On the analysis of forced oscillations of systems with two random sources of parametric effects

Boris Roev1 , Aleksey Vinokur2

1, 2Moscow State University of Printing Arts, Moscow, Russia

2National Research Nuclear University MEPhI (Moscow Engineering Physics Institute), Moscow, Russia

1Corresponding author

Vibroengineering PROCEDIA, Vol. 8, 2016, p. 147-151.
Received 7 September 2016; accepted 12 September 2016; published 7 October 2016

Copyright © 2016 JVE International Ltd. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.
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Abstract.

The problem of forced oscillations in a mechanical system with random parameters is considered in this paper. The analysis of the interaction of forced and parametric oscillators is conducted by the example of the system where the properties of inertia and stiffness are randomized. The parametric effects are presented in the form of narrowband random processes. The obtained amplitude-frequency characteristics demonstrate the development of dynamic processes.

Keywords: variance, carrier frequency, parametric effect, resonance, random process.

1. Introduction

When considering a number of machines, in particular the printing ones, the relevant issue is the interaction of parametric and forced random oscillations that occur in them. Problems of this kind in general terms were studied in [1-6].

We demonstrate the results of the interaction of forced and parametric random oscillations study by the example of the system performing torsion oscillations, when the coefficients of the inertial term and the stiffness-related term change randomly. The equation Eq. (1) describing these oscillations is as follows:

(1)
1 - f 1 t θ ¨ + 2 ε θ ˙ + ω 0 2 1 - f 3 t θ = m t ,

where θ(t) – angle of rotation fj(t) – parametric effects, m(t) – equivalent rotational moment; ε, ω0 – the system parameters [4]; the description of inciting factors fj(t) and m(t) is presented hereafter.

2. The method

To solve the problem, we use a modified spectral method [7, 8]. For functions θ(t)fj(t) we introduce the following integral representations Eq. (2):

(2)
θ t = θ 0 t + - ψ ω , t Q ω e i ω t d ω ,
f j t = - F j ω e i ω t d ω ,     j = 1,3 ,

where θ0t – the expected rotation angle of θt; ψ(ω,t) – an unknown deterministic function; Qω and Fjω – random spectra that satisfy the conditions of stochastic orthogonality. The external action is deterministic and is presented as: mt=m0cosΩt.

After substituting Eq. (2) into Eq. (1) and drawing up the torque ratios by the method described in [7, 8], for the unknown function θ0t and ψ(ω,t) we obtain the following system of differential equations Eq. (3):

(3)
θ ¨ 0 + 2 ε θ ˙ 0 + ω 0 2 θ 0 - - ψ ¨ + 2 i ω ψ ˙ - ω 2 ψ S f 1 θ + ω 0 2 ψ S f 3 θ d ω = m 0 c o s Ω t ,
ψ ¨ + 2 ε + i ω ψ ˙ + ω 0 2 - ω 2 + 2 i ε ω ψ S f 1 θ ω - θ ¨ 0 S f 1 ω - ω 0 2 θ S f 1 f 3 ω = 0 ,
ψ ¨ + 2 ε + i ω ψ ˙ + ω 0 2 - ω 2 + 2 i ε ω ψ S f 3 θ ω - θ ¨ 0 S f 1 f 3 ω - ω 0 2 θ S f 3 ω = 0 .

Let the parametric effects be the perfect narrow-band processes with spectral densities Eq. (4):

(4)
S f j ω = σ f j 2 2 δ ω - ω j ,

with the same carrier frequency ω1=ω3=ω*, but with different variance σfj2. Here δω is the Dirac delta-function.

Then we find a particular solution of this system which describes the steady-state forced oscillations. Since the right part of the system is mt=m0cosΩt, then the solution Eq. (5) will be sought in the following form:

(5)
θ 0 * t = A cos Ω t + B sin Ω t ,
ψ ω , t = D ω cos Ω t + G ω sin Ω t .

As a result of the substitution of Eq. (4) and Eq. (5) in Eq. (3) and making the necessary transformations, we obtain a formula for the amplitude of rotation angles Eq. (6):

(6)
A - = A 2 + B 2 = m 0 ω 0 2 Δ - 1 α - 22 2 + α - 21 2 ,

where:

α - 11   = 1 - γ 2 + I 1 ,         α - 12   = 2 δ γ + I 2 ,         α - 21   = - 2 δ γ + I 3 ,       α - 22   = 1 - γ 2 + I 4 ,
I 1 = σ f 1 2 a 11 A 1 + b 11 B 1 A 1 2 + B 1 2 + σ f 3 2 c 5 A 1 + d 5 B 1 A 1 2 + B 1 2 ,         I 2 = σ f 1 2 a 21 A 1 + b 21 B 1 A 1 2 + B 1 2 + σ f 3 2 c 6 A 1 + d 6 B 1 A 1 2 + B 1 2 ,
I 3 = σ f 1 2 a 31 A 1 + b 31 B 1 A 1 2 + B 1 2 + σ f 3 2 c 6 A 1 + d 6 B 1 A 1 2 + B 1 2 ,         I 4 = σ f 1 2 a 41 A 1 + b 41 B 1 A 1 2 + B 1 2 + σ f 3 2 c 5 A 1 + d 5 B 1 A 1 2 + B 1 2 ,
a 11 = - γ 2 c 1 + c 4 ,       b 11 = - γ 2 d 1 + d 4 ,       a 21 = γ 2 c 2 - c 3 ,
b 21 = γ 2 ( d 2 - d 3 ) 1 ,       a 31 = - γ 2 ( c 2 + c 3 ) , b 11 = - γ 2 ( d 2 + d 3 ) ,
a 41 = - γ 2 c 1 - c 4 ,       b 21 = - γ 2 d 1 - d 4 ,       c 1 = γ 1 2 - γ 2 1 - γ 2 - γ 1 2 ,
d 1 = 2 δ γ 1 γ 1 2 - γ 2 ,       c 2 = 2 δ γ γ 1 2 - γ 2 ,       d 2 = 2 γ γ 1 γ 1 2 - γ 2 ,
c 3 = - 4 δ γ 1 2 γ ,       d 3 = 2 γ 1 γ 1 - γ 2 - γ 1 2 ,       c 4 = - 4 γ 1 2 γ 2 ,       d 4 = 4 δ γ 2 γ 1 ,
c 5 = 1 - γ 2 - γ 1 2 , d 5 = 2 δ γ 1 ,       c 6 = 2 δ γ ,       d 6 = 2 γ 1 γ ,
A 1 = 1 - γ 2 - γ 1 2 2 + 4 γ 2 δ 2 - γ 1 2 - δ 2 γ 1 2 ,       B 1 = 4 δ γ 1 1 + γ 2 - γ 1 2 ,
γ = Ω ω 0 ,       γ 1 = ω * ω 0 ,       δ = ε ω 0 .

3. The results

In order to visualize the results of the study, these characteristics must be built into a volumetric image and in the form of level graphic charts. If we record the frequency of the external and the parametric effects in the form of one-dimensional arrays γi and γ1j (i= 1,..., 200; j= 1,..., 300 with a step of 0.02), then the amplitude (6) occurring in the drive system, will be a two-dimensional array A-ij, whose graphical image is a surface. Level graphic charts provide an opportunity to observe a change in the amplitude-frequency characteristics on the frequency plane. In this case the vertical axis corresponds to the frequency of the external effect, and the horizontal axis corresponds to the frequency of the parametric one. Let us consider the effect of the variance σf32 of parametric influence, taking only stiffness, while considering that the inertia effect is absent σf12=0. In this case the dimensionless damping parameter was taken as δ= 0.2. First, let us consider the case when σf32=0. Then the amplitude-frequency response will correspond to the system with one degree of freedom with constant parameters, where there is a single resonance at the natural frequency. At the same time, there is no distortion on the level graphic chart Fig. 1.

Fig. 1. The amplitude-frequency characteristic with σf12=0 and σf32=0: A – amplitude, γ and γ1 – frequency of external and parametric action

With increase in variance of the parametric influence on the part of stiffness σf32, in the area of the main parametric resonance γ1= 2,0 the distortion of the amplitude-frequency characteristic is observed Figs. 2-4, which changes significantly the character of the dynamic processes in the system. Also there occur additional resonant peaks.

Fig. 2. The amplitude-frequency characteristic with σf12= 0 and σf32= 0.04 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Fig. 3. The amplitude-frequency characteristic with σf12= 0 and σf32= 0.16 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Very interesting is the case when the variance of the parametric effects, associated with rigidity, σf32= 1.0. Here there are two resonances, the most significant of which is observed at low frequencies Fig. 4. A further increase in this variance again changes the picture of the dynamic processes occurring in the system. Next, we consider the influence of the inertial parametric effect on the character of amplitude-frequency characteristics Figs. 5-8.

Fig. 4. The amplitude-frequency characteristic with σf12= 0 and σf32= 1.0 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Fig. 5. The amplitude-frequency characteristic with σf12= 0 and σf32= 1.44 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Fig. 6. The amplitude-frequency characteristic with σf12= 0.04 and σf32= 0.04 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Fig. 7. The amplitude-frequency characteristic with σf12= 0.04 and σf32= 0.16 (A – amplitude, γ and γ1 – frequency of external and parametric action)

Fig. 8. The amplitude-frequency characteristic with σf12= 0.04 and σf32= 1.0 (A – amplitude, γ and γ1 – frequency of external and parametric action)

In this case, there is a qualitative change in the behavior of the system under external periodic effects. At low values of the inertial effect variance σf12= 0.04 on the amplitude-frequency characteristic there occur a group of resonant peaks. The most significant peaks are observed in the area of the main parametric resonance (γ1= 2,0; j= 100). With increase in this variance, the resonance peaks begin to shift from the resonant fields of parametric and forced oscillations. On the level graph charts these peaks are represented by dots. The shift of these resonances is connected, apparently, with the presence of other parametric resonances besides the main one. Each of them can only appear when there is a certain combination of frequencies of the external and parametric effects, because the system becomes sensitive to even a slight change in its parameters.

4. Conclusions

In [7] the results of the study of forced oscillations in mechanical systems were presented in the form of amplitude-frequency characteristics with fixed values of frequency and variance of parametric random effects. In order to have a complete understanding of the dynamic processes in these systems, within the framework of the method adopted in this work, it is necessary to analyze a significant number of amplitude-frequency characteristics. The results obtained show that the increase in the variance of the parametric effect, associated with the stiffness of the system, leads to an increase in the number of resonant peaks, because any slight change in the parameters of the effect can change their appearance significantly.

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