scholarly journals Almost Classically Damped Continuous Linear Systems

1998 ◽  
Vol 65 (4) ◽  
pp. 1022-1031 ◽  
Author(s):  
S. Natsiavas ◽  
J. L. Beck
Keyword(s):  
Boundary Conditions ◽  
Normal Modes ◽  
Mode Shapes ◽  
Continuous Linear ◽  
Perturbation Expansions ◽  
Field Equations ◽  
Regular Perturbation ◽  
Modes Of Vibration ◽  
Proper Splitting ◽  
Damped Systems

The dynamic response of a general class of continuous linear vibrating systems is analyzed which possess damping properties close to those resulting in classical (uncoupled) normal modes. First, conditions are given for the existence of classical modes of vibration in a continuous linear system, with special attention being paid to the boundary conditions. Regular perturbation expansions in terms of undamped modeshapes are then utilized for analyzing the eigenproblem as well as the vibration response of almost classically damped systems. The analysis is based on a proper splitting of the damping operators in both the field equations and the boundary conditions. The main advantage of this approach is that it allows application of standard modal analysis methodologies so that the problem is reduced to that of finding the frequencies and mode shapes of the corresponding undamped system. The approach is illustrated by two simple examples involving rod and beam vibrations.

Natural Frequencies and Normal Modes of a Spinning Timoshenko Beam With General Boundary Conditions

1992 ◽  
Vol 59 (2S) ◽  
pp. S197-S204 ◽  
Author(s):  
Jean Wu-Zheng Zu ◽  
Ray P. S. Han
Keyword(s):  
Boundary Conditions ◽  
Mode Shape ◽  
Timoshenko Beam ◽  
Natural Frequencies ◽  
Normal Modes ◽  
Single Mode ◽  
Mode Shapes ◽  
Simulation Studies ◽  
Classical Boundary ◽  
First Time

A free flexural vibrations of a spinning, finite Timoshenko beam for the six classical boundary conditions are analytically solved and presented for the first time. Expressions for computing natural frequencies and mode shapes are given. Numerical simulation studies show that the simply-supported beam possesses very peculiar free vibration characteristics: There exist two sets of natural frequencies corresponding to each mode shape, and the forward and backward precession mode shapes of each set coincide identically. These phenomena are not observed in beams with the other five types of boundary conditions. In these cases, the forward and backward precessions are different, implying that each natural frequency corresponds to a single mode shape.

Free Vibration of Continuous Skin-Stringer Panels

1960 ◽  
Vol 27 (4) ◽  
pp. 669-676 ◽  
Author(s):  
Y. K. Lin
Keyword(s):  
Free Vibration ◽  
Boundary Conditions ◽  
Natural Frequencies ◽  
Normal Modes ◽  
Time Dependent ◽  
Experimental Measurements ◽  
Structural Configuration ◽  
Modes Of Vibration ◽  
Fuselage Skin

The determination of the natural frequencies and normal modes of vibration for continuous panels, representing more or less typical fuselage skin-panel construction for modern airplanes, is discussed in this paper. The time-dependent boundary conditions at the supporting stringers are considered. A numerical example is presented, and analytical results for a particular structural configuration agree favorably with available experimental measurements.

scholarly journals Transverse Vibrations of Clamped and Simply-Supported Circular Plates with Two Dimensional Thickness Variation

2012 ◽  
Vol 19 (3) ◽  
pp. 273-285 ◽  
Author(s):  
N. Bhardwaj ◽  
A.P. Gupta ◽  
K.K. Choong ◽  
C.M. Wang ◽  
Hiroshi Ohmori
Keyword(s):  
Ritz Method ◽  
Normal Modes ◽  
Mode Shapes ◽  
Thickness Variation ◽  
Two Dimensional ◽  
Circular Plates ◽  
Simply Supported ◽  
Modes Of Vibration ◽  
Dimensional Boundary ◽  
Special Case

Two dimensional boundary characteristic orthonormal polynomials are used in the Ritz method for the vibration analysis of clamped and simply-supported circular plates of varying thickness. The thickness variation in the radial direction is linear whereas in the circumferential direction the thickness varies according to coskθ, wherekis an integer. In order to verify the validity, convergence and accuracy of the results, comparison studies are made against existing results for the special case of linearly tapered thickness plates. Variations in frequencies for the first six normal modes of vibration and mode shapes for various taper parameters are presented.

Global Parametrization of the Invariant Manifold Defining Nonlinear Normal Modes Using the Koopman Operator

2015 ◽  
Author(s):  
Giuseppe I. Cirillo ◽  
Alexandre Mauroy ◽  
Ludovic Renson ◽  
Gaëtan Kerschen ◽  
Rodolphe Sepulchre
Keyword(s):  
Invariant Manifold ◽  
Normal Modes ◽  
Geometric Approach ◽  
Nonlinear Normal Modes ◽  
Koopman Operator ◽  
The Past ◽  
Modes Of Vibration ◽  
Nonlinear Normal ◽  
Damped Systems

Nonlinear normal modes of vibration have been the focus of many studies during the past years and different characterizations of them have been proposed. The present work focuses on damped systems, and considers nonlinear normal mode motions as trajectories lying on an invariant manifold, following the geometric approach of Shaw and Pierre. We provide a novel characterization of the invariant manifold, that rests on the spectral theory of the Koopman operator. A main advantage of the proposed approach is a global parametrization of the manifold, which avoids folding issues arising with the use of displacement-velocity coordinates.

Effects of Gears, Bearings, and Housings on Gearbox Transmission Shafting Resonances

2010 ◽  
Author(s):  
Stephen A. Hambric ◽  
Micah R. Shepherd ◽  
Robert L. Campbell
Keyword(s):  
Boundary Conditions ◽  
Fundamental Mode ◽  
Spur Gear ◽  
Single Stage ◽  
Mode Shapes ◽  
Gear Noise ◽  
Input And Output ◽  
Resonance Frequencies ◽  
Modes Of Vibration ◽  
Similar Mode

Gear noise, comprised of tones centered around gear meshing frequencies, is transmitted through driveshafts, bearings, and transmission housings. Gear noise transmission is amplified, sometimes strongly, by modes of vibration of the shafting. The shafts of the input and output gears vibrate like beams at low to mid frequencies. The resonance frequencies and vibration patterns of these beam-like modes depend strongly on the shaft boundary conditions, which in turn depend on the impedances of the bearings, and of the transmission housing. In this paper, we present simulated and measured modes of the input and output shafts of a single stage spur gear system mounted in a rectangular metal gearbox. The impedances of the gears, bearings, and housing are added in sequence and the effects on the fundamental mode shapes and frequencies are shown. The bearing impedances have the largest effects on the shafting modes, increasing the resonance frequencies significantly, along with spreading the frequencies of similar mode types. Including the housing impedances at the bearing locations reduces slightly the spread of shaft mode frequencies.

Natural Frequencies and Normal Modes for Externally Damped Spinning Timoshenko Beams With General Boundary Conditions

1998 ◽  
Vol 65 (3) ◽  
pp. 770-772 ◽  
Author(s):  
J. W. Zu ◽  
J. Melanson
Keyword(s):  
Boundary Conditions ◽  
Natural Frequencies ◽  
Dimensional Space ◽  
Three Dimensional ◽  
Normal Modes ◽  
General Boundary ◽  
Mode Shapes ◽  
General Boundary Conditions ◽  
Timoshenko Beams ◽  
Classical Boundary

Vibration analysis of externally damped spinning Timoshenko beams with general boundary conditions is performed analytically. Exact solutions for natural frequencies and normal modes for the six classical boundary conditions are derived for the first time. In the numerical simulations, the trend between the complex frequencies and the damping coefficient is investigated, and complex mode shapes are presented in three-dimensional space.

Torsional Vibrations of Beams of Thin-Walled Open Section

1954 ◽  
Vol 21 (4) ◽  
pp. 381-387
Author(s):  
J. M. Gere
Keyword(s):  
Cross Section ◽  
Normal Modes ◽  
Mode Shapes ◽  
Graphical Form ◽  
Torsional Vibrations ◽  
End Conditions ◽  
Modes Of Vibration ◽  
Thin Walled ◽  
Limiting Case ◽  
Open Cross Section

Abstract This analysis deals with the free torsional vibrations of bars of thin-walled open cross section for which the shear center and centroid coincide. Such sections include I-beams and Z-sections. The differential equation for torsional vibrations is derived and includes the effect of warping of the cross section. The effect of warping on the frequency of vibration and the shapes of the normal modes of vibration are determined for bars of single span with various end conditions. For a simply supported bar, a formula for the principal torsional frequencies and an expression for mode shape are derived. For other conditions of support, the frequency equations are derived and their solutions presented in graphical form. From these graphs the frequencies of vibration and the mode shapes may be obtained directly. The case of a cross section which does not warp is a limiting case of the general problem. For such shapes (for example, a cross-shaped or cruciform section) the formulas for torsional frequencies and modes of vibration are quite simple. These formulas also are valid for a circular shaft and may be used approximately for other solid sections.

scholarly journals Preparation and the Microwave and Infrared Spectra of Vinyl Ketene

1979 ◽  
Vol 34 (11) ◽  
pp. 1269-1274 ◽  
Author(s):  
Erik Bjarnov
Keyword(s):  
Dipole Moment ◽  
Gas Phase ◽  
Infrared Spectra ◽  
Room Temperature ◽  
Normal Modes ◽  
Spectroscopic Constants ◽  
Electrical Dipole ◽  
Electrical Dipole Moment ◽  
Vacuum Pyrolysis ◽  
Modes Of Vibration

Vinyl ketene (1,3-butadiene-1-one) has been synthesized by vacuum pyrolysis of 3-butenoic 2-butenoic anhydride. The microwave and infrared spectra of vinyl ketene in the gas phase at room temperature have been studied. The trans-rotamer has been identified, and the spectroscopic constants were found to be Ã= 39571(48) MHz, B̃ = 2392.9252(28) MHz, C̃ = 2256.0089(28) MHz, ⊿j = 0.414(31) kHz, and ⊿JK = - 34.694(92) kHz. The electrical dipole moment was found to be 0.987(23) D with μa = 0.865(14) D and μb = 0.475(41) D. A tentative assignment has been made for 17 of the 21 normal modes of vibration

Normal modes of vibration of a model peptide adopting the C7 C5 structure

2009 ◽  
Vol 24 (6) ◽  
pp. 543-552 ◽  
Author(s):  
P. LAGANT ◽  
G. VERGOTEN ◽  
G. FLEURY ◽  
M.H. LOUCHEUX-LEFEBVRE
Keyword(s):  
Normal Modes ◽  
Model Peptide ◽  
Modes Of Vibration

Free Bending Vibrations of a Centrally Bonded Symmetric Double Lap Joint (or Symmetric Double Doubler Joint) With a Gap in Mindlin Plates or Panels

2007 ◽  
Author(s):  
U. Yuceoglu ◽  
O. Gu¨vendik ◽  
V. O¨zerciyes
Keyword(s):  
Boundary Conditions ◽  
Natural Frequencies ◽  
Mode Shapes ◽  
Shear Stresses ◽  
Lap Joint ◽  
Bending Vibrations ◽  
Joint System ◽  
Adhesive Layers ◽  
Bonded Joint ◽  
Free Bending

In this present study, the “Free Bending Vibrations of a Centrally Bonded Symmetric Double Lap Joint (or Symmetric Double Doubler Joint) with a Gap in Mindlin Plates or Panels” are theoretically analyzed and are numerically solved in some detail. The “plate adherends” and the upper and lower “doubler plates” of the “Bonded Joint” system are considered as dissimilar, orthotropic “Mindlin Plates” joined through the dissimilar upper and lower very thin adhesive layers. There is a symmetrically and centrally located “Gap” between the “plate adherends” of the joint system. In the “adherends” and the “doublers” of the “Bonded Joint” assembly, the transverse shear deformations and the transverse and rotary moments of inertia are included in the analysis. The relatively very thin adhesive layers are assumed to be linearly elastic continua with transverse normal and shear stresses. The “damping effects” in the entire “Bonded Joint” system are neglected. The sets of the dynamic “Mindlin Plate” equations of the “plate adherends”, the “double doubler plates” and the thin adhesive layers are combined together with the orthotropic stress resultant-displacement expressions in a “special form”. This system of equations, after some further manipulations, is eventually reduced to a set of the “Governing System of the First Order Ordinary Differential Equations” in terms of the “state vectors” of the problem. Hence, the final set of the aforementioned “Governing Systems of Equations” together with the “Continuity Conditions” and the “Boundary conditions” facilitate the present solution procedure. This is the “Modified Transfer Matrix Method (MTMM) (with Interpolation Polynomials). The present theoretical formulation and the method of solution are applied to a typical “Bonded Symmetric Double Lap Joint (or Symmetric Double Doubler Joint) with a Gap”. The effects of the relatively stiff (or “hard”) and the relatively flexible (or “soft”) adhesive properties, on the natural frequencies and mode shapes are considered in detail. The very interesting mode shapes with their dimensionless natural frequencies are presented for various sets of boundary conditions. Also, several parametric studies of the dimensionless natural frequencies of the entire system are graphically presented. From the numerical results obtained, some important conclusions are drawn for the “Bonded Joint System” studied here.

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