Free vibration of an Undamped Translational System



As mentioned earlier we are going to use the Free body diagram to derive the second order differential equation which describes the motion of the system. The procedure can be summarized as follows:
1)      Select a suitable coordinate to describe the position of the mass or rigid body in the system. Use a linear coordinate to describe the linear motion of a point mass or the centroid of a rigid body, and an angular coordinate to describe the angular motion of a rigid body.
2)      Determine the static equilibrium configuration of the system and measure the displacement of the mass or rigid body from its static equilibrium position.
3)      Draw the free body diagram of the mass or rigid body when a positive displacement and velocity are given to it. Indicate all the active and reactive forces acting on the mass or rigid body.
4)      And finally apply Newton’s second law of motion to the mass or rigid body shown in free body diagram. Newton’s second law of motion can be state as follows :
Rate of change of momentum of a mass is equal to the force acting on it.

 If the mass of the system is displaced at a distance x(t) when acted upon by a resultant force in the same direction, Newton’s second law of motion gives
$$\overrightarrow{F}\left( t \right)=\frac{d}{dt}\left( m\frac{d\overrightarrow{x}\left( t \right)}{dt} \right)$$
If a mass m is constant, this equation reduces to:
$$\overrightarrow{F}\left( t \right)=m\frac{{{d}^{2}}\vec{x}\left( t \right)}{d{{t}^{2}}}=m\ddot{\vec{x}}$$
is the acceleration of the mass. Previous equation can be stated in words as
Resultant force on the mass = mass * acceleration
Where
$$\ddot{\vec{x}}=\frac{{{d}^{2}}\vec{x}\left( t \right)}{d{{t}^{2}}}$$
For a rigid body undergoing rotational motion Newton’s law gives
$$\vec{M}\left( t \right)=J\ddot{\vec{\theta }}$$
Where $$\vec{M}$$  is resultant moment acting on the body and 
$$\ddot{\vec{\theta }}={{{d}^{2}}\theta \left( t \right)}/{d{{t}^{2}}}\;$$  

  and θ are resulting angular displacement and angular acceleration respectively. Equation or represents the equation of motion of the vibrating system.

FIGURE 1 - SPRING MASS SYSTEM

The procedure is now applied to the undamped single-degree of freedom system shown in Fig 1. Here the mass is supported on frictionless rollers and can have translator motion in the horizontal direction. When the mass is displaced a distance +x from its equilibrium position the force in spring is kx, and the free-body diagram of the mass can be represented as shown in fig 1 the application of the 1 to mass m yields the equation of motion.
$$\begin{align} & F\left( t \right)=-kx=m\ddot{x}, \\ & m\ddot{x}+kx=0 \\ \end{align}$$
The initial conditions are:
$$\begin{align} & x(0)={{x}_{0}}, \\ & \dot{x}(0)={{{\dot{x}}}_{0}} \\ \end{align}$$
The assumed solution of previously derived differential equation can be written in the following form
$$x(t)=A\cos {{\omega }_{n}}t+B\sin {{\omega }_{n}}t$$
By applying initial conditions to assumed solution we will determine the constants of integration A and B. After we determine that we can write the assumed solution in the following form
$$x(t)={{x}_{0}}\cos {{\omega }_{n}}t+\frac{{{{\dot{x}}}_{0}}}{{{\omega }_{n}}}\sin {{\omega }_{n}}t$$
As we all know the
$${{\omega }_{n}}=\sqrt{\frac{k}{m}}$$
is the natural frequency of the system.
An alternate assumed solution can be written in the following form:
$$x\left( t \right)=A\sin \left( {{\omega }_{n}}t+\phi \right)$$
By expanding the previous equation using trigonometric identity we will get:
$$\begin{align} & \sin \left( a+b \right)=\sin a\cos b+\cos a\sin b \\ & x\left( t \right)=A\cos \phi \sin {{\omega }_{n}}t+A\sin \phi \cos {{\omega }_{n}}t \\ \end{align}$$
A and ϕ can be determined from the following expressions:
$$\begin{align} & A=\sqrt{x_{0}^{2}+{{\left( \frac{{{{\dot{x}}}_{0}}}{{{\omega }_{n}}} \right)}^{2}}}, \\ & \phi ={{\tan }^{-1}}\left( \frac{{{x}_{0}}{{\omega }_{n}}}{{{{\dot{x}}}_{0}}} \right) \\ \end{align}$$
The free vibration response of a one-degree-of- freedom system is shown in next  figure:

FIGURE 2 - Free vibration response of an undaped one-degree- of-freedom system

The initial conditions determine the energy initially present in the system. Potential energy is continually converted to kinetic energy and vice versa. Since energy is conserved, the system eventually returns to its initial state with its original kinetic and potential energies, completing the first cycle of motion. The subsequent motion duplicates the previous motion. The system takes the same amount of time to execute its second cycle as it does its first. Since no energy is dissipated from the system, the system executes cycles of motion indefinitely. 

            A motion which exactly repeats after some time is said to be period. A period is the amount of time it takes the system to execute one cycle. The frequency is the number of cycles the system executes in a period of time and is the reciprocal of the period.
$$\begin{align} & T=\frac{2\pi }{{{\omega }_{n}}}, \\ & f=\frac{{{\omega }_{n}}}{2\pi } \\ \end{align}$$


Example 1.1.

An engine of mass 500 kg is mounted on an elastic foundation of stiffness 7*10^5N/m. Determine the natural frequency of the system.
Solution:
The system is modeled as a hanging mass-spring system. The natural frequency will be determined using the following expression:
$${{\omega }_{n}}=\sqrt{\frac{k}{m}}=\sqrt{\frac{7\cdot {{10}^{5}}}{500}}=37.4rad/s=5.96Hz$$

Example 2.2



A wheel is mounted on a steel shaft (G=83*10^9 N/m^2) of length 1.5 m and radius 0.80cm. the wheel is rotated 5 degrees and released. The period of oscillation is observed as 2.3.s Determine the mass moment of inertia of the wheel. 

Figure 3 – Wheel mounted on torsional spring (shaft)


Solution:
The oscillations of the wheel about its equilibrium position are modeled as the torsional oscillations of a disk on a massless shaft, as illustrated in previous figure. The differential equation is:
$$\begin{align} & \sum{{{M}_{0}}}=I\ddot{\theta } \\ & -\frac{JG}{L}\theta =I\ddot{\theta } \\ & I\ddot{\theta }+\frac{JG}{L}\theta =0 \\ \end{align}$$
If we divide the previous equation by I we will get:
$$\ddot{\theta }+\frac{JG}{LI}\theta =0$$
The natural frequency of the system can be determined from:
$${{\omega }_{n}}=\sqrt{\frac{JG}{IL}}$$
The natural frequency can be also determined from:
$${{\omega }_{n}}=\frac{2\pi }{T}=\frac{2\pi }{2.3}=2.73rad/s$$
Thus the moment of inertia of the wheel is calculated form:
$$I=\frac{JG}{L\omega _{n}^{2}}=\frac{\frac{\pi }{2}{{\left( 0.008 \right)}^{4}}\left( 83\cdot {{10}^{9}} \right)}{1.5\cdot 2.73}=47.8kg{{m}^{2}}$$

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