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Table of Contents



Introduction ................................................................................... 2

The mass-spring-damper ................................................................. 2

System behavior ............................................................................. 3

  Critical damping (ζ = 1) .................................................................. 4

  Over-damping (ζ > 1)..................................................................... 4

  Under-damping (0 ≤ ζ < 1) ............................................................. 4

The equations used ......................................................................... 5

The program created ....................................................................... 6

References...................................................................................... 7
Introduction
In this project we aim to determine

        The (undamped) natural frequency of the system
        The damped frequencyof the system
        The damping ratio
        The rise time
        The settling time
        The percentage overshoot

    By knowing the stiffness of the spring, the damping coefficient and the mass
    which the spring applied to.



The mass-spring-damper
An ideal mass–spring–damper system with mass m, spring constant K and damping
coefficient C is subject to an oscillatory force.




And damping force




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




Where:

        a is the acceleration of the mass
        x is the displacement of the mass relative to a fixed point of reference

Since
Then the following parameters are then defined:




Let




Where:




System behavior
The behavior of the system depends on the relative values of the two fundamental
parameters, the natural frequency ωn 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 as fast as
possible 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.




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




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




The equations used
m=input('the mass=')

k=input('the stifness of the spring=')

c=input('the damping coefficient=')

wn=(k/m)^.5

zeta=c/(2*m*wn)

wd=wn*(1-zeta^2)^0.5

x=atan(sqrt(1-zeta^2)/zeta)

settlingtime=4/(zeta*wn)

risetime=(pi-x)/wd

prcentageovershoot=exp(-zeta*pi/sqrt(1-zeta^2))*100

t=[0:0.01:1];

for j=1:lengthof t

r(j)=1-(((exp(-zeta*wn*t(j))).*sin(wd*t(j)+x))./sqrt(1-zeta^2));



end



plot(t,r)
The program created
References
    mathworks. (n.d.). Retrieved from www.mathworks.com

    wikipedia. (n.d.). Retrieved from www.wikipedia.com

    youtube. (n.d.). Retrieved from www.youtube.com

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Pro

  • 1. Table of Contents Introduction ................................................................................... 2 The mass-spring-damper ................................................................. 2 System behavior ............................................................................. 3 Critical damping (ζ = 1) .................................................................. 4 Over-damping (ζ > 1)..................................................................... 4 Under-damping (0 ≤ ζ < 1) ............................................................. 4 The equations used ......................................................................... 5 The program created ....................................................................... 6 References...................................................................................... 7
  • 2. Introduction In this project we aim to determine The (undamped) natural frequency of the system The damped frequencyof the system The damping ratio The rise time The settling time The percentage overshoot By knowing the stiffness of the spring, the damping coefficient and the mass which the spring applied to. The mass-spring-damper An ideal mass–spring–damper system with mass m, spring constant K and damping coefficient C is subject to an oscillatory force. And damping force Treating the mass as a free body and applying Newton's second law, the total force Ftot on the body is Where: a is the acceleration of the mass x is the displacement of the mass relative to a fixed point of reference Since
  • 3. Then the following parameters are then defined: Let Where: System behavior The behavior of the system depends on the relative values of the two fundamental parameters, the natural frequency ωn 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.
  • 4. 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 as fast as possible 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. 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 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
  • 5. 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 The equations used m=input('the mass=') k=input('the stifness of the spring=') c=input('the damping coefficient=') wn=(k/m)^.5 zeta=c/(2*m*wn) wd=wn*(1-zeta^2)^0.5 x=atan(sqrt(1-zeta^2)/zeta) settlingtime=4/(zeta*wn) risetime=(pi-x)/wd prcentageovershoot=exp(-zeta*pi/sqrt(1-zeta^2))*100 t=[0:0.01:1]; for j=1:lengthof t r(j)=1-(((exp(-zeta*wn*t(j))).*sin(wd*t(j)+x))./sqrt(1-zeta^2)); end plot(t,r)
  • 7. References mathworks. (n.d.). Retrieved from www.mathworks.com wikipedia. (n.d.). Retrieved from www.wikipedia.com youtube. (n.d.). Retrieved from www.youtube.com