Question

A 50-kg machine is placed at the midspan of a $1.5-\mathrm{m}$ simply supported beam of elastic modulus $210 \times 10^9 \mathrm{~N} / \mathrm{m}^2$ and moment of inertia $1.5 \times 10^{-6} \mathrm{~m}^4$. When running at $3000 \mathrm{r} / \mathrm{min}$, the machine's steady-state amplitude is measured as $1.2 \mathrm{~cm}$. Design an undamped absorber such that the steady-state amplitude is less than $2 \mathrm{~mm}$ at all speeds between 2900 and $3100 \mathrm{r} / \mathrm{min}$.

   A 50-kg machine is placed at the midspan of a $1.5-\mathrm{m}$ simply supported beam of elastic modulus $210 \times 10^9 \mathrm{~N} / \mathrm{m}^2$ and moment of inertia $1.5 \times 10^{-6} \mathrm{~m}^4$. When running at $3000 \mathrm{r} / \mathrm{min}$, the machine's steady-state amplitude is measured as $1.2 \mathrm{~cm}$. Design an undamped absorber such that the steady-state amplitude is less than $2 \mathrm{~mm}$ at all speeds between 2900 and $3100 \mathrm{r} / \mathrm{min}$.
 
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Theory and problems of mechanical vibrations
Theory and problems of mechanical vibrations
S. Graham Kelly 1st Edition
Chapter 8, Problem 66 ↓

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5 \times 10^{-6} \mathrm{m}^4 = 315 \times 10^3 \mathrm{N/m} \) \( m \) = mass of the machine = 50 kg Plugging in the values, we get: \[ f_n = \frac{1}{2\pi} \sqrt{\frac{315 \times 10^3}{50}} \] \[ f_n = \frac{1}{2\pi} \times 126.19 \] \[ f_n = 20 \mathrm{Hz} \]  Show more…

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A 50-kg machine is placed at the midspan of a $1.5-\mathrm{m}$ simply supported beam of elastic modulus $210 \times 10^9 \mathrm{~N} / \mathrm{m}^2$ and moment of inertia $1.5 \times 10^{-6} \mathrm{~m}^4$. When running at $3000 \mathrm{r} / \mathrm{min}$, the machine's steady-state amplitude is measured as $1.2 \mathrm{~cm}$. Design an undamped absorber such that the steady-state amplitude is less than $2 \mathrm{~mm}$ at all speeds between 2900 and $3100 \mathrm{r} / \mathrm{min}$.
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Key Concepts

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Beam Dynamics
Beam dynamics encompasses the analysis of the vibrational behavior of beam-like structures using properties like the elastic modulus, moment of inertia, and boundary conditions. In the context of simply supported beams, these parameters help in determining the natural frequencies and mode shapes, which are foundational for predicting how the beam will respond to dynamic loads.
Frequency Tuning
Frequency tuning involves adjusting the parameters, such as mass and stiffness, of a vibration absorber so that its natural frequency matches or offsets an excitation frequency of interest. This alignment is central to maximizing the vibration mitigation between the absorber and the primary structure, ensuring that the system remains effective over a range of operational conditions.
Steady-State Response
The steady-state response of a dynamic system refers to how the system behaves after transient effects have decayed and a constant amplitude is established under a continuous periodic excitation. In engineering design, understanding the steady-state amplitude is crucial for ensuring that structures perform within acceptable limits under normal operating conditions.
Forced Vibration and Resonance
Forced vibration refers to the response of a system when it is subjected to periodic external forces. Resonance occurs when the frequency of the applied force matches a natural frequency of the system, leading to large amplitude vibrations. Understanding this concept is essential for predicting and controlling excessive vibrations in structures under dynamic loads.
Dynamic Vibration Absorber
A dynamic vibration absorber is an auxiliary device attached to a primary structure to mitigate vibrations by introducing a secondary mass-spring system. It is designed to counteract the motion induced by the external force, effectively reducing the amplitude of vibrations at a specific frequency. This technique is critical in engineering to protect structures from potentially harmful oscillations.

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