Abstract
The paper is devoted to discuss the effects of nonlinear damping on the post-critical behavior of the Ziegler’s column. The classical Ziegler’s double-pendulum is considered in regime of finite displacements, in which, moreover, nonlinear damping of Van der Pol-type is introduced at the hinges. A second-order Multiple Scale analysis is carried out on the equations of motion expanded up to the fifth-order terms. The nature of the Hopf bifurcation, namely, supercritical or subcritical, as well as the occurrence of the ‘hard loss of stability’ phenomenon, are investigated. The effects of the nonlinear damping on the amplitude of the limit-cycle are finally studied for different linearly damped columns.
Similar content being viewed by others
References
Beck M (1952) Die Knicklast des einseitig eingespannten, tangential gedrückten Stabes. Zeitschrift für angewandte Mathematik und Physik ZAMP 3(3):225–228 ISSN 0044-2275
Ziegler H (1952) Die Stabilitätskriterien der Elastomechanik. Ing Arch 20(1):49–56
Bolotin VV (1963) Nonconservative problems of the theory of elastic stability. Macmillan, New York
Herrmann G, Jong IC (1965) On the destabilizing effect of damping in nonconservative elastic systems. J Appl Mech 32(3):592–597
Herrmann G (1967) Stability of equilibrium of elastic systems subjected to non-conservative forces. Appl Mech Rev 20:103–108
Leipholz H (1964) Über den Einfluss der Dämpfung bei nichtkonservativen Stabilitätsproblemen elastischer Stäbe. Ing Arch 33(5):308–321
Plaut RH, Infante EF (1970) The effect of external damping on the stability of Beck’s column. Int J Solids Struct 6(5):491–496
Plaut RH (1971) A new destabilization phenomenon in nonconservative systems. ZAMM Zeitschrift für Angewandte Mathematik und Mechanik 51(4):319–321
Walker JA (1973) A note on stabilizing damping configurations for linear nonconservative systems. Int J Solids Struct 9(12):1543–1545
Banichuk NV, Bratus AS, Myshkis AD (1989) Stabilizing and destabilizing effects in non-conservative systems. J Appl Math Mech 53(2):158–164
Kounadis AN (1992) On the paradox of the destabilizing effect of damping in non-conservative systems. Int J Non-Linear Mech 27(4):597–609
Seyranian AP, Mailybaev AA (2003) Multiparameter stability theory with mechanical applications, vol 13. World Scientific, Singapore
Kirillov ON, Seyranian AP (2005a) The effect of small internal and external damping on the stability of distributed non-conservative systems. J Appl Math Mech 69(4):529–552
Kirillov ON, Verhulst F (2010) Paradoxes of dissipation-induced destabilization or who opened Whitney’s umbrella? ZAMM Zeitschrift für Angewandte Mathematik und Mechanik 90(6):462–488
Kirillov ON (2005) A theory of the destabilization paradox in non-conservative systems. Acta Mech 174(3–4):145–166
Kirillov ON, Seyranian AP (2005b) Stabilization and destabilization of a circulatory system by small velocity-dependent forces. J Sound Vib 283:781–800
Kirillov ON (2013) Nonconservative stability problems of modern physics. Walter de Gruyter, Berlin
Luongo A, D’Annibale F (2015a) A paradigmatic minimal system to explain the Ziegler paradox. Contin Mech Thermodyn 27(1–2):211–222
Luongo A, D’Annibale F (2014) On the destabilizing effect of damping on discrete and continuous circulatory systems. J Sound Vib 333(24):6723–6741
Koiter WT (1996) Unrealistic follower forces. J Sound Vib 194(4):636–638
Sugiyama Y, Langthjem MA, Ryu B-J (1999) Realistic follower forces. J Sound Vib 225(4):779–782
Elishakoff I (2005) Controversy associated with the so-called follower forces: critical overview. Appl Mech Rev 58(2):117–142
Langthjem MA, Sugiyama Y (2000) Dynamic stability of columns subjected to follower loads: a survey. J Sound Vib 238(5):809–851
O’Reilly OM, Malhotra NK, Namachchivaya NS (1996) Some aspects of destabilization in reversible dynamical systems with application to follower forces. Nonlinear Dyn 10(1):63–87
Hagedorn P (1970) On the destabilizing effect of non-linear damping in non-conservative systems with follower forces. Int J Non-Linear Mech 5(2):341–358
Thomsen JJ (1995) Chaotic dynamics of the partially follower-loaded elastic double pendulum. J Sound Vib 188(3):385–405
Crespo da Silva MRM (1978a) Harmonic non-linear response of Beck’s column to a lateral excitation. Int J Solids Struct 14(12):987–997
Crespo da Silva MRM (1978b) Flexural–flexural oscillations of Beck’s column subjected to a planar harmonic excitation. J Sound Vib 60(1):133–144
Luongo A, Di Egidio A (2005) Bifurcation equations through multiple-scales analysis for a continuous model of a planar beam. Nonlinear Dyn 41(1–3):171–190
Luongo A, Di Egidio A (2006) Divergence, Hopf and double-zero bifurcations of a nonlinear planar beam. Comput Struct 84(24–25):1596–1605
Di Egidio A, Luongo A, Paolone A (2007) Linear and non-linear interactions between static and dynamic bifurcations of damped planar beams. Int J Non-Linear Mech 42(1):88–98
Luongo A, D’Annibale F (2013) Double zero bifurcation of non-linear viscoelastic beams under conservative and non-conservative loads. Int J Non-Linear Mech 55:128–139
Nayfeh AH (2008) Perturbation methods. Wiley, New York
Nayfeh AH, Mook DT (2008) Nonlinear oscillations. Wiley, New York
Benedettini F, Rega G, Alaggio R (1995) Non-linear oscillations of a four-degree-of-freedom model of a suspended cable under multiple internal resonance conditions. J Sound Vib 182(5):775–798
Luongo A, Paolone A (1999) On the reconstitution problem in the multiple time-scale method. Nonlinear Dyn 19(2):135–158
Bolotin VV (1964) The dynamic stability of elastic systems, volume 3 of Holden-Day series in mathematical physics. Holden-Day
Luongo A, D’Annibale F (2015) Linear and nonlinear damping effects on the stability of the Ziegler column. In: Belhaq M (ed) Springer proceedings in physics, vol 168. Springer, New York, pp 335–352
Luongo A, D’Annibale F (2016) Nonlinear hysteretic damping effects on the post-critical behavior of the visco-elastic Beck’s beam. Math Mech Solids. doi:10.1177/1081286516632381
Bellomo N, Preziosi L (1994) Modelling mathematical methods and scientific computation, vol 1. CRC Press, Boca Raton
Seydel R (2009) Practical bifurcation and stability analysis, vol 5. Springer, Berlin
Novak M (1972) Galloping oscillations of prismatic structures. J Eng Mech Div 98(1):27–46
Piccardo G, Pagnini LC, Tubino F (2015) Some research perspectives in galloping phenomena: critical conditions and post-critical behavior. Contin Mech Thermodyn 27(1–2):261–285
Xu G, Steindl A, Troger H (1992) Nonlinear stability analysis of a bogie of a low-platform wagon. Veh Syst Dyn 20(sup1):653–665
Zhang T, Wang W (2012) Hopf bifurcation and bistability of a nutrient–phytoplankton–zooplankton model. Appl Math Model 36(12):6225–6235
Luongo A, Zulli D (2012) Dynamic analysis of externally excited NES-controlled systems via a mixed Multiple Scale/Harmonic Balance algorithm. Nonlinear Dyn 70(3):2049–2061
Luongo A, Zulli D (2013) Mathematical models of beams and cables. Wiley, Hoboken
Acknowledgments
This work was granted by the Italian Ministry of University and Research (MIUR), under the PRIN10-11 program, Project N. 2010MBJK5B.
Author information
Authors and Affiliations
Corresponding author
Additional information
Dedicated to the memory of Francesco Benedettini.
Appendices
Appendix 1: Details on the Multiple Scale algorithm
This Appendix is devoted to furnish some detail on the perturbation algorithm presented in Sect. 3.
Once the generating solution of Eq. (11a), which is expressed by Eq. (12), is substituted in Eq. (11b), the following non-homogeneous problem is obtained:
Solvability condition of this latter, furnishes an equation for the unknown \({\mathrm {d}}_{1}A\) of the type of Eq. (13), namely:
where the apex H denotes the conjugate transpose, the normalization condition \(\mathbf {v}_{d}^{H}\mathbf {M}\mathbf {u}_{d}=1\) is accounted for, and \(\Omega _{d}:=\omega _{d}-i\left( \mathbf {v}_{d}^{H}\mathbf {C}\mathbf {u}_{d}\right) /2\) is introduced.
Once Eq. (19) is substituted in the \(\varepsilon\)-order problem (18), this latter reads:
where the following definitions hold:
The solution of the equation (20) is in the form of Eq. (14), where \(\mathbf {w}_{1}\), \(\mathbf {w}_{2}\) and \(\mathbf {w}_{3}\) are obtained by resolving the following algebraic problems:
In particular \(\mathbf {w}_{1}\) and \(\mathbf {w}_{2}\) are solutions of singular problems, normalized according to \(\mathbf {v}_{d}^{H}\mathbf {w}_{j}=0,\;j=1,2\), while \(\mathbf {w}_{3}\) is the solution of a non-singular problem.
Finally, Eq. (15) is obtained by straightforwardly extending the above discussed procedure to the \(\varepsilon ^{2}\)-order problem: Eqs. (12) and (14) are substituted in Eq. (11c) and solvability condition of this latter is enforced. However, this step of the algorithm entails cumbersome final expressions, which do not provide any further qualitative information on the perturbation solution; therefore, the relevant equations, which can be easily obtained through a software for symbolic calculation, are not reported here.
Appendix 2: Derivation of the equations of motion of the nonlinearly damped visco-elastic Beck’s beam
The relevant steps for deriving the equations of motion of the nonlinearly damped visco-elastic Beck’s beam are reported, in order to render the present paper self-contained. For further details the reader is referred to [39].
The beam is modeled as one-dimensional, internally constrained, polar continuum (see, e.g., [47]), embedded in the plane spanned by the unit vectors \(\bar{\mathbf {a}}_{x}\), \(\bar{\mathbf {a}}_{y}\). The rotation angle of the point P around the \(\bar{\mathbf {a}}_{z}\)-axis, namely \(\theta \left( s,t\right)\), maps the reference basis \(\left( \bar{\mathbf {a}}_{x},\bar{\mathbf {a}}_{y},\bar{\mathbf {a}}_{z}\right)\), attached to P, into the current one \(\left( \mathbf {a}_{x},\mathbf {a}_{y},\bar{\mathbf {a}}_{z}\right)\); \(\theta\) is taken as configuration variable. Moreover, the unshearability constraint, entails that \(\mathbf {a}_{x}\) is tangent to the beam axis.
The curvature of the beam is introduced as a measure of strain; it reads:
The inextensibility condition entails:
where u, v are scalar function which describe the longitudinal and transverse displacement of the beam axis, respectively. The geometrical boundary conditions at the clamp are:
The fields u, v are then rewritten as functions of \(\theta\): indeed, by integrating with respect to s Eq. (24), and by taking into account for Eq. (25), the following conditions hold:
being \(\hat{s}\) a dummy variable. The balance equations in the reference basis \(\left( \bar{\mathbf {a}}_{x},\bar{\mathbf {a}}_{y},\bar{\mathbf {a}}_{z}\right)\) read:
where R, S are the extrinsic component of the force-stress vector, M is the bending moment and \(p_{x},p_{y}\) are the external distributed loads. The mechanical boundary conditions at the free end are:
Then, by integrating Eqs. (27a, b) with respect to s, and by taking into account for Eqs. (28a, b), the extrinsic components are rewritten as:
When Eqs. (29) are substituted in Eq. (27c), this latter becomes:
Once the inertia forces and the external damping are introduced, i.e. \(p_{x}=-m\ddot{u},\,p_{y}=-m\ddot{v}-b\dot{v}\), and use of Eqs. (26) and (4) is made, Eq. (30) is transformed into:
being \(\check{s}\) a dummy variable. Equation (31) must be sided by the two remaining (i.e. not used) boundary conditions, namely Eqs. (25c) and (28c), which read:
Finally, by introducing the quantities (6) in Eqs. (31) and (32), Eqs. (5) are obtained (tilde removed).
Rights and permissions
About this article
Cite this article
Luongo, A., D’Annibale, F. & Ferretti, M. Hard loss of stability of Ziegler’s column with nonlinear damping. Meccanica 51, 2647–2663 (2016). https://doi.org/10.1007/s11012-016-0471-6
Received:
Accepted:
Published:
Issue Date:
DOI: https://doi.org/10.1007/s11012-016-0471-6