambda q^2_Q}<0\). Then, one obtains
After cross-multiplication and simplification, one has
Comparing with (3.62), one obtains
which leads to
It can be checked that this equation has real solutions if and only if
Under this condition, the optimal \(\lambda \) can be obtained as in (3.29).
Note that if \(\delta =\frac{1}{2}\), from (3.29), one has \(\lambda =0\) or \(k=\infty \). In this case, C5 reduces to C1. Thus, the more reasonable assumption is \(\delta <\frac{1}{2}\) rather than \(\delta \le \frac{1}{2}\).
Similarly, the optimal \(\zeta \) can be obtained by making \(\mu \) to have zero gradients at invariant points P and Q. After calculation and simplification, one obtains \(\zeta ^2_P\) and \(\zeta ^2_Q\) as in (3.31).
Taking an average of \(\zeta ^2_p\) and \(\zeta ^2_Q\), one obtains the optimal \(\zeta _{opt}\) as in (3.30).
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Chen, M.Z.Q., Hu, Y. (2019). Inerter-Based Isolation System. In: Inerter and Its Application in Vibration Control Systems. Springer, Singapore. https://doi.org/10.1007/978-981-10-7089-1_3
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