Research Article | Open Access

# Theoretical Analysis and Experimental Verification of Particle Damper-Based Energy Dissipation with Applications to Reduce Structural Vibration

**Academic Editor:**Changjun Zheng

#### Abstract

Particle damping technology can greatly reduce vibration of equipment and structure through friction and inelastic collisions of particles. An energy dissipation model for particle damper has been presented based on the powder mechanics and the collision theory. The energy dissipation equations of friction and collision motion are developed for the particle damper. The rationality of energy dissipation model has been verified by the experiment and the distributions for the energy dissipation of particles versus acceleration are nonlinear. As the experiment process includes lots of factors of energy dissipation, such as the noise and the air resistance, the experimental value is about 7% more than the simulation value. The simulation model can provide an effective method for the design of particle damper. And the particle parameters for damper have been investigated. The results have shown that choosing an appropriate particle density, particle size, and particle filling rate determined based on the simulation model will provide the optimal damping effect for the practical application of particle damping technology.

#### 1. Introduction

Particle damping technology can greatly reduce vibration of equipment and structure by friction and inelastic collisions of particles [1, 2]. This technology has lots of advantages, for example, reduced impact force, simple structure, low costs, small modification of original structure, low additional mass, and good adaptability to a wide temperature range. These unique features provide for broad engineering prospects in aerospace, automobile and precision machinery, and so forth [3, 4].

The mechanism of energy dissipation for particle damping is involved in the mechanical behavior and particulate matter dynamics. The high damping performance in vibration reduction has led to advances through research [5, 6]. Now, the research progress in the field is at an exploratory stage. The research methods are mostly divided into the simulation and the test [7–9]. The simulation method mainly includes the DEM (discrete element method), the regression analysis, and the optimization design [10–17]. Because the nonlinear contact model has a limit on the time step of contact parameters, DEM is inappropriate for large numerical computation when particle number is more than 10^{7} [10]. In fact, the number of particles is always more than 10^{8}, and it hinders the development of DEM. Now, some new methods are introduced into the research [18–23].

When the main structure and the damper are excited, the kinetic energy is dissipated through friction and inelastic collision between particles and damper. On this occasion, the powder mechanics is effective for calculating frictional energy dissipation, and the theory of collision energy is effective for calculating collisional energy dissipation for particle damper, which need less computation.

For the frictional motion, we established a model for particle damper based on powder mechanics, and the frictional energy dissipation was calculated. And for the inelastic collision motion, we established a collision model based on the motion of particles and the damper boundary. Then, the total energy dissipation was calculated, and the simulation results were compared with experimental results. So the simulation model can provide a new analysis method for the practical application of particle damping technology.

#### 2. Model of Frictional Energy Dissipation

The discrete element method can simulate the response of particle and damper with small numbers of particles. The large number of particles in the damper (in excess of 10^{8}) will make the DEM method computationally very demanding. A simple assessment method considering layer’s pressure is of important value in the design of damper with large number of particles.

In this paper, a parameter is introduced to describe the way, where the layer stress of the particles is redirected perpendicularly to its initial load [20].

If the total height of the rectangular particle damper is , we establish a mechanical model. Figure 1 shows the particle layer with infinitesimal thickness . The forces on the particle layer at the vertical direction are balanced bywhere and represent the force of the damper side on the particle layer, represents the force on the lower particle layer, and represents the force on the upper particle layer.

The forces on the particle layer in Figure 1 are given by where represents the gravity of the particle layer, represents the friction coefficient between the inner damper and the particles, represents the Janssen coefficient, represents the stress of the particle layer in the vertical direction, and represents the particle bulk density.

Substituting (2) into (1), the integration can be rewritten as

The distance of adjacent particles from the thinnest to the thickest is given by

During the slippage of particles, on the basis of the energy conservation law, the kinetic energy for particle system will be dissipated due to friction work. As the particle system is under a harmonic excitation, the vibration of particle damper will be reduced.

Assuming the depth of particles is and the filling rate of particle volume is , . It can be concluded that the maximum friction work for particle damper is given bywhere represents the friction coefficient of the particle layer , represents the particle layer number in the damper, , represents the particle diameter, and .

#### 3. Model of Collision Energy Dissipation

In this paper, a model of collision energy dissipation for particle damper is established based on the collision theory.

##### 3.1. The Model of Collision among the Particles

In order to judge the particle position at every moment, the local coordinates of interaction for the particles are established in Figure 2.

Assuming that the mass of particle 1 is and particle 2 is and the radius of particle 1 is and particle 2 is , the position coordinates are, respectively, and . So, the velocities are, respectively, and . The contact condition for particles 1 and 2 is given by

Before the collision of particles, assuming that the velocity of particles 1 and 2 in the local coordinates is and , the equations of the velocity for particle 1 between the original coordinates and local coordinates are given bywhere , , and are the cosine of direction for axis.

After the collision of particles, based on the momentum theorem, the equation for particles 1 and 2 is given by where and are the velocity components for particles 1 and 2 in the local coordinates, is the friction coefficient in two directions, and .

and are given by and .

The symbolic function is written as

Assuming , .

The equation of velocity before and after collision of adjacent particles in local coordinates is given bywhere matrix and matrix are given by

When two particles collide, one particle will move to a new position. After a time step , the new coordinates of position for particle 1 are given by

##### 3.2. The Model of Collision between the Damper and Particles

As the particles keep moving in the damper, the particles collide with the inner damper. The contact between the damper and the particles can be done as the mass-spring-damping system.

Assume that the mass for particle is , and its motion velocity is . The collision process can be divided into two phases “compression and recovery phase” [14]. Assuming that the motion velocity of particle is after the collision, the model of collision is given in Figure 3.

###### 3.2.1. Compression Phase

During the compression phase, based on the theorem of impulse, the equation of impulse is written aswhere is the motion velocity of particle in the tangent and the normal plane before the compression; is the motion velocity of particle in the tangent and the normal plane after the compression; is the impulse of particle in the tangent and the normal plane during the compression phase.

After the compression phase, the component of motion velocity for particle in tangent plane is where the dynamic friction coefficient in the tangent plane is defined by

###### 3.2.2. Recovery Phase

During the recovery phase, the equation of collision impulse is written aswhere is the position of particle in the tangent and the normal plane after the recovery; is the motion velocity of particle in the tangent and the normal plane after the recovery; is the impulse of particle in the tangent and the normal plane during the recovery phase.

The Newton recovery coefficient in the normal plane at the contact area between particle and the damper is defined by

After the recovery phase, the motion velocity for particle in the tangent plane becomes

After a whole collision process , the new coordinates of position for particle are given by

##### 3.3. The Model after Collision with the Inner Damper

After the collision with the inner damper for particle , Figure 4 shows the model of the adjacent particles.

Assuming that the motion velocity of particle 1 is , particle 2 is static during the collision between particle 1 and the inner damper. After the collision with particle 2, based on the momentum theorem, the motion velocity of particle 2 is given by where is the recovery coefficient between particle 1 and particle 2.

In Figure 4, the energy of particle 1 is transferred and attenuated from particle 1 to particle . By the recursion, the motion velocity during the collision of the th particle is given by

Before and after the collision, assume that the motion velocity for the damper is and . The recovery coefficient can be calculated by (17), and the motion velocity is written as

From (22), we can see that the velocity is associated with the particle number, the particle material, the damper material, and the damper velocity before the collision.

As the motion of particle changes, it will access the next step size of time and return to the above process, which calculates the increment of motion for particle again and again. By the iterative calculation, we can achieve the real time motion tracing for every particle.

For the particle damper, the energy dissipation of collision motion is defined aswhere represents the particle number participating collision.

For the damper model, the total energy dissipation of particles is given by

#### 4. Result Analysis and Experimental Verification

##### 4.1. Discussion of Parameters for Friction Model

Assuming that (magnesium oxide to steel), , (magnesium oxide), and g/cm^{3}. Figure 5 shows the variation of the stress with the depth of the particle layer and the ratio of the length to the width () for the particle damper. As the depth increases, the stress of the particle layer intensifies. When the layer depth exceeds a value, the motion amplitude of the whole particle keeps steady. As the particle depth is 1.35 m, the limiting value of the stress is 4752 Pa. This particle layer can bear the weight of the entire particle system. And, as shown in Figure 5, at the same depth of particle layer, with the increase of the ratio for the damper, the stress increases.

Figure 6 shows the effects of layer depth and filling rate on the stress . With the increase of filling rate , the stress at the same depth of particle layer increases. But with the increase of filling rate , the total particle number by frictional motion in the damper below reduces, weakening the damping effect.

##### 4.2. Discussion of Parameters for Collision Model

Figure 7 shows the effects of the particle number and the recovery coefficients on the velocity of adjacent particles. The recovery coefficients of particles are 0.25, 0.45, 0.65, and 0.85. As shown in Figure 7, after collision between particles and damper, the velocity for the adjacent particle drops quickly. A lower recovery coefficient will lead to a greater energy dissipation and damping effect. When the collision is transferred to the seventh particle and is less than 0.65, the particle velocity will drop to 6% initial velocity.

Figure 8 shows the effects of the recovery coefficients and the initial velocity on the energy dissipation . When the initial velocity for particle damper increases, the energy dissipation rises. A higher initial velocity will result in a faster energy attenuation. As the recovery coefficient increases, the damping effect weakens in the particle damper.

##### 4.3. Experimental Verification

The energy dissipation experiment is performed to verify the correctness of the model for particle damping. The shape of experimental damper is a cube, and the damper material is carbon steel, with the dimensions of 150 mm × 150 mm × 400 mm. The schematic plot of experimental system is shown in Figure 9.

The test setup is mainly composed of test components, electromagnetic exciter of JZ-30, acceleration sensors, and signal acquisition analyzer of INV-3118. The electromagnetic exciter produces the excitation signal through two-force bar. The acceleration signal of the damper is acquired by a signal collection and transferred to a signal analyzer. The sampling number per cycle is more than 500 and the experimental process is repeated 4 times. The excitation signal of the electromagnetic vibrator JZ-30 is the sine wave.

In this experiment, the energy dissipation for particles is written aswhere represents the energy dissipation for particles in this experiment, represents the excitation work of damper which could be calculated by the force gauge, and represents the kinetic energy which could be calculated by the acceleration sensor.

The photograph of this experimental system is shown in Figure 10.

Firstly, the aluminum oxide, the stainless steel, and the tungsten carbide are used for experimental material. The densities of the three materials are, respectively, 3.4 g/cm^{3}, 7.9 g/cm^{3}, and 18.4 g/cm^{3} with 85% volume filling rate and 4 mm particle size. The results showing the energy dissipation versus acceleration distributions for the simulation and experiment are shown in Figure 11 under the three densities of particle. The distributions for the energy dissipation of particles versus acceleration are nonlinear. For the low density of particle, the energy dissipation is less than the high density of particle. As the particle density increases, the damping effect rises, and the vibration attenuation of the tungsten carbide particle material is optimal in the experiment.

From Figure 11, the distributions of the energy dissipation for the simulation and test are in good agreement, and the experimental values of energy dissipation are slightly more than the simulation results. It verifies the rationality for the theoretical model of particle damper. As the experiment process includes lots of factors of energy dissipation, such as the noise and the air resistance, the experimental value is about 7% more than the simulation value. So, for the design process of particle damper, the simulation model can provide an effective method to choose an appropriate particle density.

Secondly, in order to investigate the effect of particle size and exciting acceleration on the energy dissipation, the stainless steel is used for experimental material with 85% volume filling rate. The experimental results showing the energy dissipation versus acceleration distributions for the different particle size are shown in Figure 12. As the particle size increases from 1 mm to 5 mm, the energy dissipation rises greatly. And as the particle size increases from 5 mm to 7 mm, the energy dissipation drops. So we can draw the conclusion that there is an optimum particle size for vibration attenuation of a structure. In this experiment, the 5 mm particle size is the best for stainless steel ball. One reason for this result is that there is the adhesion among the too small particle size; and another reason is that too large particle size will result in fewer chances for friction and collision, which will decrease the vibration attenuation of an exciting structure. So, for the design process of particle damper, choosing an appropriate particle size determined based on the simulation model is important.

Thirdly, in order to investigate the effect of particle filling rate and exciting acceleration on the energy dissipation, the stainless steel is used for experimental material 4 mm particle size. The experimental results showing the energy dissipation versus acceleration distributions for the different particle filling rate are shown in Figure 13.

As there is no particle in the damper, the energy dissipation value is nearly zero. And as the particle filling rate increases to 90%, the energy dissipation values rise. However, as the particle filling rate exceeds 90%, the energy dissipation values begin to drop. So we can see that there is an optimum particle filling rate for damping effect. In this experiment, the 90% particle filling rate is the best for stainless steel ball of 4 mm particle size. The main reason for this result is that there is less clearance of particle motion in the damper for too much particle, which will decrease the damping effect of an exciting structure. So, choosing an appropriate particle filling rate based on the simulation model will provide for the practical application of particle damping technology.

#### 5. Conclusions

An energy dissipation model for particle damper has been established based on the powder mechanics and the collision theory. The equations of friction energy dissipation and collision energy dissipation are developed for the particle damper. Through the experiment, the rationality of energy dissipation model is verified and the important parameters of particle damping have been investigated, such as the particle density, the particle size, and the particle filling rate.

The distributions for the energy dissipation of particles versus acceleration are nonlinear. For the low density of particle, the energy dissipation is less than the high density of particle. As the particle density increases, the damping effect rises, and the vibration attenuation of the tungsten carbide particle material is optimal in the experiment.

As the particle size increases from 1 mm to 5 mm, the energy dissipation rises greatly, and as the particle size increases from 5 mm to 7 mm, the energy dissipation drops. In this experiment, the 5 mm particle size is the best for stainless steel ball.

As the particle filling rate increases to 90%, the energy dissipation values rise. However, as the particle filling rate exceeds 90%, the energy dissipation values begin to drop. In this experiment, the 90% particle filling rate is the best for stainless steel ball of 4 mm particle size.

For the design process of particle damper, choosing an appropriate particle density, particle size, and particle filling rate determined based on the simulation model will provide the optimal damping effect for the practical application of particle damping technology.

#### Conflict of Interests

The authors declare that there is no conflict of interests regarding the publication of this paper.

#### Acknowledgments

The authors would like to acknowledge financial support from National Natural Science Foundation of China (no. 51205382) and the Fundamental Research Funds for the Central Universities, Xiamen University (no. 20720150094), and Collaborative Innovation Center of High-End Equipment Manufacturing in Fujian.

#### References

- X.-M. Bai, B. Shah, L. M. Keer, Q. J. Wang, and R. Q. Snurr, “Particle dynamics simulations of a piston-based particle damper,”
*Powder Technology*, vol. 189, no. 1, pp. 115–125, 2009. View at: Publisher Site | Google Scholar - K. Li and A. P. Darby, “Experiments on the effect of an impact damper on a multiple-degree-of- freedom system,”
*Journal of Vibration and Control*, vol. 12, no. 5, pp. 445–464, 2006. View at: Publisher Site | Google Scholar - Z. Lu, X. Lu, and S. F. Masri, “Studies of the performance of particle dampers under dynamic loads,”
*Journal of Sound and Vibration*, vol. 329, no. 26, pp. 5415–5433, 2010. View at: Publisher Site | Google Scholar - M. R. Duncan, C. R. Wassgren, and C. M. Krousgrill, “The damping performance of a single particle impact damper,”
*Journal of Sound and Vibration*, vol. 286, no. 1-2, pp. 123–144, 2005. View at: Publisher Site | Google Scholar - B. M. Shah, D. Pillet, X. M. Bai, L. M. Keer, Q. Jane Wang, and R. Q. Snurr, “Construction and characterization of a particle-based thrust damping system,”
*Journal of Sound and Vibration*, vol. 326, no. 3–5, pp. 489–502, 2009. View at: Publisher Site | Google Scholar - H. V. Panossian, “Non-obstructive particle damping tests on aluminum beams,” in
*Proceedings of the Damping 91 Conference*, pp. 13–17, San Diego, Calif, USA, 1991. View at: Google Scholar - D. Guyomar and A. Badel, “Nonlinear semi-passive multimodal vibration damping: an efficient probabilistic approach,”
*Journal of Sound and Vibration*, vol. 294, no. 1-2, pp. 249–268, 2006. View at: Publisher Site | Google Scholar - A. R. Jem and R. T. Geoffrey, “Amplitude dependent behaviour in the application of particle dampers to vibrating structures,”
*Proceedings of the 46th AIAA/ASME/ASCE/AHS/ASC Structures, Structural Dynamics, and Materials Conference*, pp. 18–21, 2005. View at: Google Scholar - C. H. Lamarque and O. Janin, “Modal analysis of mechanical systems with impact non-linearities: limitations to a modal superposition,”
*Journal of Sound and Vibration*, vol. 235, no. 4, pp. 567–609, 2000. View at: Publisher Site | Google Scholar - B. K. Mishra and C. V. R. Murty, “On the determination of contact parameters for realistic DEM simulations of ball mills,”
*Powder Technology*, vol. 115, no. 3, pp. 290–297, 2001. View at: Publisher Site | Google Scholar - J. Chen, L.-B. Wang, and X.-M. Huang, “Micromechanical modeling of asphalt concrete fracture using a user-defined three-dimensional discrete element method,”
*Journal of Central South University*, vol. 19, no. 12, pp. 3595–3602, 2012. View at: Publisher Site | Google Scholar - S. T. Nase, W. L. Vargas, A. A. Abatan, and J. J. McCarthy, “Discrete characterization tools for cohesive granular material,”
*Powder Technology*, vol. 116, no. 2-3, pp. 214–223, 2001. View at: Publisher Site | Google Scholar - Z.-Y. Xie and J.-X. Feng, “Numerical analysis of behavior of active layer in rotary kilns by discrete element method,”
*Journal of Central South University*, vol. 20, no. 3, pp. 634–639, 2013. View at: Publisher Site | Google Scholar - B. M. Shah, J. J. Nudell, K. R. Kao, L. M. Keer, Q. J. Wang, and K. Zhou, “Semi-active particle-based damping systems controlled by magnetic fields,”
*Journal of Sound and Vibration*, vol. 330, no. 2, pp. 182–193, 2011. View at: Publisher Site | Google Scholar - K. S. Marhadi,
*Particle impact damping: influence of material and size [Master's thesis]*, Texas A&M University, 2003. - Y. Y. Michael,
*Development of master design curves for particle impact damper [Ph.D. thesis]*, Pennsylvania State University, 2003. - A. R. Jem and G. R. Tomlinson, “Amplitude dependent behaviour in the application of particle dampers to vibrating structures,” in
*Proceedings of the 46th AIAA/ASME/ASCE/AHS/ASC Structures, Structural Dynamics & Materials Conference*, vol. 10, pp. 6433–6441, Austin, Tex, USA, April 2005. View at: Google Scholar - C. Shi, S. N. Wang, L. Liu, Q. X. Meng, and Q. Zhang, “Mesomechanical simulation of direct shear test on outwash deposits with granular discrete element method,”
*Journal of Central South University*, vol. 20, no. 4, pp. 1094–1102, 2013. View at: Publisher Site | Google Scholar - D. I. Ryzhkov, “Vibration damper for metal cutting,”
*The Engineer's Digest*, vol. 14, pp. 246–251, 2003. View at: Google Scholar - W. Liu, G. R. Tomlinson, and J. A. Rongong, “The dynamic characterisation of disk geometry particle dampers,”
*Journal of Sound and Vibration*, vol. 280, no. 3–5, pp. 849–861, 2005. View at: Publisher Site | Google Scholar - L. Wu and F.-Z. Qu, “Discrete element simulation of mechanical characteristic of conditioned sands in earth pressure balance shield tunneling,”
*Journal of Central South University of Technology*, vol. 16, no. 6, pp. 1028–1033, 2009. View at: Publisher Site | Google Scholar - G. B. Gong and X. X. Zha, “DEM simulation of liquefaction for cohesionless media at grain scale,”
*Journal of Central South University*, vol. 19, no. 9, pp. 2643–2649, 2012. View at: Publisher Site | Google Scholar - K. Mao, M. Y. Wang, Z. Xu, and T. Chen, “DEM simulation of particle damping,”
*Powder Technology*, vol. 142, no. 2-3, pp. 154–165, 2004. View at: Publisher Site | Google Scholar

#### Copyright

Copyright © 2015 Wangqiang Xiao et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.