I am working on the vibration of the continuous system, I have seen lots of books on vibrations which talks about the natural frequency and mode shapes of the continuous system. I am interested in finding when particular time varying load is applied on continuous system how do we know which modes of the systems are excited and why?

Take the Fourier Transform of the time varying driving force, this will give the frequency content of the driving force. Multiple modes of vibration can be driven at once, and will superpose with each other, but time varying driving forces with a frequency content that are high at frequencies near a particular resonant frequency will mainly drive the resonant frequency's corresponding vibration mode. Note that for a perfectly sinusoidal (in time) driving force will have an infinite (Dirac delta) frequency content at the frequency of the sinusoid, and zero for all other frequencies. A perfect impulse (i.e. infinite force applied for infinitesimal time) will have a frequency content equal over all frequencies.

The reason this can be done is because superposition applies to vibrating systems, assuming vibrations are small enough. You can split any time varying driving force into a the sum of multiple sinusoids: consider what modes each sinusoid drives, and superpose all the effects together.

MODAL PARTICIPATION

For this section, I will only consider 1D vibrating systems governed by the wave equation. There exist cases, such as a transversely vibrating cantilever beam, that are governed by wave-like equations which I won't cover here unless it's of interest. Since the governing equation is the wave equation, the mode shapes will be sinusoidal.

In order to determine what amounts of each mode is being driven it is useful to write the deflected shape, $w(x,t)$, as the sum of each of the modes.

$$w(x,t) = \sum_{i} \alpha_i (t) u_i(x)$$

where $\alpha_i (t)$ is the amplitude of the $i^{th}$ mode, which can vary in time, and $u_i(x)$ is the $i^{th}$ mode shape of unit amplitude. This expression is then substituted into the governing wave equation.

For example, the governing wave equation for a vibrating tense string is given as follows:

$$\mu \frac{\partial^2 w}{{\partial t}^2} - T \frac{\partial^2 w}{{\partial x}^2} = f(x,t)$$

where $w(x,t)$ is the transverse displacement $\mu$ is mass-per-unit-length of the string, $T$ is the tension in the string, and $f(x,t)$ is the distributed transverse force-per-unit-length acting on the string.

(This equation can be adapted to other wave-governed systems by replacing the variables appropriately).

Substituting the sum of modes expression into the wave equation gets:

$$\mu \sum_i{(\ddot \alpha_i + \omega_i^2 \alpha_i) u_i(x)} = f(x,t)$$

Where $\omega_i$ is the resonant frequency corresponding to the $i^{th}$ mode. Then, by multiplying by $u_j(x)$ and integrating along the whole domain with respect to $x$, noting that some terms cancel out (the integral of $u_i(x) u_j(x)$ is zero for $i\ne j$ due to orthogonality between different mode shapes), we get the following differential equation:

$$\ddot \alpha_j + \omega_j^2 \alpha_j = \frac{2}{\mu L} \int_0^L f(x,t) u_j(x) dx$$

Where $L$ is the length of the 1D domain (in this case, the length of the string).

What this all means is that, given the distributed force-per-unit length on the system, solving the above differential equation will give the amplitude of the $j^{th}$ mode as a function of time, and hence quantify how much that mode is present at any point in time. If the distributed force is sinusoidal, after a while (i.e. at steady state) the modal amplitude will also vary sinusoidally at the same frequency. For example if:

$f(x,t) = f_0(x) \sin(\omega t)$

Then,

$\alpha_j(t) = \alpha_{j,0} \sin(\omega t)$

Where,

$\alpha_{j,0} = \frac{\frac{2}{\mu L} \int_0^L f_0(x) u_j(x) dx}{\omega_j^2 - \omega^2}$

Note how the modal amplitude seems to rocket to infinity if the system is sinusoidally driven at the resonant frequency. This is to be expected for undamped resonance: in reality, damping will prevent such unphysical responses, but this has be omitted from the scope of this answer.

It is possible to modify the modal amplitude differential equation so that the force applied is a point force instead of a distributed force. Therefore, if a point force $F(t)$ is applied at $x=x_0$, then (substituting $f(x,t) = F(t) \delta(x -x_0)$, where $\delta(x)$ is the Dirac delta function):

$$\ddot \alpha_j + \omega_j^2 \alpha_j = \frac{2}{\mu L} F(t) u_j(x_0)$$

• thank you for valuable answer,I understood it. Also I want to know about modal participation, that means under the applied load which modes vibrates with what amplitude? If you are aware with this please help me in understanding that. Thank you Sep 19 '16 at 6:16
• I've updated my answer; hope that helps. Sep 20 '16 at 22:54
• thank you for your valuable time and effort for explaining I will try to get back to you if I need some more help, hope you dont mind that!! Sep 21 '16 at 9:35
• Certainly, that'd be no problem :) Sep 21 '16 at 9:52