On the natural frequencies of helical compression springs
Introduction
Helical springs represent a fundamental component of engineering design, and quantification of their resonant frequencies has been an active area of research since at least the work of Michell [1] in 1890. The majority of studies in this area have focused on helical springs without externally applied loads (e.g. [2], [3], [4], [5], [6], [7], [8], [9]); the remainder have dealt mainly with the case of purely axial compression, which is perhaps the most common type of loading in practical applications.
The first and most comprehensive theoretical analysis of the effect of static axial compression on the natural frequencies of helical springs was conducted by Haringx [10], in which the spring is idealized as an elastic prismatic rod with rigidities corresponding to those of unclosed circular rings. In our previous, closely related work on buckling of helical springs under compression and/or torsion [11], [12], [13], [14], we have verified that his rod-model approximation is indeed appropriate for springs with sufficiently large numbers of turns. Given this simplified representation of the spring, Haringx obtained analytically a somewhat complicated set of transcendental equations for the natural frequencies corresponding to transverse (symmetric/asymmetric) modes of vibration amplitude, and he solved these equations by graphical means (around 1947) to produce a single comprehensive design chart for the fundamental frequency. This work, together with another pioneering study on the lateral rigidity of springs, constitutes the second in a series of six ingenious papers by Haringx related to the application of springs for vibration-free mountings.
More recent investigations have sought to compute the resonant frequencies and/or stability of a compressed helical spring treated as a curved and twisted rod under load. Mottershead [15] and Pearson [16] independently obtained different governing equations by summing forces and moments on a perturbed element of a helical compression spring, but their equations do not agree with the preceding rigorous treatise on this general subject in the textbook by Wempner [17], and one may verify that their equations do not reduce correctly to those for simpler rods; discrepancies in their results for buckling of helical compression springs are detailed in Ref. [11]. Most recently, Tabarrok and Xiong [18], [19], [20] derived a finite element formulation for the vibration and buckling of curved and twisted rods under load, the sample results of which agreed well with our previous work on buckling of compression springs (see Ref. [14]).
In this paper, we incorporate inertial terms into our prior formulation for buckling of helical springs, and investigate the effect of static axial compression upon the resonant frequencies. In the following section, we state the equations governing the initial deflections and the small-amplitude, linearized vibrations of a helical compression spring, as outlined by Wahl [21] for the static deflection of helices, and by Wempner [17] for the dynamical equations of curved and twisted rods under load. Analogous to our earlier studies, the resonant frequencies in the loaded state are computed using the transfer matrix method detailed in Ref. [16], and the corresponding initial configurations are determined to produce frequency design charts. This study represents primarily the first detailed examination of the fundamental natural frequencies of helical springs, under static axial load with clamped ends, since the pioneering work by Haringx [10] using the rod-model of a helix, and with our formulation we are able to investigate the heretofore untreated effect of low numbers of turns.
Section snippets
Governing equations
A circular-bar helical spring with helix angle α0, coil radius R0, wire radius r, and number of turns n0 prior to any loading, is subjected to a static axial compressive force P, and a section of the spring in the loaded state is depicted in Fig. 1. The compressed spring, with helix angle α, coil radius R, and number of turns n, is described conveniently by a Frenet trihedral , representing the normal, binormal, and tangent unit vectors, respectively. These vectors obey the
Results
In Fig. 2, we summarize the behavior of the lowest resonant frequency obtained from our model of a helical compression spring with an initial number of turns of n0=30. The lines indicate our numerical results for ratios of initial axial length to initial coil diameter (l0/D0) in the range from 1 to 10. This figure essentially reproduces Fig. 38 of Haringx [10], who treated the spring as an elastic prismatic rod with rigidities corresponding to those of unclosed circular rings. He determined
Discussion and concluding remarks
Haringx's rod-model of the helix relies on the fact that whenever the vibration amplitudes of a particular mode of vibration vary with axial length over a length scale that is much larger than the length of a single coil, then the response of the spring may be described by an equivalent rod with effective rigidities to bending, shearing, and compression [10]. Haringx's model uses as inputs the effective rigidities corresponding to unclosed circular rings, restricting the applicability of his
Acknowledgements
LEB acknowledges support from United States Department of Energy Grant DE-FG02-88ER25053. WLC acknowledges support from the Natural Sciences and Engineering Research Council of Canada.
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