Eigenvalue extraction

Abaqus/Standard offers eigenvalue extraction methods that are computationally inexpensive and provide useful insight into the structure's dynamic behavior.

The following topics are discussed:

Related Topics
In Other Guides
Eigenvalue buckling prediction
Natural frequency extraction
Complex eigenvalue extraction

ProductsAbaqus/Standard

There are many important areas of structural analysis in which it is essential to be able to extract the eigenvalues of the system and, hence, obtain its natural frequencies of vibration or investigate possible bifurcations that may be associated with kinematic instabilities. For example, structural evaluation for seismic events is often based on linear analysis, using the structure's modes up to a limiting cutoff frequency, which is usually taken as 33 Hz (cycles/second). Once the modes are available, their orthogonality property allows the linear response of the structure to be constructed as the response of a number of single degree of freedom systems. This opens the way to several response evaluation methods that are computationally inexpensive and provide useful insight into the structure's dynamic behavior. Several such methods are provided in Abaqus/Standard and are described in the following sections.

The mathematical eigenvalue problem is a classical field of study, and much work has been devoted to providing eigenvalue extraction methods. Wilkinson's (1965) book provides an excellent compendium on the problem. The eigenvalue problems arising out of finite element models are a particular case: they involve large but usually narrowly banded matrices, and only a small number of eigenpairs are usually required. For many important cases the matrices are symmetric. The eigenvalue problem for natural modes of small vibration of a finite element model is

(μ2MMN+μCMN+KMN)ϕN=0

or, in classical matrix notation,

(1)(μ2[M]+μ[C]+[K]){ϕ}=0,

where [M] is the mass matrix, which is symmetric and positive definite in the problems of interest here; [C] is the damping matrix; [K] is the stiffness matrix, which may include large-displacement effects, such as “stress stiffening” (initial stress terms), and, therefore, may not be positive definite or symmetric; μ is the eigenvalue; and {ϕ} is the eigenvector—the mode of vibration. This equation is available immediately from a linear perturbation of the equilibrium equation of the system.

The eigensystem (Equation 1) in general will have complex eigenvalues and eigenvectors. This system can be symmetrized by assuming that [K] is symmetric and by neglecting [C] during eigenvalue extraction. The symmetrized system has real squared eigenvalues, μ2, and real eigenvectors only.

Typically, for symmetric eigenproblems we will also assume that [K] is positive semidefinite. In this case μ becomes an imaginary eigenvalue, μ=iω, where ω is the circular frequency, and the eigenvalue problem can be written as

(2)(-ω2[M]+[K]){ϕ}=0.

If the model contains hybrid elements, contact pairs, or contact elements, the system of equations contains Lagrange multipliers and the stiffness matrix [K] becomes indefinite. However, all the terms of the mass matrix corresponding to the Lagrange multipliers are equal to zero. Therefore, all the eigenvalues are imaginary, and the eigenvalue problem can still be written as Equation 2.

Abaqus provides eigenvalue extraction procedures for both symmetric and complex eigenproblems. For symmetrized eigenproblems Abaqus/Standard offers two approaches: Lanczos and subspace iteration methods. For complex eigenproblems the subspace projection method is used.