This is the second post in a series on vibrations determine by the equation

*m* *u*`''`

+ γ *u*`'`

+ *k u* = *F* cos ω*t*

The first post in the series looked at the simplest case, γ = 0 and *F* = 0. Now we’ll look at the more realistic and more interesting case of damping γ > 0. We won’t consider forcing yet, so F = 0 and our equation reduces to

*m* *u*`''`

+ γ *u*`'`

+ *k u* = 0.

The effect of damping obviously depends on the amount of damping, i.e. the size of γ relative to other terms. Damping removes energy from the system and so the amplitude of the oscillations goes to zero over time, regardless of the amount of damping. However, the system can have three qualitatively different behaviors: under-damping, critical damping, and over-damping.

The characteristic polynomial of the equation is

*m* *x*^{2} + γ *x* + *k*

This polynomial has either two complex roots, one repeated real root, or two real roots depending on whether the discriminant γ^{2} – 4*mk* is negative, zero, or positive. These three states correspond to under-damping, critical damping, and over-damping.

**Under-damping**

When damping is small, the system vibrates at first approximately as if there were no damping, but the amplitude of the solutions decreases exponentially. As long as γ^{2} < 4*mk* the system is under-damped and the solution is

*u*(*t*) = *R* exp( –γ*t*/2*m* ) cos( μ*t*– φ )

where

μ = √(4*mk* – γ^{2}) / 2*m.*

The amplitude R and the phase φ are determined by the initial conditions.

As an example, let γ =1, *m* = 1, and *k* = 5. This implies μ = √19/2. Set the initial conditions so that *R* = 6 and φ = 1. The solid blue line below is the solution 6 exp(-*t*/2) cos(*t*– 1), and the dotted green lines above and below are the exponential envelope 6 exp(-*t*/2).

And here is a video of the mass-spring-dashpot system in action made using the code discussed here.

Note that the solution is not simply an oscillation at the natural frequency multiplied by an exponential term. The damping changes the frequency of the periodic term, though the change is small when the damping is small.

The factor μ is called the quasi-frequency. Recall from the previous post that the natural frequency, the frequency of the solution with no damping, is denoted ω_{0}. The quasi-frequency is related to the natural frequency by

μ = √(1 – γ^{2}/4*mk*) ω_{0} ≈ (1 – γ^{2}/8*mk*) ω_{0}.

The approximation above holds for small γ since a Taylor expansion shows that √(1 – *x*) ≈ 1 – *x*/2 for small *x*.

This says that the quasi-frequency decreases the natural frequency by a factor of approximately γ^{2}/8*mk*. So when γ is small there is little change to the natural frequency, but the amount of change grows quadratically as γ increases.

**Critical damping**

Critical damping occurs when γ^{2} = 4*mk*. In this case the solution is given by

*u*(*t*) = (*A* + *Bt*) exp( – γ*t*/2*m*).

The position of the mass will asymptotically approach 0. Depending on the initial velocity, it will either go monotonically to zero or reach some maximum displacement before it turns around and goes to 0.

For an example, let *m* = 1 and *k* = 5 as before. For critical damping, γ must equal √20. Choose initial conditions so that *A* = 1 and *B* = 10.

**Over-damping**

When γ^{2} > 4*mk* the system is over-damped. When damping is that large, the system does not oscillate at all.

The solution is

*u*(*t*)* = A* exp(*r*_{1} *t*) + *B* exp(*r*_{2} *t*)

where *r*_{1} and *r*_{2} are the two roots of

*m* *x*^{2} + γ *x* + *k* = 0.

Because γ > 0, both roots are negative and solutions decay exponentially to 0.

**Coming up**

The next two posts in the series will add a forcing term, i.e. *F* > 0 in our differential equation. The next post will look at undamped driven vibrations, and the final post will look at damped driven vibrations.

Off topic, but the

`''`

ticks look odd to me.Kyle: Agreed. But the ticks look worse without the code tag. Then they curl like quotation marks.

John: You should consider using MathJax. It will allow you to use TeX code directly in your posts (they’d even be enclosed by $$ or [ ] depending on configuration), and the math would be rendered right here in a Web native way without requiring special browser support.

There was a beautiful application of mechanical damping invented by Alistair Day, Ove Arup, UK, 1974. You solved the static equilibrium equations of a structure by first allowing it to vibrate, then damping down its oscillations until the structure became static.

http://en.wikipedia.org/wiki/Dynamic_relaxation

John, the link to “the next post” actually links to this post itself.

Adrien: Thanks. I fixed it.

Great Post Thanks!!!