Parameters of convergence analysis simulation.

## Abstract

This chapter presents the modeling procedure, numerical application, and experimental validation of uncertain quantification techniques applied to flexible rotor systems. The uncertainty modeling is based both on the stochastic and fuzzy approaches. The stochastic approach creates a representative model for the flexible rotor system by using the stochastic finite element method. In this case, the uncertain parameters of the rotating machine are characterized by homogeneous Gaussian random fields expressed in a spectral form by using the Karhunen-Loève (KL) expansion. The fuzzy approach uses the fuzzy finite element method, which is based on the α-level optimization. A comparative study regarding the numerical and experimental results obtained from a flexible rotor test rig is analyzed for the stochastic and fuzzy approaches.

### Keywords

- rotordynamics
- uncertainty
- fuzziness
- randomness
- experimental validation

## 1. Introduction

Rotating machines are unavoidably subjected to uncertainties that affect their parameters and, consequently, their dynamic behavior. Thus, mathematical models that encompass variability and randomness are required for the analysis and design of rotating machines instead of using deterministic models.

Uncertain dynamic responses of flexible rotors have been analyzed by applying two main approaches, namely, stochastic and fuzzy. Thus, the uncertainty analysis has been applied in flexible rotors by using the polynomial chaos theory [1], as modeled by considering Gaussian homogeneous stochastic fields discretized by Karhunen-Loève expansion [2] or through the fuzzy approach [3, 4]. These methods are well-established tools that may present limitations and drawbacks depending on the application conveyed.

In this context, this chapter presents two different approaches to model uncertain parameters and to simulate the uncertain dynamic responses of rotating machines. In this way, the stochastic and fuzzy approaches are applied to different parameters of a flexible rotor. The procedure used to obtain the stochastic model of the rotor is based on the stochastic finite element method. Moreover, the fuzzy finite element model of the rotor system is formulated according to the fuzzy approach. Then, the corresponding numerical method used to compute the fuzzy dynamic responses of the rotating machine is described. A comparative study between the stochastic and fuzzy approaches along with the validation of the obtained results by using experimental data is presented.

## 2. Rotor system model

The deterministic model of a flexible rotor based on the finite element method (FE model) is obtained in this section by following the formulation previously presented in [5]. The rotor system is composed of a flexible shaft, rigid discs, and bearings. Figure 1 shows the finite element used to represent the shaft. In this case, the finite element has two nodes and four degrees of freedom (DOFs) per node. The DOFs are associated with the nodal displacements along the * x* and

*directions (defined by*z

*and*u

*, respectively) and the rotations around the*w

*and*x

*directions (*z

*= ∂*θ

*/∂y and*w

*= ∂*ψ

*/∂*u

*, respectively).*y

In this contribution, the FE model of the shaft was obtained based on the Euler-Bernoulli and Timoshenko beam theories. The displacement field along the finite element is represented by a cubic interpolation function. Therefore, ** u**(

*,*y

*) =*t

**(**N

*)*y

u

*(*

_{e}

*), where*t

**(**N

*) is a matrix containing shape interpolation functions and*y

u

*(*

_{e}

*) = [*t

*]*u

_{i}w

_{i}θ

_{i}ψ

_{i}

*(*

^{T}

*= 1, 2) is the vector of DOFs.*i

The strain and kinetic energies of the shaft finite element are defined according to analytical equations derived from the variational principle. Therefore, the mass and stiffness elementary matrices of the shaft are given by

where (

_{s}

^{e}

*×*N

_{e}

*) is the elementary mass matrix of the shaft element,*N

_{e}

G

*(*

_{s}

^{e}

*×*N

_{e}

*) is the gyroscopic matrix,*N

_{e}

K

*(*

_{s}

^{e}

*×*N

_{e}

*) is the stiffness matrix, and*N

_{e}

**is the isotropic matrix that contains the elastic properties of the material.**E

**(**B

*) is the matrix composed of differential operators that characterize the strain–displacement relationship.*y

N

*and*

_{mi}

^{T}

N

*represent the shape interpolation functions associated with the mass and inertia matrices, respectively.*

_{g}

^{T}

*= 8 is the number of DOFs considered in the shaft finite element.*N

_{e}

Rigid discs are introduced in the global FE model of the shaft by considering their corresponding kinetic energy. Thus, (

_{d}

^{e}

*×*N

_{d}

*) and*N

_{d}

G

*(*

_{d}

^{e}

*×*N

_{d}

*) are the mass and gyroscopic matrices associated with each disc (*N

_{d}

*= y is the number of DOFs considered for the disc). Moreover, the bearings are modeled by using linear stiffness and damping coefficients that are introduced conveniently in the stiffness and damping matrices of the shaft FE model, respectively [6].*N

_{d}

Eq. (2) presents the differential equation that characterizes the dynamic behavior of rotating machines (FE model with * N* DOFs), which is obtained by assembling the elementary finite element matrices of the shaft:

where ** M** =

M

*+*

_{s}

M

*(*

_{d}

*×*N

*) and*N

**=**K

K

*+*

_{s}

K

*(*

_{b}

*×*N

*) are the global mass and stiffness matrices of the rotor model, respectively.*N

K

*is the matrix containing the stiffness coefficients of the bearings.*

_{b}

**=**C

C

*+*

_{b}

C

*(*

_{p}

*×*N

*) is the damping matrix that considers the damping coefficients of the bearings (matrix*N

C

*) and the proportional damping*

_{b}

C

*=*

_{p}

α

**+**M

β

**(**K

*and*α

*are the so-called proportional coefficients).*β

**=**G

G

*+*

_{s}

G

*(*

_{d}

*) is the gyroscopic matrix.*NxN

**(**q

*) (*t

*× 1) and*N

**(**F

*) (*t

*× 1) are the vectors of DOFs and external loads, respectively. Ω is the rotation speed of the shaft. More details about the formulation of the rotor FE model adopted in the present contribution can be found in [5].*N

## 3. Stochastic modeling

Among the various methods used to model uncertainties, the stochastic finite element method (SFEM) has been widely applied to complex engineering systems of industrial applications. SFEM presents well-established mathematical fundaments and suitable experimental validation [7]. Some details about the formulation of the SFEM are presented next.

### 3.1 Stochastic modeling of flexible shafts

The Karhunen-Loève (KL) expansion is used to model the random fields as a spectral representation. Consequently, a random field is represented as a spatial expansion of a random variable that fluctuates randomly. For instance, uncertainties affecting Young’s modulus of the shaft can be evaluated by using the KL expansion. A one-dimensional random field * H*(

*,*y

*) can be defined as [8]*θ

where * f*(

_{r}

*) and*y

*are the eigenfunctions and eigenvalues of the covariance function*λ

_{r}

*(*C

y

_{1},

y

_{2}), respectively.

*is the number of terms used in the KL expansion.*n

_{KL}

In this work, the exponential covariance is adopted, which is defined as * C*(

y

_{1},

y

_{2}) = e

^{(−|y₁−y₂|/Lc)}, where (

y

_{1},

y

_{2})

*] and*L

*represent the correlation length.*L

_{c}

*(*ξ

_{r}

*) denotes the random variables that are orthonormal with respect to the functions*θ

*(*f

_{r}

*). The KL expansion is used to model the stochastic finite element matrices of the flexible shaft, as given by Eq. (4):*y

where

in which
* E*,

_{s}

*, and*A

_{s}

*(Young’s modulus, cross-sectional area, and inertia moment of the shaft, respectively).*I

_{s}

### 3.2 Stochastic modeling of bearings’ parameters

The uncertainties associated with bearings’ stiffness and damping coefficients of rotating machines can be evaluated by using the following relations: * k*(

*) =*θ

k

_{o}+

k

_{o}

*(*δ

_{k}ξ

*) and*θ

*(*d

*) =*θ

d

_{o}+

d

_{o}

*(*δ

_{d}ξ

*), respectively. In this case,*θ

k

_{o}and

d

_{o}are the mean values of the stiffness and damping coefficients of the bearings, respectively.

*and*δ

_{k}

*are the corresponding dispersion levels.*δ

_{d}

*(*ξ

*) represents the stochastic distribution. The stochastic model of the rotor is solved by using the Monte Carlo simulation (MCS) in combination with Latin hypercube sampling [9].*θ

### 3.3 Numerical results

In this section, SFEM is applied to the FE model as given by Figure 2. The rotating machine is composed of a horizontal flexible shaft discretized into 20 Euler-Bernoulli’s beam elements, three asymmetric bearings (_{1}, _{2}, and _{3}), and two rigid discs (_{1} and _{2}). The physical and geometrical characteristics used in the FE model of the rotor system are given in [2].

In this case, the uncertain random fields associated with Young’s modulus of the shaft are modeled as homogeneous Gaussian stochastic fields, which are represented in the spectral form by using the Karhunen-Loève expansion. The uncertainty variables associated with the stiffness and damping coefficients of the bearings are modeled as random variables. This modeling process considers the frequency- and time-domain vibration responses of the rotating machine in terms of their working envelopes (frequency response functions (FRFs) and orbits).

Initially, the convergence of the stochastic model is verified by changing the number of terms used in the KL expansion and the number of samples considered in MCS (* n* and

_{KL}

*, respectively). The convergence analysis was performed based on the root-mean-square (RMS) value as given by Eq. (6):*n

_{s}

where ** H**(

*, Ω) is the FRF obtained by using the deterministic FE model of the rotor and*ω

**(**H

*, Ω,*ω

*) is the corresponding FRF of the stochastic model associated with independent realizations*θ

The deterministic and stochastic FRFs were obtained by considering the shaft at rest (
* x* direction of the disc

D

_{1}and measures obtained at the same position and direction. Two scenarios were evaluated to achieve convergence for

*and*n

_{KL}

*, as given by Table 1. In both cases, the correlation length*n

_{s}

*was assumed as being equal to the length of the shaft elements.*L

_{C}

Scenario | _{KL} |
_{s} |
---|---|---|

(a) | 1 ≤ ≤ 50_{KL} |
100 |

(b) | 10 | 1 ≤ ≤ 250_{s} |

Figures 3a and b present the upper and lower limits of the RMS envelopes obtained by considering the scenarios (a) and (b) of Table 1, respectively. Note that convergence is achieved for * n* = 10 and

_{KL}

*= 70.*n

_{s}

Figure 4a and b show the FRF and orbit, respectively, obtained by using the deterministic (mean) and stochastic FE models of the rotor system. The uncertain envelopes were determined by applying a 5% dispersion level both in Young’s modulus of the shaft (* E*) and in the stiffness and damping coefficients of the bearings (

_{s}

*,*k

_{xx}

*,*k

_{zz}

*, and*d

_{xx}

*; see Figure 2). The results show the influence of the uncertain parameters on the dynamic behavior of the flexible rotor, which are highlighted by the dispersion of the uncertain envelopes around the curves of the deterministic FRF and orbit (mean model) (Figures 3 and 4).*d

_{zz}

## 4. Fuzzy dynamic analysis

The fuzzy dynamic analysis computes the uncertain dynamic responses of rotating machines by modeling the uncertain parameters as fuzzy variables or fuzzy fields. The fuzzy dynamic analysis is based on the * α*-level optimization, which was introduced by [10]. In the

*-level approach, an optimization problem should be solved to compute the fuzzy responses of the system as presented next.*α

### 4.1 Fuzzy variables

Figure 5 presents the definition of fuzzy sets. Considering ** X** as a universal set whose elements are defined by

*, subset*x

*(*A

*∈*A

**) is defined by the membership function**X

*:*μ

_{A}

**{0, 1}, where**X →

*= 1) or does not belong to the classical set*μ

_{A}

*(see Figure 5a). Moreover, a fuzzy set*A

*is defined by the membership function*Ã

*:*μ

_{A}

**[0, 1]. The membership function**X →

*(*μ

_{A}

*) defines how compatible the element*x

*is with respect to the fuzzy set*x

*. Thus,*Ã

*(*μ

_{A}

*) close to 1 indicates high pertinence of*x

*to*x

*.*Ã

Fuzzy variables are represented by using intervals weighted by the membership function, namely, * α*-levels. According to the

*-level representation,*α

*is defined as*Ã

where 0 ≤ * μ*(

_{A}

*) ≤ 1.*x

Moreover, according to Figure 5b

If the fuzzy set is convex, each * α*-level subset

*corresponds to the interval [*A

_{αk}

*, x*x

_{αkl}

*], where*

_{αku}

### 4.2 Fuzzy dynamic analysis

The fuzzy dynamic analysis is a numerical method used to map a fuzzy input

Figure 6 shows that the fuzzy dynamic analysis is composed of two main steps. The first step consists in discretizing the input fuzzy parameter according to the
* X* = [

_{iαk}

*,*x

_{iαkl}

*], where*x

_{iαku}

α

_{k}

X

_{1αk}, …

*)*X

_{nαk}

In the second step, an optimization problem is performed. This optimization process maximizes and minimizes the value of the output for the mapping model

where * z* and

_{αkl}

*are the lower and upper limits of the interval*z

_{αku}

*= [*z

_{αk}

*,*z

_{αkl}

*] corresponding to the*z

_{αku}

*-level*α

*.*α

_{k}

The complete set of the intervals * z* for

_{αk}

α

_{k}

The fuzzy analysis of either a transient time-domain response or a frequency response function demands the solution of a large number of

### 4.3 Numerical results

The numerical results for the fuzzy analysis are also obtained by using the rotor FE model presented in Figure 2. In this case, Young’s modulus * E* of the shaft and the stiffness and damping coefficients of the bearings (

_{S}

B

_{1},

B

_{2}, and

B

_{3}) were considered as fuzzy triangular numbers (uncertain parameters). In this case, a 5% dispersion level was applied around the deterministic value of Young’s modulus and a 15% dispersion level around the deterministic values of the stiffness and damping coefficients of the bearings. The fuzzy response of the rotor system was assessed at three different

The fuzzy responses both on the time and frequency domains show that the fuzzy uncertainty parameters produce a significant variation of the lower and upper curves of the fuzzy envelope. Note that the results obtained in the present analysis are similar to the ones presented in Figure 4, for which the stochastic approach was applied.

## 5. Comparative study of uncertainty quantification techniques

The uncertainty analysis of dynamic systems has been previously studied by applying techniques based both on stochastic and fuzzy approaches. The fuzzy approach has demonstrated to be more appropriate in the cases of applications for which there is no knowledge regarding the stochastic process that governs the uncertainties themselves.

In the present study, the uncertainties that affect the dynamic response of a flexible rotor system are modeled by using both stochastic and fuzzy approaches. These methodologies have been compared by evaluating the dynamic responses obtained by numerical simulations regarding the frequency responses and time-domain responses. The numerical and experimental results of this section have been obtained from the flexible rotor test rig depicted in Figure 8.

The corresponding FE model was discretized in 33 finite elements, as given by Figure 8b. This rotating machine is composed of a flexible steel shaft of 860 length and 17 mm diameter (* E* = 205 GPa,

*= 7850 kg/m*ρ

^{3},

*= 0.29); two ball bearings (*υ

B

_{1}and

B

_{2}); located at nodes #4 and #31, respectively; and two rigid discs

*(located at node #13) and*D

_{1}

*(at node #23). Displacement sensors are placed at nodes #8 (*D

_{2}

*and*S

_{8X}

*) and #28 (S*S

_{8Z}

_{28X}and S

_{28Z}) to measure the shaft vibration responses. An electric DC motor drives the shaft.

A representative FE model of the rotating machine was obtained by applying a model updating procedure. The differential evolution optimization approach was used to identify the unknown parameters of the FE model, namely, coefficients * α* and

*(proportional damping), the stiffness and damping coefficients of the bearings, and the angular stiffness*β

*introduced by the coupling between the electric motor and the shaft (orthogonal to plane*k

_{ROT}

*at node #1). Further information about the model updating procedure can be found in [8].*XZ

Figure 9 shows the simulated Bode diagram obtained by using the parameters identified by the considered optimization procedure. The experimental diagram is added to the figure for comparison purposes. The similarity between the numerical and experimental Bode diagrams demonstrates the representativeness of the obtained FE model.

### 5.1 Frequency-domain analysis

In the present analysis, the uncertain envelope of the FRF was obtained by considering Young’s modulus of the shaft as uncertain information. Regarding the stochastic approach, uncertain Young’s modulus is modeled as a Gaussian random field with nominal value * E* = 205 GPa and a 15% dispersion level. The convergence analysis was carried out to evaluate the number of terms retained in the truncated KL expansion (

_{s}

For the fuzzy approach, a fuzzy triangular number with the same nominal value and dispersion considered for the stochastic approach (

In this contribution, the performed uncertainty analysis aims at obtaining the minimum and maximum responses of the rotor system, i.e., the bounds of the uncertain dynamic responses. Therefore, the fuzzy uncertainty analysis was devoted to the

Figure 11 presents a comparative evaluation of the FRFs’ uncertain envelopes obtained by applying the stochastic and fuzzy approaches. In this case, the obtained FRFs were determined by considering the force applied along the * x* direction of disc

*and sensor*D

_{1}

S

_{8X}. The results show that the uncertain envelopes obtained from the stochastic and fuzzy approaches are similar. Additionally, the updated FRF is also shown for comparison purposes.

### 5.2 Time-domain analysis

The time-domain analysis was performed based on the orbits of the flexible shaft. This analysis considers uncertainties affecting the stiffness coefficients * k* and

_{xx}

*of bearing*k

_{zz}

B

_{1}. For the stochastic approach, the uncertain parameters were modeled as Gaussian random variables with

*= 8.551 × 10*k

_{xx}

^{5}N/m,

*= 1.198 × 10*k

_{zz}

^{6}N/m (mean values), and deviation of ±10%. The rotation speed of the rotor is 1200 rev/min, and an unbalance of 487.5 g mm/0

^{0}was applied to disc

D

_{1}.

The convergence analysis was performed to determine * n* and

_{KL}

*based on the time-domain vibration responses of the rotor system. Figure 12 shows the obtained results. Note that convergence was achieved for*n

_{s}

*≥ 100 and*n

_{KL}

*≥ 500.*n

_{s}

Considering the fuzzy approach, the uncertain parameter is defined as a fuzzy triangular number with the same nominal value and deviation of the stochastic modeling. The objective function of the
* S*. Figure 13 presents a comparative evaluation of the uncertain envelopes of the rotor orbits determined by using the stochastic and fuzzy approaches. Note that the obtained results are similar, demonstrating that both approaches lead to equivalent responses.

_{8X}

## 6. Conclusions

This chapter is dedicated to the modeling, numerical methods, and simulations for the uncertainty analysis of flexible rotors. The stochastic and fuzzy approaches showed to be suitable methods to quantify the effect of uncertain parameters on the dynamic responses of rotating machines. The comparative study permitted to evaluate the two studied approaches is based on numerical simulations. Although the numerical results obtained by applying both approaches were similar, the fuzzy approach demands a greater computational effort than the stochastic method. Nevertheless, the stochastic approach requires an extensive mathematical background and an insight knowledge on the uncertain parameters. In this case, the stochastic distribution should be known or assumed. However, both approaches can be applied to the design of rotating machines.

## Acknowledgments

The authors are thankful for the financial support provided to the present research effort by CNPq (574001/2008-5, 304546/2018-8, and 431337/2018-7), FAPEMIG (TEC-APQ-3076-09, TEC-APQ-02284-15, TEC-APQ-00464-16, and PPM-00187-18), and CAPES through the INCT-EIE. The authors are also thankful to the companies CERAN, BAESA, ENERCAN, and Foz do Chapecó for the financial support through the R&D project Robust Modeling for the Diagnosis of Defects in Generating Units (02476-3108/2016).

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