Engineering Acoustics. Malcolm J. Crocker
Чтение книги онлайн.
Читать онлайн книгу Engineering Acoustics - Malcolm J. Crocker страница 31
Here ωd is known as the damped “natural” angular frequency:
(2.15)
where ωn is the undamped natural frequency
Figure 2.7 Motion of a damped mass–spring system, R < (4MK)1/2.
The amplitude of the motion decreases with time unlike that for undamped motion (see Figure 2.3). If the damping is increased until R equals (4MK)1/2, the damping is then called critical, Rcrit = (4MK)1/2. In this case, if the mass in Figure 2.6 is displaced, it gradually returns to its equilibrium position and the displacement never becomes negative. In other words, there is no oscillation or vibration. If R > (4MK)1/2, the system is said to be overdamped.
The ratio of the damping constant R to the critical damping constant Rcrit is called the damping ratio δ:
(2.16)
In most engineering cases, the damping ratio, δ, in a structure is hard to predict and is of the order of 0.01–0.1. There are, however, several ways to measure damping experimentally [8, 9].
Example 2.3
A 600‐kg machine is mounted on springs such that its static deflection is 2 mm. Determine the damping constant of a viscous damper to be added to the system in parallel with the springs, such that the system is critically damped.
Solution
The static deflection is given by Eq. (2.8a) as d = Mg/K. Therefore K = Mg/d = 600(9.8)/2 × 10−3 = 294 × 104 N/m. The system is critically damped when the damped constant Rcrit = (4MK)1/2 = (4 × 600 × 294 × 104)1/2 = 84 000 Ns/m.
(c) Forced Vibration – Damped
If a damped spring–mass system is excited by a simple harmonic force at some arbitrary angular forcing frequency ω (see Figure 2.8), we now obtain the equation of motion Eq. (2.17):
Figure 2.8 Forced vibration of damped simple system.
The force F is normally written in the complex form for mathematical convenience. The real force acting is, of course, the real part of F or |F| cos(ωt), where |F| is the force amplitude.
If we assume a solution of the form y = A ejωt then we obtain from Eq. (2.17):
(2.18)
We can write A = |A| ejα, where α is the phase angle between force and displacement. The phase, α, is not normally of much interest, but the amplitude of motion |A| of the mass is. The amplitude of the displacement is
(2.19)
This can be expressed in alternative form:
Equation (2.20) is plotted in Figure 2.9. It is observed that if the forcing frequency ω is equal to the natural frequency of the structure, ωn, or equivalently f = fn, a condition called resonance, then the amplitude of the motion is proportional to 1/(2δ). The ratio |A|/(| F|/K) is sometimes called the dynamic magnification factor (DMF). The number |F|/K is the static deflection the mass would assume if exposed to a constant nonfluctuating force |F|. If the damping ratio, δ, is small, the displacement amplitude A of a structure excited at its natural or resonance frequency is very high. For example, if a simple system has a damping ratio, δ, of 0.01, then its dynamic displacement amplitude is 50 times (when exposed to an oscillating force of |F| N) its static deflection (when exposed to a static force of amplitude |F| N), that is, DMF = 50.
Figure 2.9 Dynamic magnification factor (DMF) for a damped simple system.
Situations such as this should be avoided in practice, wherever possible. For instance, if an oscillating force is present in some machine or structure, the frequency of the force should be moved away from the natural frequencies of the machine or structure, if possible, so that resonance is avoided. If the forcing frequency f is close to or coincides with a natural frequency fn, large amplitude vibrations can occur with consequent vibration and noise problems and the potential of serious damage and machine malfunction.
The force on the idealized damped simple system will create a force on the base