Printer Friendly

Development of electromagnetic damper.

This paper presents the development of an electromagnetic

damper on proposed system of three stages of

damping. Mechanical design, control system and control

algorithm was developed for EMD. Control algorithm for

EMD was explained by considering feedback system, and

choosing control elements, sensor. Investigation was done

regarding the three stages of damping. Based on the experimental

setup theoretical evaluations as well as finite element

modelling was done. The possible application of

proposed EMD is mentioned in this paper.

Keywords: electromagnetic damper (EMD), eddy current

damping, magnetic levitation, magnetic repulsion, solenoid.

1. Introduction

Mechanical vibration may be caused by force whose magnitude or direction or point of application varies with time. Vibration deals with force and motion, therefore it can be considered as subfield of dynamics. In some cases resulting vibrations may be of no consequences, in others they may be disastrous. Vibration may be undesirable because they can result in deflection of sufficient magnitude to lead to malfunction [1-3].

To reduce the impact of vibration force, damping is provided. The energy dissipation properties of material or a system under cyclic stress is known as damping [1-3]. Dampers are essential in reducing the vibration transmitted to a body. Dampers can be classified as passive and semi-active dampers [1-3]. Hydraulic damper comes under passive dampers [4]. Magnetorheological (MR) damper and electromagnetic dampers are classified under semi-active dampers [5-9].

The magnetic flux from electromagnet (EM) can be controlled by varying the current passing through electromagnet [10-12]. This type of electromagnet can be implemented in several fields of application in day to day life [13-14]. Currently there exist many damping devices which work under the principal of electromagnetism. Various research and development are ongoing related to electromagnetic damping [10-18].

The idea of combination of three stages of damping, explained in this paper, was obtained from the principles of eddy current damping [11] (Fig. 1), the adaptive magnetic levitation system [19] (Fig. 2) and the working of shunt damping [20-28].

From the investigation of existing dampers and taking into consideration, constructing a damper which is easy to construct, adaptive and cost-efficient, a device is proposed in this paper, where three stages of damping (Fig. 3) are combined to make an effective damping and to sustain a shock (vibration force) ranging from 10 to 50 N. The proposed technology can be used to replace the existing packing methods like bubble wraps, package cushioning for fragile items, there by helps to provide a more reliable and real-time damping system. The wall of shock absorbing box can be constructed using the proposed EMD as shown in Fig. 4. The force transmitted from external wall of the box to the interior wall of the box will be reduced (damped) by the small units of EMD, which is placed in between the walls. The idea and work for future development are innovative and can be applicable in transportation, medical and industrial fields.

Proposed working principle of electromagnetic damper (EMD) is shown in Fig. 5. Stage-1 damping is obtained due to the effect of eddy current formation, when the piston with the magnets moves through copper pipe (Fig. 5). Stage-2 damping is obtained when the magnet enters the region of solenoid setup and starts to levitate and there by resist the downward movement of magnet (Fig. 5). When the force acting on the piston is larger, then magnetic levitation breaks and piston moves downward. To resist the downward movement of the piston stage-3 damping is provided, in which the electromagnet is used to repel the permanent magnet upward (Fig. 5)

2. Mathematical modelling of damper system

For better understanding of the prototype and based on required design parameters and to find out the excitation of force from base to top platform, a mathematical modelling was done for a damper system with single degree of freedom.

If the spring supplies a restoring force proportional to its elongation and the dashpot (electromagnetic damper) provides a force which opposes motion of the mass proportional to its velocity, then the system response is proportional to the excitation, and the system is said to be linear [29, 30]. Therefore the mathematical model developed will be linear single degree of freedom system.

Base motion of a damper system with a single degree of freedom is shown in the Fig. 6, in which K is the spring constant of spring and c is the damping coefficient.

The modelling of spring was done as per the prototype and some assumptions were made. These are summarised in Table 1. The shaded sections are the values assumed and the other values were determined as per the calculation using respective formulas [29, 30].

The above results are applied in proposed model of single degree of freedom system.The system is shown in Fig. 7.

Consider y(t) represents the motion of the base center, the base is subjected to external forces as shown in Fig. 7. The vertical motion X of top platform, is determined from [30]:


The 14 mm excitation of base is transmitted as magnitude of oscillation, [absolute value of X] = 7.544 mm to the top platform of mass M (1 kg). This amplification occurs because the assumption forcing frequency (1 Hz) is near the suspension's natural frequency (0.39 Hz).

A graph between top platform's responses, X, to forcing frequencies r, obtained using MATLAB (Fig. 8).

3. Investigation on three stages of damping and results

Stage-1 damping. Stage-1 damping is obtained by Eddy current damping. Eddy currents are generated in a conductor in a time-varying magnetic field [31]. They are induced either by the movement of the conductor in the static field or by changing the strength of the magnetic field, initiating motional and transformer electromotive forces, respectively. Since the generated eddy currents create a repulsive force that is proportional to the velocity of the conductor, the moving magnet and conductor behave like a viscous damper. The diagrammatic representation of the magnet falling through the metal pipe is shown in Fig. 9.

The stage-1 is investigated by the free fall of Neodymium magnet of 20 mm diameter and 0.2 mm thick through copper pipe 160 mm long and 28 mm diameter. The results of observations are given in Table 2.

From Table 2 it is clear that when the magnetic field of magnet is increased, then the time taken by the magnet to cover 160 mm length copper pipe in freefall also increases. This states that, when magnetic field of permanent magnet increases, the Eddy current induced in the copper pipe also increases there by providing a damping effect.

Modelling of stage-1 damping. To justify the above experiment, modelling of free fall of magnet through copper pipe was done using COMSOL Multuphysics. Simulation of the magnetic flux density formed inside the copper pipe at time t = 50 ms from the start of free fall of magnet inside the copper pipe is shown in Fig. 10.

Simulation of the current density (Eddy current) formed when the magnet moves and reaches the centre of the copper pipe (time t = 50 ms) is shown in Fig. 11.

The effect of Eddy current damping can be explained using the gradual increases, in case of Lorentz force and velocity and after a time 50 ms both become constant, in the case of magnet falling freely inside a copper pipe. Whereas the acceleration reduces and become constant. The respective cases can be justified using the graph obtained from the modelling of stage-1 experiment (Figs. 12, 13 and 14).

Stage-2 damping. For stage-2 damping, different types of solenoids were constructed and tested, in order to understand the nature of magnetic field formed inside the solenoid. Each types differ from each other by number of windings, number of layer of windings, combination of magnetic poles on coil, by varying the current through coil and making of split coils. Among this a simple solenoid construction with number of windings N (90), with 2 layers and length of solenoid L (50 mm) was chosen.

The main objective of stage-2 investigation is to study the nature of behaviour of magneticfield inside the solenoid by determining the magnetic field thoriticaly as well as from modelling and observe the nature of a permenent magnet levitating inside the solenoid.

Solenoid is a long straight coil of wire that can be used to generate a nearly uniform magnetic field similar to that of a bar magnet (Fig. 15) [32]. The field can be greatly strengthened by the addition of an iron core.

At the centre of a long solenoid, the magnetic field is [32]:

B = [mu]nl. (1)

From Eq. (1) for the magnetic field B, n is the number of turns per unit length (turn's density), I--current passing through the wire, [mu] is the permeability ([mu] = k ([[mu].sub.0] and [[mu].sub.0] = 4[pi]x[10.sup.-7] H [m.sup.-1)], k is relative permeability of core. The core used here is a copper pipe. Permeability of copper pipe is 0.999994 (permeability of air is 1.00000037 [33]).

Hence value of k is taken to be 1 for theoretical experiment and also for finite element modelling. The turn density is denoted as n = N/L, where N is number of turns and L is length of solenoid.

A simple solenoid was constructed with coper pipe of 0.2 mm thick as the core and the number of turns (winding of insulated copper wire) N (90) and length of solenoid L (50 mm) was made (Fig. 16).

Experimental setup is shown in Fig. 16. The value of magnetic field at the centre of the solenoid is determined theoretically using Eq. (1). Theoretically the expected magnetic field B is calculated as 2.261946711 x [10.sup.-3] T.

Modelling of stage-2 damping. The modelling of above experimental setup is done using the software Vizimag. Magnetic field line representation and magnetic flux density of at the centre of solenoid is shown in figure Fig. 17. The maximum flux density [B.sub.max], force around solenoid P due to magnetic field and magnetic field density at the centre of the core B obtained from modelling of stage-2 setup is shown in Table 3.

To know the nature of levitation inside solenoid a piece of neodymium magnet was allowed to fall freely through solenoid setup. It was observed that the neodymium magnet was able to levitate inside the solenoid; this is shown in Fig. 18, a and schematic drawing of magnet aligning inside the solenoid is shown in Fig. 18, b.

For an extra external force while magnet falls freely, a 12 g of weight (e.g.: bolt) which is equivalent 1.18 N on free fall is attached to the magnet. For an extra external force during the free fall of magnet a weight is attached with single disc magnet is shown in Fig. 19, a and with multiple magnets is shown in Fig. 19, b.

It was observed that the magnet with extra weight was able to levitate. As the magnets increased the strength of levitation also increased. On varying external force acting on the levitating unit (the magnet with attached weight), was able to reciprocate.

Stage-3 damping is provided by magnetic repulsion between the edges of solenoid and magnet. Simple solenoid construction with coper pipe of 0.2 mm thick and outer diameter 18 mm is used as inner core of solenoid 2. The number of turns N (90) and length of solenoid is L (50 mm).The solenoid setup is as shown in Fig. 20.

There is a magnetic field produced inside the solenoid which is theoretically determined from Eq. (1). Theoretically the expected magnetic field B is calculated as 2.261946711 x [10.sup.-3] T.

Modelling of stage-3 damping. The magnetic field line representation and magnetic flux density of stage-3 damping system is shown in Fig. 21. The maximum flux density [B.sub.max], Force around solenoid P due to magnetic field and magnetic field density at the centre of the core B obtained from modelling of stage-3 setup is shown in Table 4.

Fig. 22 illustrate the experimental setup of stage-3 damping. Fig. 22, a shows that the magnet repels when south pole of magnet comes in contact with south pole of solenoid. Fig. 22, b shows that when north pole of magnet come in contact with south pole of solenoid both unit get attracted and rests over the solenoid. For stage-3 damping we will be using experimental setup as shown in Fig. 22, a.

4. Design and prototyping of EMD

4.1. Design of proposed EMD

The design of the proposed EMD is shown in Fig. 23. The EMD is placed between load acting platform and a base. The main part of the construction consists of the spring, neodymium magnet and solenoid setup. The other parts are: piston (which connects the load acting platform and the magnet arrangement), spring holder and a coupling (which helps to couple the solenoid 1 and the outer cover of the solenoid 2).

Parts are shown in Fig. 23. It consists of two solenoids: solenoid 1 made from copper pipe of 28 mm diameter and 100 mm length and solenoid 2 made from copper pipe of 18 mm diameter and 50 mm length. A spring of outer diameter 27 mm, 7 units of permanent magnet, 90 mm long piston which holds the permanent magnet, outer cover of solenoid 2, coupling for coupling two solenoid section and a spring holder.

4.2. Control system of proposed EMD

The control system for EMD is shown in Fig. 24. The purpose of the control system is to sense the distance between two walls (platform where the load acts and the base), and there by activate the solenoids to resist the frequent and sudden downward movement of permanent magnets. When the distance between the walls varies, it is detected by the proximity sensor. The output from proximity sensor is send to microcontroller in the form of analogue signals. Micro controller is programmed in such a way that it produces output signal to the driver module board to activate solenoid 1 and solenoid 2 respectively (Fig. 24).

The microcontroller will be programmed to emit digital signal to the controller according to the distance diagram in Fig. 25. The signal will be adjusted using feedback signals from the proximity sensors. Driver act as a digital-to-analogue signal convertor. The process continues as long as there will be force acting on the system. Initially the distance between the platform where load act and sensor is read and when the sensor reads distance between the regions a solenoid 1 is activated and when sensor reading is between b solenoid 2 is activated. The parameters a and b depends on the placing of sensor module.

The control system is supported by a feedback system as shown in Figs. 26 and 27. Considering a simple system characterized by a single variable L which represents the distance between base and load acting platform. Under normal conditions the system has a steady state value of L=[L.sub.0] which may vary somewhat over time due to the variation of force acting f on the load acting platform which cannot be measured or are unaware. To rectify the variation in the value of L as a result of varying force a mechanism for measuring the state of the system as well as a control input i, with which can be used to modify the state L of the system. In summary, the system has the following functional form L (i; f; t). Fig. 26 shows a block diagram of the relationship between the system, the variables i and f, and the measurement of the system state L. Created according to feedback and PID control theory [34].

Fig. 27 illustrates the block diagram of system with the feedback loop. In which an unknown force f modifies the distance between two wall L and a new value for the distance between the walls [L.sub.d]. An error e is calculated by taking the difference between L and [L.sub.d]. The input which is a function of error e, calculates the error and send it to the controller to modify L.

Final assembly (Fig. 28) shows the complete setup of proposed EMD. This consists of the EMD device (assembled EMD), micro controller module with driver module, digital sensor module, external power supply and LED lights.

5. Conclusions

In this paper an adaptive and semi active EMD is developed, by implementing proposed idea of combination of three stages of damping. The proposed EMD can be used to damp forces between 10-50 N and one of its major application is in developing a shock absorbing box, which can be used for the transportation of fragile and valuable materials.

Mathematical modelling of damper system (single-degree-of-freedom system) for the proposed system was modelled. It was observed that an excitation of 14 mm on the base of system is transmitted as 7.554 mm on top platform. Based on this modelling, a damper was constructed by implementing the three stages of damping which includes the technology of electromagnets and permanent magnet.


[1.] Russell Richards. 2007. Comparison of Linear, Nonlinear, Hysteretic, and Probabilistic MR Damper Models. Master project, Virginia Polytechnic Institute and State University. 99p, [online] [accessed 15 February-2014]. Internet source:

[2.] Ragelio Palomera Arias. 2005. Passive Electromagnetic Damping device for motion control of building structures. Doctor of Philosophy in Architecture: Building Technology. Massachusetts Institute of Technology.146p.

[3.] David, I. G. Jones. 2001. Handbook of Visco-elastic Vibration Damping.- John Wiley & Sons Ltd. 389p.

[4.] Masi, J.W. 2001. Affective of Control Techniques on the Performance of Semiactive Dampers. Master of Science Project: Department of Mechanical Engineering, Virginia Tech. 184p.

[5.] Lord Corporation .Rheonetic[TM] MR Damper RD-10053 [online] [accessed 15 August 2014]. Internet source:

[6.] Simon, D. 2001. Investigation of the Effectiveness of Skyhook Suspension for Controlling Roll Dynamics of Sport Utility Vehicles using Magneto-Rheological Dampers, Ph.D. Dissertation: Department of Mechanical Engineering, Virginia Tech. 202p. http://scholar. lib .vt. edu/theses/available/etd-12032001202230.

[7.] Ma, X.Q.; Wang, E.R.; Rakheja, S.; Su, C.Y. 2002. Modeling hysteretic characteristics of MR fluid damper and model validation. Proceedings of the 41st IEEE Conference on Decision and Control. Las Vegas, NV.

[8.] Spencer, B,F.; Dyke, SJ.; Sain, M,K.; Carlson, J,D. Phenomenological model for a magnetorheological damper, J. Eng. Mech. Am. Soc. Civil Eng. 123: 230-252.

[9.] Dominguez, A.; Sedaghati, R.; Stiharu. I. 2004. Modeling the hysteresis phenomenon of megnetorheological dampers, Smart Materials and Structures 13: 1351-1361p.

[10.] Wen-ai, Shen; Songye, Zhu; You-lin, Xu. 2012. An experimental study on self-powered vibration control and monitoring system using electromagnetic TMD and wireless sensors, Sensors and Actuators A 180: 166-176.

[11.] Ebrahimia, Babak; Khameseea, Mir Behrad; Golnaraghi, M. Farid. 2008 Design and modeling of a magnetic shock absorber based on eddy current damping effect, Journal of Sound and Vibration 315(45): 875-889.

[12.] Alanoly, J.; Sankar, S. 1986. A new concept in semiactive vibration isolation, ASME Design Engineering Technical Conference 86-DET-28: 291-309.

[13.] Arsem, H.B. 1971. Electric shock absorber, US. Patent Number 3559027 .

[14.] Aspinall, D.T.; Oliver, R.J. 1964. Vehicle riding comfort: the correlation between subjective assessments of vehicle ride and physical measurements of vehicle motion, Publisher: Motor Industry Research Association report.

[15.] Bae, J.S.; Kwak, M.K.; Inman, D.J. 2005 Vibration suppression of cantilever beam using eddy current damper, Journal of Sound and Vibration 284(3-5): 805-824.

[16.] Barak, P. 1992. Passive versus active and semi-active suspension from theory to application in north American industry, SAE Technical Paper 922140.

[17.] Bernard, J.; Shannan, J.; Vanderploeg, M. 1991. Vehicle rollover on smooth surface, SAE Technical Paper Series, 891991.

[18.] Graves, K.E.; Toncich, D.; Iovenitti, P.G. 2000. Theoretical comparison of motional and transformer EMF device damping efficiency, Journal of Sound and Vibration 233: 441-453.

[19.] Elliott, Stephen J.; Zilletti, Michele. 2014. Scaling of electromagnetic transducers for shunt damping and energy harvesting, Journal of Sound and Vibration 33: 2185-2195.

[20.] Fleming, Andrew J.; Moheimani, S.O. Reza. 2006. Inertial vibration control using a shunted electromagnetic transducer, IEEE/ASME Transactions on Mechatronics 11: 84-92.

[21.] Paulitsch, C.; Gardonio, P.; Elliott, S.J. 2007. Active vibration damping using an inertial, electro-dynamic actuator, ASME Journal of Vibration and Acoustics 129(1): 39-47.

[22.] Glynne-Jones, P.; Tudor, M.J.; Beeby, S.P.; White, N.M. 2004. An electromagnetic, vibration-powered generator for intelligent sensor systems, Sensors and Actuators A: Physical 110(1-3): 344-349.

[23.] Nakano, K.; Elliott, S.J.; Rustighi, E. 2007. A unified approach to optimal conditions of power harvesting using electromagnetic and piezoelectric transducers, Smart Materials and Structures 16(4): 948-958.

[24.] Hagood, N.W.; von Flotow, A. 1991. Damping of structural vibrations with piezoelectric material sand passive electrical networks, Journal of Sound and Vibration 146: 243-268.

[25.] Moheimani, S.O.R. 2003. A survey of recent innovations in vibration damping and control using shunted piezoelectric transducers, IEEE Transactions on Control Systems Technology 11: 482-494.

[26.] Cheng, T.H.; Xuan, D.J.; Li, Z.Z.; Shen, Y.D. 2010 Vibration control using shunted electromagnetic transducer, Applied Mechanics and Materials 26-28: 905-908.

[27.] Rothemann, L.; Schretter, H. 2010. Active vibration damping of the alpine ski, Procedia Engineering 2(2): 2895-2900.

[28.] Scruggs, J.T.; Iwan, W.D. 2005. Structural control with regenerative force actuation networks, Structural Control and Health Monitoring 12(1): 25-45. 10.1002/stc.50.

[29.] Rothbart, Harold A.; Hauserman, R.W.; Smith, S.M.; Schmidt, D.F. 1996 Mechanical Design Handbook :-McGraw-Hill Press. 1400p.

[30.] Schmitz, T.L.; Smith, K.S. 2012. Mechanical Vibration --Modelling and measurements. Springer Publishers. 373p.

[31.] The relative motion between a conductor and magnetic field is used to generate an electrical voltage, [online] [accessed 9 June 2014]. Internet source: ectrical_voltage.

[32.] Solenoid. [online] [accessed 20 July 2014]: Internet source:

[33.] Permeability, Wikipedia, [online] [accessed 20 July 2014]. Internet source:

[34.] Feed Back And PID Control Theory -1,[online] [accessed 15 August 2014]. Internet source:

Received February 12, 2015

Accepted May 06, 2015

Shanker Ganesh Krishnamoorthy *, Inga Skiedraite **

* Kaunas University of Technology, Studentq St. 56, 51424 Kaunas, Lithuania, E-mail:

** Kaunas University of Technology, Studentq St. 56, 51424 Kaunas, Lithuania, E-mail:

Table 1

Summary of values for modelling of EMD

Spring constant K                     1.52 N/mm
Mass of platform M                      1 kg
Maximum load                           24.32 N
Natural frequency                      0.39 Hz
Forcing frequency [[omega].sub.n]       1 Hz
Forcing ratio r                         2.56
Damping ratio [zeta]                     0.5
Damping coefficient c                 3.86 Ns/m

Table 2

Stage-1 results

Number of magnets      Time taken to cover
attached, units      160 mm in free fall, ms

1                               23
2                               35
3                               50
4                               55
5                               85
6                               98

Table 3

Results from modelling

[B.sub.max]                             1.89 x [10.sup.-3] T

P (force around solenoid)               5.55 x [10.sup.-6] N
B (magnetic flux density at centre     1.528 x [10.sup.-3] T
  of solenoid)

Table 4

Results from stage-3 modelling

[B.sub.max]                                3.63X[10.sup.-3] T

P (force around solenoid)                 1.57 X[10.sup.-5] N
B (magnetic flux density at centre of     3.687X[10.sup.-3] T
COPYRIGHT 2015 Kauno Technologijos Universitetas
No portion of this article can be reproduced without the express written permission from the copyright holder.
Copyright 2015 Gale, Cengage Learning. All rights reserved.

Article Details
Printer friendly Cite/link Email Feedback
Author:Krishnamoorthy, Shanker Ganesh; Skiedraite, Inga
Article Type:Report
Date:May 1, 2015
Previous Article:The effect of joint edge surface preparation on the efficiency of fiber laser welding of low-alloyed steels.
Next Article:The definition of cutting forces in square shoulder milling by 3D numerical smooth particle hydrodynamics methodology.

Terms of use | Privacy policy | Copyright © 2020 Farlex, Inc. | Feedback | For webmasters