1. S1-1 SECTION 1 REVIEW OF FUNDAMENTALS

2. S1-2 n This section will introduce the basics of Dynamic Analysis by considering a Single Degree of Freedom (SDOF) problem n Initially a free vibration model is used to describe the natural frequency n Damping is then introduced and the concept of critical damping and the undamped solution is shown n Finally a Forcing function is applied and the response of the SDOF is explored in terms of time dependency and frequency dependency and compared to the terms found in the equations of motion SINGLE DOF SYSTEM

3. S1-3 SINGLE DOF SYSTEM (Cont.) n Consider the System Shown m = mass (inertia) b = damping (energy dissipation) k = stiffness (restoring force) p = applied force u = displacement of mass = velocity of mass = acceleration of mass u,, and p are time varying in general. m, b, and k are constants.

4. S1-4 n Some Theory: u The equation of motion is: u In undamped, free vibration analysis, the SDOF equation of motion reduces to: l Has a solution of the form: l This form defines the response as being HARMONIC, with a resonant frequency of: SINGLE DOF SYSTEM (Cont.)

5. S1-5 UNDAMPED FREE VIBRATION SDOF SYSTEM n For an SDOF system the resonant, or natural frequency, is given by: n Solve for the constants:

6. S1-6 UNDAMPED FREE VIBRATION SDOF SYSTEM (Cont.) n The response of the Spring will be harmonic, but the actual form of the response through time will be affected by the initial conditions: n If there is no response n If response is a sine function magnitude n If response is a cosine function (180 phase change), magnitude n If response is phase and magnitude dependent on the initial values

7. S1-7 SINGLE DOF SYSTEM – UNDAMPED FREE VIBRATIONS n The graph is from a transient analysis of a spring mass system with Initial velocity conditions only Time Disp. k = 100 m = 1 T = 1/f = 0.63 secs T Amp

8. S1-8 DAMPED FREE VIBRATION SDOF n If viscous damping is assumed, the equation of motion becomes: n There are 3 types of solution to this, defined as: u Critically Damped u Overdamped u Underdamped n A swing door with a dashpot closing mechanism is a good analogy u If the door oscillates through the closed position it is underdamped u If it creeps slowly to the closed position it is overdamped. u If it closes in the minimum possible time, with no overswing, it is critically damped.

9. S1-9 DAMPED FREE VIBRATION SDOF (Cont.) n For the critically damped case, there is no oscillation, just a decay from the initial conditions: n The damping in this case is defined as: n A system is overdamped when b > b cr n Generally only the final case is of interest - underdamped

10. S1-10 DAMPED FREE VIBRATION SDOF (Cont.) n For the underdamped case b < b cr and the solution is the form: u represents the Damped natural frequency of the system u is called the (Critical) damping ratio and is defined by: u In most analyses is less than.1 (10%) so

11. S1-11 n The graph is from a transient analysis of the previous spring mass system with damping applied Frequency and period as before Amplitude is a function of damping 2% Damping 5% Damping DAMPED FREE VIBRATION SDOF (Cont.) Time Disp.

12. S1-12 DAMPING WITH FORCED VIBRATION n Apply a harmonic forcing function: u note that is the DRIVING or INPUT frequency n The equation of motion becomes n The solution consists of two terms: u The initial response, due to initial conditions which decays rapidly in the presence of damping u The steady-state response as shown: u This equation is described on the next page

13. S1-13 DAMPING WITH FORCED VIBRATION (Cont.) n This equation deserves inspection as it shows several important dynamic characteristics: At  =  n this term = (2 )^2 and controls the scaling of the response From this is derived the Dynamic Magnification Factor 1/2 This is the static loading and dominates as  tends to 0.0 At  =  n this term = 0.0 With no damping present this results in an infinite response Phase lead of the response relative to the input (see next page) At  >>  n both terms drive the response to 0.0

14. S1-14 n  is defined as a phase lead in Nastran : DAMPING WITH FORCED VIBRATION (Cont.)

15. S1-15 n Summary: u For l Magnification factor 1 (static solution) l Phase angle 360 º (response is in phase with the force) u For l Magnification factor 0 (no response) l Phase angle 180 º (response has opposite sign of force) u For l Magnification factor 1/2  l Phase angle 270 º DAMPING WITH FORCED VIBRATION (Cont.)

16. S1-16 When the Damped system is loaded with an exponential function of a single frequency, the resultant oscillations are called harmonic: HARMONIC OSCILLATIONS

17. S1-17 HARMONIC OSCILLATIONS (CONT.)

18. S1-18 n A Frequency Response Analysis can be used to explore the response of our spring mass system to the forcing function. n This method allows us to compare the response of the spring with the input force applied to the spring over a wide range of input frequencies n It is more convenient in this case than running multiple Transient Analyses, each with different input frequencies n Apply the input load as 1 unit of force over a frequency range from.1 Hz to 5 Hz n Damping is 1% of Critical DAMPING WITH FORCED VIBRATION (Cont.)

19. S1-19 Magnification Factor = 1/2  = 1/G = 50 Static Response = p/k =.01 Peak Response =.5 at 1.59 Hz Note: Use of a Log scale helps identify low order response Displacement Frequency (Hz) DAMPING WITH FORCED VIBRATION (Cont.)

20. S1-20 n There are many important factors in setting up a Frequency Response Analysis that will be covered in a later section n For now, note the response is as predicted by the equation of motion u At 0 Hz result is p/k u At 1.59 Hz result is p/k factored by Dynamic Magnification u At 5 Hz result is low and becoming insignificant n The Phase change is shown here: u In phase up to 1.59 Hz u Out of phase180 Degrees after 1.59 Hz DAMPING WITH FORCED VIBRATION (Cont.)

21. S1-21 n Try a Transient analysis with a unit force applied to the spring at 1.59 Hz n Again damping of 1% Critical is applied n The result is shown on the next page: u The response takes around 32 seconds to reach a steady-state solution u After this time the displacement response magnitude stays constant at.45 units u The theoretical value of.5 is not reached due to numerical inaccuracy (see later) and the difficulty of hitting the sharp peak DAMPING WITH FORCED VIBRATION (Cont.)

22. S1-22 n Transient analysis with a unit force applied to the spring at 1.59 Hz Displacement Time DAMPING WITH FORCED VIBRATION (Cont.)

23. S1-23 n When plotting a input and output at the steady-state period, the input signal is not very accurate – hence our problem finding the exact magnification factor n It is also visible that the phasing between input and output is around 90 degrees as expected at resonance Lead = 0.18 sec (approx) =103 degrees (approx 90) T input = 1/1.59 = 0.629 sec input output DAMPING WITH FORCED VIBRATION (Cont.)

24. S1-24 MSC.Marc and MSC.Patran DOCUMENTATION n MSC.Marc u Volume A u Chapter 5 – “Dynamics” section u Volume E u Chapter 6 – Dynamics u User’s guide u Chapter 3.32 ~ 3.35 n MSC.Patran u MSC.Patran MSC.Marc preference guide