Abstract
In this paper, we study and compare performance and robustness of linear and nonlinear Lanchester dampers. The linear Lanchester damper consists of a small mass attached to a primary system through a linear dashpot, whereas the nonlinear Lanchester damper is linked to the primary mass through dry friction forces. In each case, we propose a semi-analytical method for computing the frequency response, for different values of the design parameters, in order to evaluate the performance and robustness of the two kinds of damper. Overall, it is shown that linear Lanchester dampers perform better than nonlinear damper both in terms of attenuation and robustness. Moreover, the nonlinear frequency response curves, that include the intrinsic non-smooth nature of the friction force, may serve as reference curve for further numerical studies.
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References
Preumont, A.: Vibration Control of Active Structures, 3rd edn. Springer, New York (2011)
Ducarne, J., Thomas, O., Deü, J.-F.: Structural vibration reduction by switch shunting of piezoelectric elements: modelling and optimization. J. Intell. Mater. Syst. Struct. 21(8), 797–816 (2010)
Thomas, O., Ducarne, J., Deü, J.-F.: Performance of piezoelectric shunts for vibration reduction. Smart Mater. Struct. 21(1), 015008 (2012)
Berardengo, M., Thomas, O., Giraud-Audine, C., Manzoni, S.: Improved resistive shunt by means of negative capacitance: new circuit, performances and multi-mode control. Smart Mater. Struct. 25(7), 075033 (2016)
Hammami, C., Balmes, E., Guskov, M.: Numerical design and test on an assembled structure of a bolted joint with viscoelastic damping. Mech. Syst. Signal Process. 70–71, 714–724 (2016)
Morin, B., Legay, A., Deü, J.-F.: Reduced order models for dynamic behavior of elastomer damping devices. Finite Elem. Anal. Des. 143, 66–75 (2018)
Krenk, S.: Frequency analysis of the tuned mass damper. J. Appl. Mech. 72, 936–942 (2005)
Lanchester, F.W.: Damping torsional vibrations in crank shafts, U.S. Patent No. 1085443 (1914)
Den Hartog, J.P.: Mechanical Vibrations. McGraw-Hill, New York (1956)
Vidmar, B.J., Shaw, S.W., Feeny, B.F., Geist, B.K.: Nonlinear interactions in systems of multiple order centrifugal pendulum vibration absorbers. J. Vib. Acoust. 135, 061012 (2013)
Renault, A., Thomas, O., Mahé, H.: Numerical antiresonance continuation of structural systems. Mech. Syst. Signal Process. 116, 963–984 (2019)
Berardengo, M., Thomas, O., Giraud-Audine, C., Manzoni, S.: Improved shunt damping with two negative capacitances: an efficient alternative to resonant shunt. J. Intell. Mater. Syst. Struct. 28(16), 2222–2238 (2017)
Snowdon, J.C.: Vibration and Shock in Damped Mechanical Systems. Wiley, New York (1968)
Genta, G.: Vibration Dynamics and Control. Springer, New York (2009)
Lanchester, F.: Damping torsional vibrations in crank-shafts, US Patent 1,085,443 (1914). https://www.google.com/patents/US1085443
Charleux, D., Gibert, C., Thouverez, F., Dupeux, J.: Numerical and experimental study of friction damping blade attachments of rotating bladed disks. J. Rotating Mach. 2006, 13 (2006)
Laxalde, D., Thouverez, F.: Forced response analysis of integrally bladed disks with friction ring dampers. J. Vib. Acoust. 132(1), 011013-1–011013-9 (2010)
Lopez, L., Busturia, J.M., Nijmeijer, H.: Energy dissipation of a friction damper. J. Sound Vib. 278, 539–561 (2004)
Brunel, J.F., Dufrenoy, P., Charley, J., Demilly, F.: Analysis of the attenuation of railway squeal noise by preloaded rings inserted in wheels. J. Acoust. Soc. Am. 127, 1300–1306 (2010)
Den Hartog, J.: Forced vibrations with combined Coulomb and viscous friction. Trans. ASME 53(15), 107–115 (1931)
Den Hartog, J., Ormondroyd, J.: Torsional vibration dampers. Trans. Am. Soc. Mech. Eng. Appl. Mech. Div. 52, 133–152 (1929)
Ye, S., Williams, K.A.: Torsional friction damper optimization. J. Sound Vib. 294(3), 529–546 (2006)
Bapat, V., Prabhu, P.: Optimum design of lanchester damper for a viscously damped degree of freedom system by using minimum force transmissibility criterion. J. Sound Vib. 67(1), 113–119 (1979)
Bapat, V., Prabhu, P.: Optimum design of a lanchester damper for a viscously damped single degree of freedom system subjected to inertial excitation. J. Sound Vib. 73(1), 113–124 (1980)
Fu, Z.F., He, J.: Modal Analysis. Butterworth-Heinemann, Oxford (2001)
Nayfeh, A.H., Balachandran, B.: Applied Nonlinear Dynamics: Analytical, Computational and Experimental Methods. Wiley, New York (1995)
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Appendix A: Symmetry in the response curves
Appendix A: Symmetry in the response curves
We consider the following harmonically forced dynamical system:
where x(t) is a function of time t, \({\dot{\circ }}\) is the time derivative of \(\circ \), m, c, k are mass, damping and stiffness constants, \({ f}_\mathrm{nl}({ {\dot{x}}})\) is the nonlinear internal force and \({ f}_\mathrm{e}\) is the external force.
We assume that \({ f}_\mathrm{nl}({ \dot{x}})\) is an odd function of \({ \dot{x}}\), which means that for all \({ \dot{x}}\):
As a consequence, its Taylor series expansion around 0 contents only odd terms:
where the \(a_i\), \(i\in \mathbb {N}\) are the Taylor coefficients of \(f_\mathrm{nl}\). If periodic solutions of Eq. (A.1), in the steady state, are under concern, they can be written as the following Fourier series:
where \(\Omega =2\pi /T\) is the frequency of motion, T its period and \((x_h^c, x_h^s)\) are the Fourier coefficients of x(t). In Eq. (A.1), the harmonics content of x(t) is created by the only nonlinear term of the equation, the function \(f_\mathrm{nl}\). Since it is odd, it creates only odd harmonics in x(t). For instance, if \(x(t)=\cos (\Omega t+\varphi )=\cos \phi \), \(x^3=(3\cos \phi + \cos 3\phi )/4\), \(x^5=(10\cos \phi + 5\cos 3\phi +\cos 5\phi )/16\)... so that:
As a consequence, the simplest solution x(t) of Eq. (A.1) is composed only by odd harmonics:
Even harmonics can still be created after a symmetry breaking bifurcation, a case out of the scope of the present text. Now, we consider the following symmetry property of the T-periodic time function x(t):
so that one half of the period is the inverse mirror of the other half-period. Inserting Eq. (A.7) into Eq. (A.4), one shows that necessarily all even harmonics of x(t) are zero, so that x(t) has an odd harmonics content [Eq. (A.6)]. The reciprocal rule is also verified: any time periodic function with an odd harmonics content verifies the symmetry property (A.7).
As a conclusion, if \(f_\mathrm{nl}(\dot{x})\) is an odd function of \(\dot{x}\), the harmonics content of the basic (without considering symmetry breaking bifurcations) nonlinear solution x(t) of Eq. (A.1) is necessarily odd and the symmetry property (A.7) is verified.
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Vakilinejad, M., Grolet, A. & Thomas, O. A comparison of robustness and performance of linear and nonlinear Lanchester dampers. Nonlinear Dyn 100, 269–287 (2020). https://doi.org/10.1007/s11071-020-05512-x
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DOI: https://doi.org/10.1007/s11071-020-05512-x