Synchronization and effect of Zommerfelda as typical resonant samples (стр. 1 из 3)

Synchronization and Sommerfeld as Typical Resonant Patterns

Part I. Single Driver Example

Kovriguine D.A.

Abstract We analyze a classical problem of oscillations arising in an elastic base caused by rotor vibrations of an asynchronous driver near the critical angular velocity. The nonlinear coupling between oscillations of the elastic base and rotor takes place naturally due to unbalanced masses. This provides typical frequency-amplitude patterns, even let the elastic properties of the beam be linear one. As the measure of energy dissipation increases the effect of bifurcated oscillations can disappear. The latter circumstance indicates the efficiency of using vibration absorbers to eliminate or stabilize the dynamics of the electromechanical system.

Key Words Sommerfeld effect, asynchronous device; Lyapunov criterion, Routh-Hurwitz criterion, stability.

stationary oscillation resonance synchronization

Introduction

The phenomenon of bifurcated oscillations of an elastic base, while scanning the angular velocity of an asynchronous driver, is referred to the well-known Sommerfeld effect [1-9]. Nowadays, this plays the role of one of classical representative examples of unstable oscillations in electromechanical systems, even being the subject of student laboratory work in many mechanical faculties. This effect is manifested in the fact that the descending branch of resonant curve can not be experienced in practice. A physical interpretation is quite simple. The driver of limited power cannot maintain given amplitude of stationary vibrations of the elastic base. Any detailed measurements can reveal that the oscillation frequency of the base is always somewhat higher than that predicted by linear theory. This implies a very reasonable physical argument. With an increase of base vibrations, for example, the geometric nonlinearity of the elastic base should brightly manifest itself, so that this assuredly may lead to the so-called phenomenon of “pulling” oscillations. However, a more detailed mathematical study can demonstrate that the dynamic phenomena associated with the Sommerfeld effect are of more subtle nature. If one interprets this effect as a typical case of resonance in nonlinear systems, then one should come to a very transparent conclusion. The appearance of the frequency-amplitude characteristic naturally encountered in nonlinear systems, say, when regarding the Düffing-type equations, does not necessarily have place due to the geometric nonlinearity of the elastic base. This dependence appears as a result of nonlinear resonant coupling between oscillations of the elastic base and rotor vibrations, even when the elastic properties being absolutely linear one. The latter circumstance may attract an interest in such a remarkable phenomenon, as the effect of Sommerfeld, which is focused in the present paper.

The equations of motion

The equations describing a rotor rolling on an elastic base read [1-6]

Synchronization and effect of Zommerfelda as typical resonant samples

;(1)

where

is the mass of a base with one degree of freedom, characterized by the linear displacement

is the elasticity coefficient of the base,

is the damping coefficient,

stands for the mass of an eccentric,

denotes the radius of inertia of this eccentric,

is the moment of inertia of the rotor in the absence of imbalance,

is the driving moment,

describes the torque resistance of the rotor. The single device (unbalanced rotor) set on the platform, while the rotation axis is perpendicular to the direction of oscillation. The angle of rotation of the rotor

is measured counter-clockwise. Assume that the moment characteristics and the engine drag torque are modeled by the simple functions

and

, where

is the starting point,

is the coefficient characterizing the angular velocity of the rotor, i.e.

is the resistance coefficient. Then the equations of motion are rewritten as

After introducing the dimensionless variables the basic equations hold true:

where

is the-small parameter,

. Here

stands for the oscillation frequency of the base,

is the new dimensionless linear coordinate measured in fractions of the radius of inertia of the eccentric,

is the dimensionless coefficient of energy dissipation,

.is the new dimensionless time.

The set (3) is now normalized at the linear part approaching a standard form. First, the equations can be written as a system of four first-order equations

Then we introduce the polar coordinates,

and

. So that the equations take the following form

Now the set (5) experiences the transform on the angular variable

. Then the equations obtain the form close to a standard form

Here

denotes the partial angular velocity of the rotor. The system of equations (6) is completely equivalent to the original equations. It is not a standard form, allowed for the higher derivatives [10], but such form is most suitable for the qualitative study of stationary regimes of motion, due to the explicit presence of generalized velocities in the right-hand side terms.

Resonance

We study the resonance phenomenon in the dynamical system (6). Let

, then eqs. (6) are reduced to the following set:

, which has a simple solution

where

are the integration constants. Now the solution (7) is substituted into the right-hand terms of eqs. (6). Then one discards all the terms in order

and higher, as well, to perform the averaging over the period of fast rotating phases. In the problem (6) the fast variables are the angles

and

, accordingly, the slow variables are

and

. The average of an arbitrary function

is calculated as

Now the average

isexamined for the presence of jumps along a smooth change of system parameters. One of which represents the partial angular velocity

. It is easy to see that the jump of the average takes place at the value

The equations of slow motions