
Finite Element Methods. The most numerous programs are classed as finite ele-
ment or lumped-parameter programs, as described in detail in Chap. 28, Part II. In a
lumped-parameter program, the structure to be analyzed is represented in a model
as a number of point masses (or inertias) connected by massless, spring-like ele-
ments. The points at which these elements are connected, and at which a mass may
or may not be located, are the nodes of the system. Each node may have up to six
degrees-of-freedom at the option of the analyst.The size of the model is determined
by the sum of the degrees-of-freedom for which the mass or inertia is nonzero. The
number of natural frequencies and normal modes that may be computed is equal to
the number of dynamic degrees-of-freedom. However, the number of frequencies
and modes that reliably represent the physical structure is generally only a fraction
of the number that can be computed. Each program is limited in capacity to some
combination of dynamic and zero mass degrees-of-freedom. The spring-like ele-
ments are chosen to represent the stiffness of the physical structure between the
selected nodes and generally may be represented by springs, beams, or plates of
specified shapes. The material properties, geometric properties, and boundary con-
ditions for each element are selected by the analyst.
In the more general finite element programs, the spring-like elements are not
necessarily massless, but may have distributed mass properties. In addition, lumped
masses may be used at any of the nodes of the system. The equations of motion of
the finite element model can be expressed in matrix form and solved by the methods
described in Chap. 28, Part I. Regardless of the computational algorithms employed,
the program computes the set of natural frequencies and orthogonal mode shapes of
the finite-dimensional system. These modes and frequencies are sorted for future
use in computing the response of the system to a specified excitation. For the latter
computations, a damping factor must be specified. Depending on the programs, this
damping factor may have to be equal for all modes, or it may have a selected value
for each mode.
Component Mode Synthesis. The method of modeling described above leads to
the creation of models with a very large number of degrees-of-freedom compared
with the number of modes and frequencies actually of interest. Not only is this
expensive, but it rapidly exceeds the capacity of many programs. To overcome these
problems, component mode synthesis
8,9
techniques have been developed. Instead of
developing a model of an entire physical system, several models are developed, each
representing a distinct identifiable region of the total structure and within the capac-
ity of the computer program. The modes and frequencies of interest in each of these
models are computed independently. Where actual hardware exists for some or all
components, modes and frequencies from an experimental modal analysis may be
used (see Chap. 21).A model of the entire structure is then obtained by joining these
several models, using the component model synthesis technique. This model retains
the essential features of each substructure model, and thus the entire structure, with
a greatly reduced number of degrees-of-freedom.
Reduction of Model Complexity. Companion methods developed to reduce the
cost of analysis, permit the joining of several substructure models, and provide for
correlation with experimental results are described under reduction techniques in
Chap. 28, Part II. For cost reduction and joining of substructures, the objective is to
reduce the mass and stiffness matrices to the minimum size consistent with retaining
the modes and frequencies of interest, as well as other dynamic characteristics such
as base impedance. For test/analysis correlation, the objective is to match the
degrees-of-freedom of the test. It should be noted, however, that the Guyan reduc-
tion method (see Chap. 28, Part II) yields a mass matrix which is nondiagonal and
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