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74

S.B. Karavashkin, O.N. Karavashkina

With it the first condition of (11) is satisfied automatically. To satisfy the second one, the equality

or

(14)

has to be true. On the other hand, when substituting (13) into (9), we obtain

(15)

As the values C=0 and sin palphacut.gif (839 bytes) = 0  are not of our interest, this condition can be true only when

(16)

or

(17)

(18)

[4, p.280].

Despite the effective transformation, the cited method does not resolve finally the problems of seeking an analytical solution. Even if omegacut.gif (838 bytes)q is determined exactly, the vibration amplitude has to be calculated on the basis of polynomials (12), with the complication growing as n grows. And etacut.gif (842 bytes) will be numerical all the same, so this method cannot be thought rigorously analytical. Furthermore, the technique to find omegacut.gif (838 bytes)q analytically is limited not only by homogeneous finite lines but also by the boundary conditions. As it was shown above, for the fixed ends the method gives a solution, but if at least one end is loaded or free, the entire structure of this technique will be destroyed. Actually, as is shown in [1], for a line with unfixed ends ''according to the allowed frequencies, the solution of this system has the form

(19)

where deltabig.gif (843 bytes)i is the i-th element shift, A is the first element vibration amplitude,  taucut.gif (827 bytes)p = Image379.gif (1060 bytes) is the parameter corresponding to the allowed frequencies omegacut.gif (838 bytes)q which are calculated analytically in the process of solution, and s is the line stiffness coefficient. We can see from (19) that at i=n, at the end of a line, the vibration amplitude will not be maximal, as we used to think for a distributed line, but will be shifted by some phase taucut.gif (827 bytes)p depending on the allowed mode number. This effect will be especially perceptible at high frequencies, when taucut.gif (827 bytes)p   is comparable with 1. And the denominator of (19) will also effect on the amplitude. It means, doing not knowing the exact analytical solutions presented in [1], one cannot state a priori the boundary conditions for a free-ends line. However without this the entire Magnus method does not work.

True, for today it is practicable to extend the boundary conditions which are true for distributed lines to those lumped. In particular, this procedure is used in [6, pp.149-150] and [11, pp.48-49] when studying a shaft with n fitted disks and a beam having n lumped masses. None the less, as is shown in [1], (19) fully satisfies the conventional modelling system of differential equations. Therefore, when calculating the exact analytical solutions for a lumped line, we have to consider this difference.

As regards to the known methods to describe the infinite models, this direction is even less clear. The solutions are mainly limited by finding the phase delay of a process along an infinite elastic line by the dispersion characteristics (see, e.g., [14, p.169], [15, pp.106-107]). At the same time Pain writes: ''The utmost ultrasonic frequency achieved for today is approximately 10 times less than nucut.gif (828 bytes) = c0 /2picut.gif (834 bytes)alphacut.gif (839 bytes)  (the critical frequency). At the range from 5*1012 to1*1013  Hz one should expect many interesting experimental results'' [14, p.169]. Actually, the results presented in [2] show that in the infinite elastic systems both forced and free vibrations can exist. They can take place not only at the subcritical regime (less than critical frequency), as in finite lines, but also at the overcritical band, when the entire vibration energy localises at a small region, but is not distributed along the entire infinite elastic line. In this case the energy accumulated in an infinite line can be finite. This conclusion is especially important, since many real processes, e.g., in crystals, can be modelled with the help of an ideal infinite model [15, p.105]. The more, such modelling is valid also for the finite elastic lines loaded by a wave impedance. So this is a great demerit that for today in this area one cannot take into account the line features, the external force application point, the description of the pattern of processes etc. To a definite extent this gap was filled in [2]. In the present paper we will study one more important factor - the external force application point influence. But the material interesting and important for the researchers and engineers is well more voluminous and requires a special attention to this research direction.

 

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