for direct-integration (nonlinear, implicit or explicit),
subspace-based direct-integration, direct-solution steady-state, and
subspace-based steady-state dynamic analysis; or
for mode-based (linear) dynamic analysis in
Abaqus/Standard.
In direct-integration dynamic analysis you very often define energy
dissipation mechanisms—dashpots, inelastic material behavior, etc.—as part of
the basic model. In such cases there is usually no need to introduce additional
damping: it is often unimportant compared to these other dissipative effects.
However, some models do not have such dissipation sources (an example is a
linear system with chattering contact, such as a pipeline in a seismic event).
In such cases it is often desirable to introduce some general damping.
Abaqus
provides “Rayleigh” damping for this purpose. It provides a convenient
abstraction to damp lower (mass-dependent) and higher (stiffness-dependent)
frequency range behavior.
Rayleigh damping can also be used in direct-solution steady-state dynamic
analyses and subspace-based steady-state dynamic analyses to get quantitatively
accurate results, especially near natural frequencies.
To define material Rayleigh damping, you specify two Rayleigh damping
factors:
for mass proportional damping and
for stiffness proportional damping. In general, damping is a material property
specified as part of the material definition. For the cases of rotary inertia,
point mass elements, and substructures, where there is no reference to a
material definition, the damping can be defined in conjunction with the
property references. Any mass proportional damping also applies to
nonstructural features (see
Nonstructural Mass Definition).
For a given mode i the fraction of critical
damping, ,
can be expressed in terms of the damping factors
and
as:
where
is the natural frequency at this mode. This equation implies that, generally
speaking, the mass proportional Rayleigh damping, ,
damps the lower frequencies and the stiffness proportional Rayleigh damping,
,
damps the higher frequencies.
Mass Proportional Damping
The
factor introduces damping forces caused by the absolute velocities of the model
and so simulates the idea of the model moving through a viscous “ether” (a
permeating, still fluid, so that any motion of any point in the model causes
damping). This damping factor defines mass proportional damping, in the sense
that it gives a damping contribution proportional to the mass matrix for an
element. If the element contains more than one material in
Abaqus/Standard,
the volume average value of
is used to multiply the element's mass matrix to define the damping
contribution from this term. If the element contains more than one material in
Abaqus/Explicit,
the mass average value of
is used to multiply the element's lumped mass matrix to define the damping
contribution from this term.
has units of (1/time).
Defining Variable Mass Proportional Damping
Mass proportional damping can vary during an analysis. In
Abaqus/Standard
you can define
as a tabular function of temperature. In
Abaqus/Explicit
you can define
as a tabular function of temperature and/or field variables.
Stiffness Proportional Damping
The
factor introduces damping proportional to the strain rate, which can be thought
of as damping associated with the material itself.
defines damping proportional to the elastic material stiffness. Since the model
may have quite general nonlinear response, the concept of “stiffness
proportional damping” must be generalized, since it is possible for the tangent
stiffness matrix to have negative eigenvalues (which would imply negative
damping). To overcome this problem,
is interpreted as defining viscous material damping in
Abaqus,
which creates an additional “damping stress,” ,
proportional to the total strain rate:
where
is the strain rate. For hyperelastic (Hyperelastic Behavior of Rubberlike Materials)
and hyperfoam (Hyperelastic Behavior in Elastomeric Foams)
materials
is defined as the elastic stiffness in the strain-free state. For all other
materials,
is the material's current elastic stiffness.
will be calculated based on the current temperature during the analysis.
This damping stress is added to the stress caused by the constitutive
response at the integration point when the dynamic equilibrium equations are
formed, but it is not included in the stress output. As a result, damping can
be introduced for any nonlinear case and provides standard Rayleigh damping for
linear cases; for a linear case stiffness proportional damping is exactly the
same as defining a damping matrix equal to
times the (elastic) material stiffness matrix. Other contributions to the
stiffness matrix (e.g., hourglass, transverse shear, and drill stiffnesses) are
not included when computing stiffness proportional damping.
has units of (time).
Defining Variable Stiffness Proportional Damping
Stiffness proportional damping can vary during an analysis. In
Abaqus/Standard
you can define
as a tabular function of temperature. In
Abaqus/Explicit
you can define
as a tabular function of temperature and/or field variables.
Band-Limited Damping in an Explicit Dynamic Analysis
For stiffness proportional damping, the fraction of critical damping is linearly
proportional to the response frequency. Therefore, the desired damping ratio is achieved
only at one target frequency. For practical purposes, it is useful to define the desired
damping ratio uniformly over a reasonable frequency range. Band-limited damping in Abaqus/Explicit provides this capability.
Unlike stiffness proportional damping, which creates an additional damping stress
proportional to the total strain rate, band-limited damping creates an additional damping
stress, . This additional damping stress is proportional to the rate of filtered
constitutive stress at the integration point:
where
is the actual damping ratio calculated based on the desired damping ratio
and the frequency range,
is the stress caused by the constitutive response at the integration point,
and
is the rate of linear transform , which is the low-pass filter operator.
The frequency range is defined by the low-frequency cutoff, , and the high-frequency cutoff, . The actual damping ratio varies with frequency and achieves the desired
damping ratio only within the frequency range. Outside the frequency range, the damping
ratio is not exactly zero. The accuracy to achieve the desired damping ratio depends on the
ratio of the high-frequency cutoff to the low-frequency cutoff, .
For example, if the desired damping ratio is , the normalized damping ratio is . Figure 1 shows the normalized damping ratio as a function of frequency for
two cases: the red dotted line for the range with , and the blue solid line for the range with .
It is well known that band-limited damping has a significant impact on the dynamic
stiffness of the structure. The changes in the dynamic stiffness of the structure depend on
the damping ratio and the frequency range. It increases the natural frequency of each mode,
and the percentage change of the damped frequency could be large. For example, if , the maximum percentage change of the damped frequency to the natural
frequency could reach approximately 1.65% (increased) with . Compared to stiffness proportional damping, the percentage change of the
damped frequency is only 0.02% (reduced). For the fixed , this percentage change is approximately linearly proportional to the
damping ratio. Therefore, in practical applications, it is recommended that you use a low
value for the damping ratio.
Similar to stiffness proportional damping, the band-limited damping stress is added to the
stress caused by the constitutive response at the integration point when the dynamic
equilibrium equations are formed, but it is not included in the stress output.
Defining Variable Band-Limited Damping
You can define the desired damping ratio, , as a tabular function of temperature and/or field variables to define
band-limited damping.
Structural Damping
Structural damping assumes that the damping forces are proportional to the
forces caused by stressing of the structure and are opposed to the velocity.
Therefore, this form of damping can be used only when the displacement and
velocity are exactly 90° out of phase. Structural damping is best suited for
frequency domain dynamic procedures (see
Damping in Modal Superposition Procedures
below). The damping forces are then
where
are the damping forces, ,
s is the user-defined structural damping factor, and
are the forces caused by stressing of the structure. The damping forces due to
structural damping are intended to represent frictional effects (as distinct
from viscous effects). Thus, structural damping is suggested for models
involving materials that exhibit frictional behavior or where local frictional
effects are present throughout the model, such as dry rubbing of joints in a
multi-link structure.
Structural damping can be added to the model as mechanical dampers such as
connector damping or as a complex stiffness on spring elements.
Structural damping can be used in steady-state dynamic procedures that allow
for nondiagonal damping.
Defining Variable Stiffness Proportional Structural Damping in Abaqus/Standard
Stiffness proportional structural damping can vary during an
Abaqus/Standard
analysis. You can define
as a function of temperature.
Artificial Damping in Direct-Integration Dynamic Analysis
In
Abaqus/Standard
the operators used for implicit direct time integration introduce some
artificial damping in addition to Rayleigh damping. Damping associated with the
Hilber-Hughes-Taylor and hybrid operators is usually controlled by the
Hilber-Hughes-Taylor parameter ,
which is not the same as the
parameter controlling the mass proportional part of Rayleigh damping. The
and
parameters of the Hilber-Hughes-Taylor and hybrid operators also affect
numerical damping. The ,
,
and
parameters are not available for the backward Euler operator. See
Implicit Dynamic Analysis Using Direct Integration
for more information about this other form of damping.
Artificial Damping in Explicit Dynamic Analysis
Rayleigh damping is meant to reflect physical damping in the actual
material. In
Abaqus/Explicit
a small amount of numerical damping is introduced by default in the form of
bulk viscosity to control high frequency oscillations; see
Explicit Dynamic Analysis
for more information about this other form of damping.
Effects of Damping on the Stable Time Increment in Abaqus/Explicit
As the fraction of critical damping for the highest mode
()
increases, the stable time increment for
Abaqus/Explicit
decreases according to the equation
where (by substituting ,
the frequency of the highest mode, into the equation for
given previously)
These equations indicate a tendency for stiffness proportional damping to
have a greater effect on the stable time increment than mass proportional
damping.
To illustrate the effect that damping has on the stable time increment,
consider a cantilever in bending modeled with continuum elements. The lowest
frequency is
1 rad/sec, while for the particular mesh chosen, the highest frequency is
1000 rad/sec. The lowest mode in this problem corresponds to the cantilever in
bending, and the highest frequency is related to the dilation of a single
element.
With no damping the stable time increment is
If we use stiffness proportional damping to create 1% of critical damping in
the lowest mode, the damping factor is given by
This corresponds to a critical damping factor in the highest mode of
The stable time increment with damping is, thus, reduced by a factor of
and becomes
Thus, introducing 1% critical damping in the lowest mode reduces the stable
time increment by a factor of twenty.
However, if we use mass proportional damping to damp out the lowest mode
with 1% of critical damping, the damping factor is given by
which corresponds to a critical damping factor in the highest mode of
The stable time increment with damping is reduced by a factor of
which is almost negligible.
This example demonstrates that it is generally preferable to damp out low-frequency response with
mass proportional damping rather than stiffness proportional damping. However, mass
proportional damping can significantly affect rigid body motion, so large is often undesirable. To avoid a dramatic drop in the stable time
increment, the stiffness proportional damping factor, , should be less than or of the same order of magnitude as the initial
stable time increment without damping. With , the stable time increment is reduced by about 52%.
The above equation to calculate the stable time increment with critical damping is not
suitable for band-limited damping. Because band-limited damping affects the dynamic
stiffness of the structure, the stable time increment could have a dramatic drop if the
damping ratio, , or the ratio of high-frequency cutoff to low-frequency cutoff, , is large. Figure 2 illustrates the scale factor for the stable time increment with
band-limited damping. The red dotted line shows the scale factor as a function of with , and the blue solid line shows the scale factor as a function of with . For comparison, with stiffness proportional damping, the scale factor is
0.9801 when and is 0.9049 when , respectively.
Damping in Modal Superposition Procedures
Damping can be specified as part of the step definition for modal
superposition procedures.
Damping in a Linear Dynamic Analysis
describes the availability of damping types, which depends on the procedure
type and the architecture used to perform the analysis, and provides details on
the following types of damping:
Viscous modal damping (Rayleigh damping and fraction of critical
damping)
Structural modal damping
Composite modal damping
Material Options
The
factor applies to all elements that use a linear elastic material definition
(Linear Elastic Behavior)
and to
Abaqus/Standard
beam and shell elements that use general sections. In the latter case, if a
nonlinear beam section definition is provided, the
factor is multiplied by the slope of the force-strain (or moment-curvature)
relationship at zero strain or curvature. In the case of equation of state
materials, the
factor can apply only to elements that use a tabulated equation of state
material definition, a linear
equation of state material definition, or a equation of state material definition. In addition, the
factor applies to all
Abaqus/Explicit
elements that use a hyperelastic material definition (Hyperelastic Behavior of Rubberlike Materials),
a hyperfoam material definition (Hyperelastic Behavior in Elastomeric Foams),
or general shell sections (Using a General Shell Section to Define the Section Behavior).
In the case of a no tension elastic material the
factor is not used in tension, while for a no compression elastic material the
factor is not used in compression (see
No Compression or No Tension).
In other words, these modified elasticity models exhibit damping only when they
have stiffness.
Elements
The factor is applied to all elements that have mass including point mass
elements (discrete DASHPOTA elements in each
global direction, each with one node fixed, can also be used to introduce this type of
damping). For point mass and rotary inertia elements mass proportional or composite modal
damping are defined as part of the point mass or rotary inertia definitions (Point Masses and Rotary Inertia).
The factor is not available for spring elements: discrete dashpot elements
should be used in parallel with spring elements instead.
The factor is also not applied to the transverse shear terms in Abaqus/Standard beams and shells.
The hybrid element stiffness matrix formulation is different than the corresponding
non-hybrid formulation; therefore, the stiffness proportional damping is different for the
same value of the factor in nonlinear dynamic analysis. In linear analyses Abaqus/Standard imposes equivalent stiffness proportional damping for hybrid and non-hybrid elements.
In Abaqus/Standard composite modal damping cannot be used with or within substructures. Rayleigh damping can
be introduced for substructures. When Rayleigh damping is used within a substructure, and are averaged over the substructure to define single values of and for the substructure. These are weighted averages, using the mass as the
weighting factor for and the volume as the weighting factor for . These averaged damping values can be superseded by providing them
directly in a second damping definition. See Using Substructures.
References
Huang, Y., R. Sturt, and M. Willford, “A Damping Model for Nonlinear Dynamic Analysis Providing Uniform Damping Over a Frequency Range,” Computer & Structures, vol. 212, pp. 101–109, 2019.