On the other hand the refined model (6) says that for the stable synchronization the performance of the above conditions (8) is not enough. It is also necessary condition that the coefficient of the resonant excitation of vibrations in the base should not exceed the rate of energy dissipation , i. e. . The last restriction significantly alters the stability zone of synchronization in the space system parameters that is demonstrated here on the specific computational examples.

Examples of stable and unstable regimes of synchronization

The table below shows the calculation of the different theoretical implementations of stable and unstable regimes of the phase synchronization. The example 1 (see the first line in the table) demonstrates a robust synchronization with a small mismatch between the angular velocities of drivers . The example 2 (see, respectively, the second line in the table, etc.) displays an unstable phase-synchronization regime at the same small difference between the angular velocities, i. e. . One can reach a stable steady-state synchronization pattern in this example by adding a damping element with the coefficient . The example number 3. This is a robust synchronization for the small differences in eccentrics () and equal angular velocities. The example number 4. This is an unstable synchronization mode with the same small differences in eccentrics () and small mismatch in angular velocities, i. e. . One can reach a stable regime in this example by adding a dissipative element with the damping coefficient. The example number 5. This is an unstable synchronization regime. One cannot reach any stable synchronization regime in this example, it is impossible, even when adding any damping element. The example number 6. This is an unstable regime of synchronization at different angular speeds. It is also impossible to achieve any sustainable sync mode in this case.

Table. Parameters of stable and unstable regimes of synchronization.

1	0.1	1	1	0.5	0.5	1	1	0.751	0.75	-0.244	-0.204
2	0.1	1	1	0.5	0.5	1	1	0.251	0.25	-0.072	0.008
3	0.1	1	1	0.6	0.4	1	1	0.25	0.25	-0.075	-0.001
4	0.1	1	1	0.6	0.4	1	1	0.251	0.25	-0.075	0.009
5	0.1	1	1	0.6	0.4	1	1	1.25	1.25	0.239	-0.085
6	0.1	1	1	0.5	0.5	1	1	0.26	0.25	0.998	-0.007

The matching condition .

After substitution from the expressions (3) into the standard form of equations (2), separation of fast and slow motions within the first-order approximation in the small parameter , under the assumption that , one obtains the following evolutionary equations

; (9)

,

where

is the new slow variable (), is the small detuning. The coefficients of eqs. (9) are as it follows:

;

;

;

.

The resonance of this type, as already mentioned, has no practical significance. Let the detuning be zero, then these equations (9) are highly simplified up to the full their separation:

;

(10)

.

The formal criterion of stability is extremely simple. Namely, the coefficient of the resonant excitation of vibrations in the base exceeds no the rate of energy dissipation , i. e. , but the synchronization is awfully destroyed at any positive values of other parameters.

synchronization phase resonant pattern

Conclusions

Synchronous rotations of drivers are almost idle and required no any high-powered energy set in this dynamical mode. Most responsible treatment for the drivers is their start, i. e. a transition from the rest to steady-state rotations [14]. So that, the utilizing vibration absorbers for high-powered electromechanical systems has advantageous for the two main reasons. On the one hand it provides a control tool for substantially mitigating the effects of transient shocking loads during the time of growth the acceleration of drivers. This contributes to integrities of the electromechanical system and save energy. On the other hand there is an ability to configure the appropriate damping properties of vibration absorbers to create a stable regime of synchronization when it is profitable, or even get rid of him, to destroy the synchronous movement, creating conditions for a dynamic interchange of drivers.

Acknowledgments

The work was supported in part by the RFBR grant (project 09-02-97053-р поволжье).

References

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[3] Andronov A. A, Witt A. A. By the mathematical theory of capture (J), Zhurn. Math. Physics., 1930, 7 (4): 3-20.

[4] Andronov A. A, Witt A. A. Collected Works. Moscow: USSR Academy of Sciences, 1930: 70-84.

[5] Arnold V.I. Geometrical methods in the theory of ordinary differential equations, Springer-Verlag, 1988: 372.

[6] Leonov G. A., Ponomarenko D. V., Smirnova V. B. Frequency-domain methods for nonlinear analysis (Proc.). Theory and applications. Singapore: World Sci., 1996: 498.

[7] Blekhman I.I. Vibrational Mechanics. Singapore: World Sci., 2000: 509.