model reduction techniques
DESCRIPTION
A summary of model reduction techniques in MB dynamics, references at the endTRANSCRIPT
Presentation for the course in Multibody Dynamics
Flavia Buonanno
February 2012
• Techniques for the efficient analysis and simulation of large models, reducing
computational requirements without damaging the dynamical properties of the model �
suitable with Finite Elements spatial discretization
• Departing from the linear equation of motion
• The idea is to find a lower dimension space
• Such that the state vector can be approximated as
• The projection versus the lower dimension yields
• With the reduced
system matrices
• The reduced model mass and stiffness matrices can be derived energetically by
substituting the coordinate change into kinectic and potential energy expressions of the
original model
• The transformation T will take different forms depending on the transformation
technique utilized
The equation of
motion for the
undamped system
can be partitioned
Where:
• Main assumption: for the lowest frequency modes, inertia forces on the slave dof are much
less important than the elastic forces transmitted by the master dofs � slave dofs are
assumed to move quasi-statically wrt the motion of the master dofs
• In order to obtain a relationship between xs and xm, inertia terms are neglected (static
nature) and it is assumed that no force is applied on the slave dofs
• From the lower partition:
Expressing the state vector of the full
model in terms of the master dof, the
transformation matrix is obtained as:
� Is a good approximation (exact for static analyses) for the low eigenvalue
spectrum of a FE structure, the quality of the eigenvalue approximation
decreases as the mode number increases
� In general, when high frequency motion is considered, the influence of the inertia
terms is significant � the basic assumption of static reduction is contradicted
and the method becomes inaccurate.
� The quality of the eigenvalue approximations is highly dependent on the location
of the preserved dof (master)
� The mass of the reduced system is not effectively preserved and generally
reduced model frequencies are higher than those of the original full space model
• The structure of the transformation matrix is “similar” to the Guyan reduction, with the
difference that, this time, the inertia information of the model is considered
• Applying the Laplace transformation to the equation of motion of the undamped system,
we obtain the description in frequency domain:
• The system can be rewritten and partitioned in master and slave as in the Guyan
reduction, with
for undamped system
B(w) is called the dynamic
stiffness matrix
• Assuming again that no forces are applied
on the slave dof, and following the same
steps as for the static case, the
transformation matrix is obtained
� For w=0, it reduces to the Guyan reduction
� With respect to its static counterpart, it is a better candidate for approximating
high frequency motion, though, T depends of the choice of an initial frequency
� As the transformation depends on w, the choice of this value should not be
conducted randomly, but it should constitute a value out of the model’s
frequency spectrum (the free vibration equation with the dynamic stiffness
matrix involved is not satisfied)
� The accuracy of the method is limited to a frequency range around the initial
value selected for initializing the method � has high accuracy for systems under
periodical excitations
• As its name indicates, this method is an effort for improving the already presented
reduction methods, by including the inertia terms of the original model in the definition
of the transformation matrix
• From the dynamic equation of a
free vibrated Guyan reduced model:
• From the definition of the
Guyan transformation:
• Both relations are substituted into
the equation for the lower partition
• For obtaining the following transformation matrix
• The transformation obtained can be expanded,
evidentiating its direct dependence on the static
transformation matrix obtained from Guyan
• Taking the Guyan condensation as basis, the static information is perturbed by introducing
the inertia terms as pseudo-static forces
• The generated reduced model capture the dynamics of the original model better than the
Guyan condensation, as expected from the introduction of a summand (that adds
information to the static matrix) containing the inertia info from the original model
• A dynamic counterpart can be found by taking as basis the dynamic reduction, and, with
analogous passages, we obtain the similar transformation matrix for the dynamic variant:
• The IRS variants shown rely on the reduced models of Guyan or dynamic condensation.
Once the transformation is computed, an improved estimate for the transformation matrix
can be obtained by applying an iteration scheme given by:
• Also known as substructuring � division of a structure into components
• Reduced-order models of the components are obtained and then assembled into a
reduced order model of the entire structure
• The individual substructure models are transformed from physical to component modal
coordinates using a set of chosen basis functions � normal modes (eigenproblem),
constraint modes, attachment modes
• One of the most diffused CMS methods in structural analysis is the Craig – Bampton
Method, based on normal modes and constraint modes
• Primary uses of dynamic substructuring:
- Couple reduced order models of moderately complex structures
- Test verification of FE models of components
- Implement computation of dynamics of very large FE models
• The physical dof’s for a singular component can be partitioned into a set of interior dofs
and a set of interface or boundary dof’s :
Free interface
Fixed interface
Fixed – Interface Normal Modes:
Mass normalised eigenvectors
of the component with the
interface dofs fixed, which
form the columns of the fixed
interface modal matrix ��; a
subset of k modes are kept
Constraint Modes:
Static displacement of the
component due to a unit
displacement of one interface dof
with all other interface dofs fixed,
where �� is a matrix of
displacements of the interior dofs
and Ψ� is the constraint mode matrix
• CM space includes both fixed interface normal modes and static constraint modes
The interior physical coordinates �� are
transformed into the fixed interface modal
coordinates ��, and the physical interface
coordinates �� are retained, but denoted
as constraint coordinates ��
• After transformation, the equation of motion for the generic component remains:
• The component modal mass and stiffness matrices
Where:
�� ��� � constraint modal mass and
stiffness matrices for component
�� � coupling matrix
�� � diagonal matrix of kept modal
eigenvalues
• For the synthesis of two components and �, compatibility of
displacements at the boundary is given by
• Imposing the coupling conditions through a transformation matrix,
the assembled stiffness and mass matrixes are obtained
• Most applications of CMS employ one from two approaches: - Constraint mode: employ constraint and fixed interface normal modes (Hurty and Craig-Bamptom)
- Attachment mode: attachment and free-interface normal modes (McNeal and Rubin)
• Component models based on the used of fixed-interface plus constraint modes are
essentially «superelements» � all physical boundary coordinates are retained as
independent generalized coordinates, greatly facilitating component coupling
• CMS generates reduced order models which capture very well the dynamics of the
original model with relatively few component modes, no wonder is implemented as a
standard and most reliable reduction algorithm in several FE packages
• The components couple in a quite straightforward way, and the sparsity patterns of the
resulting system matrices allow for faster computation times
• The constrained modes embodying the quasi-static effect of high-level normal modes
can compensate the error caused by normal modes truncation at certain extents and
accelerate convergence. The reduced model depends on the sum of the normal and
constrained modes. The more dof at the interface, the more accurate the description of
structural motion.
• The basis is the modal matrix of the discretized FE structure, Φ��� where n is the
dimension of the model, and q the number of computed eigenvectors
• By making use of the modal transformation
(relation between state vector and modal
coordinates) and partitioning, it holds
• From the first line of the equation, the modal coordinates can be expressed in terms of
the master dof, by using the pseudo-inverse definition
• Then, by substituting into the initial modal transformation, the SEREP transformation
matrix is obtained
• Due to the nature of the transformation, an analytical expression for the reduced mass
and stiffness matrices can be derived The reduced system matrices can be computed
directly by using only the eigenvalue data
• SEREP exactly preserves all the modes selected from the original model, and the
reduction’s quality depends on the selection of the full eigenvectors
• It has two main drawbacks:
- Its application is only feasible if the modal matrix of the original model is
available: sparse algebra techniques or lumped mass approximation can be used
to overcome this problem
- The system is truly equivalent when m=q. Different choices can be made, but
careful must be taken.
• The reduction methods presented so far are based on the selection of master and slave dofs,
where
- master are kept after reduction and therefore constitute the dof of the reduced model
- slave are the unwanted dof to be removed from the ODE of the original model
The selection of master and slave dof sets is model-dependent and requires much experience
• Other reduction techniques non dependent on the selection of master dofs have been
originated within control theory, such as Krylov Subspace Method and Balanced Truncation
approach. Though, those methods were initially developed for LTI first order systems
• It is not advised the direct aplication of KSM or BT , since there is no guarantee for
preservation of reduced model structure � Modifications have been introduced to derive
second order methods
• Krylov Subspace: A is a constant nxn matrix, b a nx1 start vector. The Krylov subspace is the
subspace spanned by the q column vectors as defined below
FEW BASIC CONCEPTS
• Given the set of equations of a MIMO system, and its transfer matrix obtained after Laplace
transformationInput matrices
Output matrix
Input , output and state vectors
• Two important quantities can be defined:
System Moments:
coefficients of the
Taylor expansion of
H around zero
System Markov Parameters: replacing the eigenvalue term s by 1/lambda, the
Taylor expansion about lambda=0 yields a different expansion
Reproduces low frequency range
Reproduces high frequency range
• A reduced q dimension subspace is seeked (q<<n) in order to approximate the state space
vector of the original system �
• For then projecting the system in the subspace spanned
by another coordinate transformation matrix
• The KSM algorithm provides certain Krylov subspaces for the assignment of the projection
matrices, such that the moments of the original and reduced model match � they are
INVARIANT parameters
• For an undamped mechanical system, it can be demonstrated that
• The method is implemented by using the Arnoldi algorithm for calculation of basis vectors
and Gram-Schmidt orthonormalization for obtaining the orthonormal basis vectors
• The associated reduced model preserves structure and stability properties of
the original model
• Eigenvalues are well approximated, generally better than the rest of the
reduction approaches already presented � captures very well the dynamics of
the original model
• It is independent from the position of master and slave dof, thus the method
minimizes user intervention and has better numerical properties since the band
diagonal structure of the system matrices is not damaged
• However, the dependence of the Arnoldi algorithm on the definition of a
starting vector leads to the derivation of different projection matrices when
different starting vectors are applied � a suitable algorithm for obtaining a start
vector is essential
• Large dimension FE discretized systems: due to high accuracy required, or geometry
complexity leading to smoother meshes � the efficiency of the reduction is affected by
the system’s large dimension
• The efficiency can be measured through its goodness in capturing the dyamics of the
original model, and the computation time � likewise high for large systems
• For coping with this, the reduction can be accomplished stepwise in two stages:
- In the first stage, a reduction is applied generating a still large reduced order model,
computed relatively fast and able to capture well the dynamics of the original model, up
to certain frequency
- the dimension is still reduced by applying a further reduction method
• Choice of the algorithm for first ROM is determinant for the efficiency of the two step
method � it should be able to create an accurate reduced model with a fairly low
computation time
• The master and slave allocation constitutes an essential aspect for this first stage: the
method should be m non – dependent (to ensure that an inadequate selection of dofs
would not affect negatively the first step) but simultaneously the set of m dof must be
included in the first total set of dof
• A study on a rod was performed by Koutsovasilis and Beitelschmidt, comparing the
different reduction techniques presented
Characteristics of the Model:
- Discretized with FE in ANSYS
- Tetrahedral elements
- A total of 23835 nodes, with UX, UY and UZ
dofs each � n = 71505
- Master nodes are m=10 (black dots)
• For validity check, comparison between full and reduced model is done � it is useful to
compare the eigenfrequencies and eigenvectors of both models by a modal analysis
• For comparison of eigenvectors, the transformation matrix should be available, so as to
compare eigenvectors of the same dimension: expand the reduced eigenvector to the
dimension of the full model or viceversa
• Different Modal Correlation Criteria can be applied in order to make the comparison
• The lower the value, the
better the reduction
method
Modal Correlation Criterion: Eigenfrequency Difference
and Normalized Relative Difference
Modal Correlation Criterion:
Modified Modal Assurance Criterion
• Gives information about the angle of both compared eigenvectors, both mass
normalized and reduced to the same dimension
• 100% means absolute correlation, but a modMAC correlation equal or larger than 80%
indicates a qualitative succesful reduction
• Gives information about the relative vector difference of stiffness-normalized
eigenvectors
• Similar to the normalized relative frequency difference, since both modal stiffnesses
are compared, which are eigenfrequency dependent
• The smaller the value, the best is the comparison
Modal Correlation Criterion:
Stiffness Normalized Vector Difference
Modal Correlation Criterion:
Normalized Modal Difference
• Gives the deviation of single coordinates of compared eigenvectors � isolates the
vector coordinates that result in the worst correlation
• User is able to define at this or near this node position a master dof and reapply the
reduction procedure, by minimizing the bad coordinate correlation
• Based on Modal Scale Factor
• Results are shown for some eigenvectors
Modal Correlation Criterion:
Normalized Modal Difference
Modal Correlation Criterion:
Normalized Modal Difference
• SEREP and Krylov were the techniques delivering better eigenvalues results
• Guyan is the least reliable method for approximation of high frequency motion, due
to its static nature
• IRS has good correlation results for the lower and some higher frequency motions �
by iterative scheme, the IRS transformation matrix can be improved giving good
approximation results
• For CMS, the success depends on the selected number of eigenmodes for the internal
structure (for the rod, 5 eigenmodes were taken) � a selective choice of CB modes
belonging to the whole eigenmodes spectrum (from lower, medium and higher
ranges) seem to improve the results
• In general, the results could have been improved for a different choice of master dofs
� Krylov is a promising reduction method since there is no such dependence, and
the user intervention is minimized, by just deciding the max dimension of the reduced
system
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