Consider a system excited by a harmonic force F1 sin ωt expressed by the matrix equation
Since the system is undamped, the solution can be assumed as
Substituting equation (ii) in equation (i), one obtains
Hence
Hence
(i) Two vectors x1 and x2 are normal if
(ii) Two vectors x1 and x2 are orthogonal if
.
(iii) If x1 and x2 normal and orthogonal, they are called orthonormal, in that case
where is the Kronecker delta, defined by
Tuned Vibration Absorber
Consider a vibrating system of mass m1, stiffness k1, subjected to a force F sin ωt. As studied in case of forced vibration of single-degree of freedom system, the system will have a steady state response given by
which will be maximum when ω = ωn. Now to absorb this vibration, one may add a secondary spring and mass system as shown in figure below
The equation of motion for this system can be given by
As we know for steady state vibration, the system will vibrate with a frequency of the external excitation; we can assume the solution to be
Substituting Equation (3) in equation (2) one may write
Using Cramer's rule one may write
where
Now
Here λ1 and λ2 are the roots of the characteristic equation |Z(ω)| = 0. One may note that these roots are the normal mode frequency for this two-degrees of freedom system. These free-vibration frequencies can be given by
From equation (6), it is clear that,
Hence, if a system called the primary system with a stiffness k1 mass m1 is subjected to an exciting force or base motion to vibrate, it is possible to completely eliminate the vibration of the primary system by suitably designing an attached spring-mass system (secondary system) with stiffness k2 and mass m2 such that the natural frequency of the secondary system coincide with the exciting frequency.
This is the principle of dynamic vibration absorber.
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