Dynamics of Orthogonal Mechanism of Vibrating Table in View of Friction

Iskakov, Zharilkassin; Bissembayev, Kuatbay; Jamalov, Nutpulla

doi:10.1007/978-3-319-60702-3_27

Cited by 2 publications

(3 citation statements)

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“…From these graphs, first of all, you can observe the deviations of the dependencies φ ′ = φ ′ ( u 1 0.25em normalor 0.25em t ¯ ) from a straight line and change φ ′ depending on t ¯ or u 1 , similar dependencies M ( u 1 or t ¯ ) and N ( u 1 or t ¯ ) , and hopping effects in resonant regions. 44 . When two critical speeds are close to each other, for example, when C ¯ 12 = 2 . 50 , 2 . 38 (Figure 21) exit from resonance at a lower speed, it can lead to capture at another resonance at a higher speed.…”

Section: Resultsmentioning

confidence: 99%

“…By comparing the tabular values of the maximum amplitude and the corresponding shaft rotation speed at different values of the coefficient of nonlinear cubic damping for cases with a nonideal source and an ideal energy source, one can verify the reliability of the previously given conclusions. Expressions (44) and (49) without frequency response equations ( 26) and (48) determine the boundaries of the instability regions for the cases of a rotor with nonideal and ideal energy sources. The boundaries of the instability region constructed according to the stability criteria (44) and (49) at the value of the linear damping coefficient m 1 = 0.01 and different values of the coefficient of nonlinear cubic damping m 3 are shown in Figure 13.…”

Section: Nonstationary Resonant Transition and Their Analysismentioning

confidence: 99%

“…Expressions (44) and (49) without frequency response equations ( 26) and (48) determine the boundaries of the instability regions for the cases of a rotor with nonideal and ideal energy sources. The boundaries of the instability region constructed according to the stability criteria (44) and (49) at the value of the linear damping coefficient m 1 = 0.01 and different values of the coefficient of nonlinear cubic damping m 3 are shown in Figure 13.…”

Section: Nonstationary Resonant Transition and Their Analysismentioning

confidence: 99%

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Dynamic modeling of a non-ideal gyroscopic rotor system with nonlinear damping and nonlinear rigidity of an elastic support

Iskakov¹,

Jamalov

Bissembayeb

et al. 2022

Advances in Mechanical Engineering

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The article considers the effect of joint linear and nonlinear cubic damping on dynamics of a gyroscopic rigid rotor interacting with an electric motor with a rectilinear characteristic, taking into account the nonlinear rigidity of the support material. The method of regulating the control parameter (voltage on the motor), the amplitude of vibration, and the angular velocity of the shaft in the frequency equation, depending on the value of the coefficient of nonlinear cubic damping of the support, offers the most effective options for controlling resonant oscillations of large amplitudes. It is shown that the greater the value of the coefficient of nonlinear cubic damping, the easier it is to control these oscillations. Moreover, it is proved that the Sommerfeld effect (of the first kind) can also be weakened and eliminate with the help of joint linear and nonlinear damping. To do this, in the case of a rigid characteristic of the nonlinear elasticity of the support material, in a rotor system with a nonideal energy source to eliminate the bistability region, that is, jumping effects, more nonlinear damping of support or energy from a nonideal energy source will be required than in the case of an ideal rotor system.

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