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In physics, damping is any effect that tends to reduce the amplitude of oscillations in an oscillatory system, particularly the harmonic oscillator.

In mechanics, friction is one such damping effect. For many purposes the frictional force Ff can be modeled as being proportional to the velocity v of the object:

Ff = −cv,

where c is the viscous damping coefficient, given in units of newton-seconds per meter.

Generally, damped harmonic oscillators satisfy the second-order differential equation:

 \frac{d^2x}{dt^2} + 2\zeta\omega_0\frac{dx}{dt} + \omega_0^2 x = 0,

where ω0 is the undamped angular frequency of the oscillator and ζ is a constant called the damping ratio. For a mass on a spring having a spring constant k and a damping coefficient c, ω0 = k/m and ζ = c/20.

The value of the damping ratio ζ determines the behavior of the system. A damped harmonic oscillator can be:

  • Overdamped (ζ > 1): The system returns (exponentially decays) to equilibrium without oscillating. Larger values of the damping ratio ζ return to equilibrium slower.
  • Critically damped (ζ = 1): The system returns to equilibrium as quickly as possible without oscillating. This is often desired for the damping of systems such as doors.
  • Underdamped (ζ < 1): The system oscillates (with a slightly different frequency than the undamped case) with the amplitude gradually decreasing to zero.

The frequency of the underdamped harmonic oscillator is given by

\omega_1 = \omega_0\sqrt{1 - \zeta^2}.

Contents

Definition

In physics and engineering, damping may be mathematically modelled as a force synchronous with the velocity of the object but opposite in direction to it. If such force is also proportional to the velocity, as for a simple mechanical viscous damper (dashpot), the force F may be related to the velocity v by

 \bold{F} = -c \bold{v} \, ,

Where c is the viscous damping coefficient, given in units of newton-seconds per meter.

This relationship is perfectly analogous to electrical resistance. See Ohm's law.

This force is an approximation to the friction caused by drag.

Example: mass-spring-damper

A mass attached to a spring and damper. The damping coefficient, usually c, is represented by B in this case. The F in the diagram denotes an external force, which this example does not include.

An ideal mass-spring-damper system with mass m (in kilograms), spring constant k (in newtons per meter) and viscous damper of damping coefficient c (in newton-seconds per meter or kilograms per second) is subject to an oscillatory force

F_\mathrm{s} = - k x \,

and a damping force

F_\mathrm{d} = - c v = - c \frac{dx}{dt} = - c \dot{x}.

Treating the mass as a free body and applying Newton's second law, the total force Ftot on the body is

F_\mathrm{tot} = ma = m \frac{d^2x}{dt^2} = m \ddot{x}.

where a is the acceleration (in meters per second squared) of the mass and x is the displacement (in meters) of the mass relative to a fixed point of reference.

Since Ftot = Fs + Fd,

m \ddot{x} = -kx + -c\dot{x}.

This differential equation may be rearranged into

\ddot{x} + { c \over m} \dot{x} + {k \over m} x = 0.\,

The following parameters are then defined:

\omega_0 = \sqrt{ k \over m }
\zeta = { c \over 2 \sqrt{m k} }.

The first parameter, ω0, is called the (undamped) natural frequency of the system . The second parameter, ζ, is called the damping ratio. The natural frequency represents an angular frequency, expressed in radians per second. The damping ratio is a dimensionless quantity.

The differential equation now becomes

\ddot{x} + 2 \zeta \omega_0 \dot{x} + \omega_0^2 x = 0.\,

Continuing, we can solve the equation by assuming a solution x such that:

x = e^{\gamma t}\,

where the parameter γ (gamma) is, in general, a complex number.

Substituting this assumed solution back into the differential equation gives

\gamma^2 + 2 \zeta \omega_0 \gamma + \omega_0^2 = 0 \, ,

which is the characteristic equation.

Solving the characteristic equation will give two roots, γ+ and γ. The solution to the differential equation is thus[1]

 x(t) = Ae^{\gamma_+ t} + Be^{\gamma_- t} \, ,

where A and B are determined by the initial conditions of the system:

 A = x(0)+\frac{\gamma_+x(0)-\dot{x}(0)}{\gamma_--\gamma_+}
 B = -\frac{\gamma_+x(0)-\dot{x}(0)}{\gamma_--\gamma_+}.
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System behavior

Dependence of the system behavior on the value of the damping ratio ζ, for under-damped, critically-damped, over-damped, and undamped cases, for zero-velocity initial condition.

The behavior of the system depends on the relative values of the two fundamental parameters, the natural frequency ω0 and the damping ratio ζ. In particular, the qualitative behavior of the system depends crucially on whether the quadratic equation for γ has one real solution, two real solutions, or two complex conjugate solutions.

Critical damping (ζ = 1)

When ζ = 1, there is a double root γ (defined above), which is real. The system is said to be critically damped. A critically damped system converges to zero faster than any other, and without oscillating. An example of critical damping is the door closer seen on many hinged doors in public buildings. The recoil mechanisms in most guns are also critically damped so that they return to their original position, after the recoil due to firing, in the least possible time.

In this case, with only one root γ, there is in addition to the solution x(t) = eγt a solution x(t) = teγt:[2]

 x(t) = (A+Bt)\,e^{-\omega_0 t} \,

where A and B are determined by the initial conditions of the system (usually the initial position and velocity of the mass):

 A = x(0) \,
 B = \dot{x}(0)+\omega_0x(0) \,

Over-damping (ζ > 1)

When ζ > 1, the system is over-damped and there are two different real roots. An over-damped door-closer will take longer to close than a critically damped door would.

The solution to the motion equation is[3]:

 x(t) = Ae^{\gamma_+ t} + Be^{\gamma_- t}

where A and B are determined by the initial conditions of the system:

 A = x(0)+\frac{\gamma_+x(0)-\dot{x}(0)}{\gamma_--\gamma_+}
 B = -\frac{\gamma_+x(0)-\dot{x}(0)}{\gamma_--\gamma_+}.

Under-damping (0 ≤ ζ < 1)

Finally, when 0 ≤ ζ < 1, γ is complex, and the system is under-damped. In this situation, the system will oscillate at the natural damped frequency ωd, which is a function of the natural frequency and the damping ratio. To continue the analogy, an underdamped door closer would close quickly, but would hit the door frame with significant velocity, or would oscillate in the case of a swinging door.


In this case, the solution can be generally written as[4]:

x (t) = e^{- \zeta \omega_0 t} (A \cos\,(\omega_\mathrm{d}\,t) + B \sin\,(\omega_\mathrm{d}\,t ))\,

where

\omega_\mathrm{d} = \omega_0 \sqrt{1 - \zeta^2 }\,

represents the natural damped frequency of the system, and A and B are again determined by the initial conditions of the system:

A = x(0)\,
B = \frac{1}{\omega_\mathrm{d}}(\zeta\omega_0x(0)+\dot{x}(0)).\,

For an under-damped system, the value of ζ can be found by examining the logarithm of the ratio of succeeding amplitudes of a system. This is called the logarithmic decrement.

Alternative models

Viscous damping models, although widely used, are not the only damping models. A wide range of models can be found in specialized literature, but one of them should be referred here: the so called "hysteretic damping model" or "structural damping model".

When a metal beam is vibrating, the internal damping can be better described by a force proportional to the displacement but in phase with the velocity. In such case, the differential equation that describes the free movement of a single-degree-of-freedom system becomes:

 m \ddot{x} + h x i + k x = 0

where h is the hysteretic damping coefficient and i denotes the imaginary unit; the presence of i is required to synchronize the damping force to the velocity (xi being in phase with the velocity). This equation is more often written as:

 m \ddot{x} + k ( 1 + i \eta ) x = 0

where η is the hysteretic damping ratio, that is, the fraction of energy lost in each cycle of the vibration.

Although requiring complex analysis to solve the equation, this model reproduces the real behaviour of many vibrating structures more closely than the viscous model.

A more general model that also requires complex analysis, the fractional model not only includes both the viscous and hysteretic models, but also allows for intermediate cases (useful for some polymers):

 m \ddot{x} + A \frac{d^r x}{dt^r} i + k x = 0

where r is any number, usually between 0 (for hysteretic) and 1 (for viscous), and A is a general damping (h for hysteretic and c for viscous) coefficient.

See also

References

  1. ^ MathWorld--A Wolfram Web Resource. [1]
  2. ^ Weisstein, Eric W. "Damped Simple Harmonic Motion--Critical Damping." From MathWorld--A Wolfram Web Resource. [2]
  3. ^ Weisstein, Eric W., "Damped Simple Harmonic Motion--Overdamping." from MathWorld.
  4. ^ Weisstein, Eric W. "Damped Simple Harmonic Motion--Underdamping." From MathWorld--A Wolfram Web Resource. [3]

Books

Komkov, Vadim (1972) Optimal control theory for the damping of vibrations of simple elastic systems. Lecture Notes in Mathematics, Vol. 253. Springer-Verlag, Berlin-New York.

External links


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