|
|
|
A simple vibration isolation system is
itself a resonant structure. It can be
effective at high frequencies (along one direction), but it amplifies the
vibration at, and below its resonant frequency. Moreover, the isolation system’s dimensions
must accommodate large displacements at low frequencies and high
accelerations.
|
|
For sinusoidal vibration, the vibration
displacement d = dosin 2ft, and the acceleration
a = -do(2f)2 sin 2ft, where do is the peak displacement and f is
the vibration frequency. Therefore, do
= 0.50 G/f2 meters, peak-to-peak, where G is the acceleration in
units of g. For example, the peak-to-peak displacement at 1 Hz and 1 g is 0.5
meters.
|
|
Acoustic noise can be especially
troublesome in certain applications.
For example, when an extremely low noise oscillator was required in an
aircraft radar application, after the system designers built a three-level
vibration isolation system to isolate the oscillator from the vibration of
the aircraft, they discovered that the isolation system failed to deliver the
expected phase noise of the oscillator because the isolation system failed to
deal with the acoustic noise in the aircraft; i.e., the isolation system was
effective in isolating the oscillator from the vibrations of the airframe,
but it was ineffective in blocking the intense sound waves that impinged on
the oscillator.
|
|
|
|
|
|
J. R. Vig, C.
Audoin, L. S. Cutler, M. M. Driscoll, E. P. EerNisse, R. L. Filler, R. M.
Garvey, W. L. Riley, R. C. Smythe, and R. D. Weglein, "Acceleration,
Vibration and Shock Effects - IEEE Standards Project P1193," Proc. 1992
IEEE Frequency Control Symposium, 763-781, 1992; also, The Effects of
Acceleration on Precision Frequency Sources, U. S. Army Laboratory
Command Research and Development Technical Report SLCET-TR-91-3, March 1991,
AD-A235470.
|