Mathematical Problems in Engineering

Volumeย 2011, Article IDย 254547, 17 pages

http://dx.doi.org/10.1155/2011/254547

## An Evolutionary Analytic Method of Multi-DOF Nonlinear Coupling Dynamic Model for Controllable Close-Chain Linkage Mechanism System

^{1}College of Mechanical Engineering, Guangxi University, Nanning 530004, China^{2}Guangxi Key Laboratory of Manufacturing System & Advanced Manufacturing Technology, College of Mechanical Engineering, Guangxi University, Nanning 530004, China

Received 26 December 2010; Revised 27 March 2011; Accepted 20 April 2011

Academic Editor: Angeloย Luongo

Copyright ยฉ 2011 Ru-Gui Wang 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.

#### Abstract

The 2-DOF controllable close-chain linkage mechanism is investigated in this paper. Based on the characteristics of the multi-DOF nonlinear coupling dynamic equation of the system established by the finite element method, an analytic method of multiple-scales Newmark is presented after thinking about the method of perturbation and the method of numerical analysis. Firstly, the first-order approximate solution of the dynamic responses of the system at the time of is calculated by the multiple scales method. Then, taken the first-order approximate solution as the initialization of the generalized coordinate of the system, the stable dynamic response of the system is obtained by the implicit Newmark method. The simulation and experimental results are given in the end. The studies indicate that the method of multiple-scales Newmark is correct and practicable to study the dynamic characteristics of such kind of multi-DOF nonlinear coupling system.

#### 1. Introduction

Multi-DOF controllable linkage mechanism, which can accurately actualize the given trajectory, velocity, and acceleration, will has a wide outlook of application in robots, automatic production lines, and so on [1โ5]. The dynamic equation of such kind of linkage mechanism is nonlinear coupling time-variant from the dynamics modeling process of the linkage system. The numerical Newmark method can calculate the dynamic responses, but that method could not analyze internal relation between the dynamic characteristics and scale and electromagnetism parameters. Though the multiple-scales method can analyze the vibratory mechanism, it usually adopts first approximations and quadratic or higher order approximation is very complex [6โ10]. An evolutionary analytic method of multiple-scales-Newmark method is firstly presented to study the dynamic characteristics of such kind of multi-DOF coupling system synthetically using the property that the implicit Newmark method can calculate the unconditioned stable solution when the Newmark parameters are specific constants the features of the multiple scales method.

#### 2. Nonlinear Dynamic Equation of System

The 2-DOF controllable close-chain linkage mechanism is investigated in this paper. The analysis diagram of system is shown in Figure 1. Based on the air-gap field of nonuniform airspace of controllable motors of the linkage mechanism caused by the eccentricity of rotor, the controllable motor element [11] as shown in Figure 2, which defined the transverse vibration and torsional vibration of the controllable motors as its nodal displacement, was established. In the diagram, numbers 1, 2, 3, and 4 denote four nodes of the element. So the transverse vibration and the torsional vibration can be expressed by the generalized coordinate vector , and is the coordinate system of controllable motor element.

According to the mechatronics analysis dynamics, the air-gap eccentric vibration is shown in Figure 3, where point is the inner circle geometric center of the motor stator, point O_{1} is the outer circle geometric center of the rotor journal, point O_{2} is the outer circle center of the journal under the deformation of shaft or bearing, the coordinate of point is the outer circle geometric center of the rotor, is the length of air gap, and is the air-gap eccentricity. is the static eccentricity, which is caused by the rotor gravity and mismachining tolerance of motor. is the rotational eccentricity, which is caused by centering error between the outer circle center of the journal and the outer circle geometric center of the rotor. The static eccentricity and the rotational eccentricity are considered at the same time in this paper. The static and rotational eccentricities also can be ignored, and only the eccentricity caused by rotor vibration can be considered in engineering application latterly. Then, ,
where and are the components of vibration eccentricity in the and direction, and . is the rotational angle of rotor with respect to the stator of controllable motor. is the synchronous speed of rotation of controllable motor. is the slide ratio.

According to the theory of electromechanics and electromechanical analysis dynamics, as far as controllable motor is concerned, the voltage and current between the two windings are asymmetric, that is to say, the controllable motor works in elliptic magnetic field. According to this real running state of controllable motor, the kinetic energy and potential energy of controllable motor can be obtained as follows: where and the transverse displacements and the angle of elastic torsion of any points in the controllable motor element, respectively (see the appendix), and is the length of controllable motor shaft (see the appendix);, including the rotor mass which is at , is the mass distribution function of the controllable motor shaft;, including the moment of inertia of rotorwhich is at, is the moment of inertia distribution function of the controllable motor shaft. is the inner radius of the controllable motor stator, is the effective length of the rotor, is the even air gap permeance of the controllable motor, is the magnetic permeability coefficient of air, , is saturation, is the uniform air-gap size, , is the calculation air-gap coefficient of the even air gap, is the equivalent air-gap of ferromagnetic materials, is the phase angle of the positive-sequence current of rotor lagging behind the positive-sequence current of stator, and is the phase angle of the negative-sequence current of rotor lagging behind the negative-sequence current of stator. , and are the positive-sequence and negative-sequence components of the magnetomotive amplitude of stator and rotor respectively (see the appendix). is the mass matrix of controllable motor element, is the stiffness matrix of controllable motor element in connection with the structural parameters of the rotor, is the stiffness matrix of controllable motor element in connection with the electromagnetic parameters of the rotor, and is the 4-order vector in connection with the eccentric motor (see the appendix). is a matrix in connection with the static and rotary eccentricity of the controllable motor.

In general, the links of the 2-DOF controllable linkage mechanism are slim bars, so they are adapted to be simulated using beam element as shown in Figure 4. In dynamic analysis of the beam element, the coupling terms of the elastic motion and the rigid body motion in the Coriolis acceleration and transport acceleration are neglected in studying the absolute acceleration of any point in the beam element. In calculation of strain energy, the shearing deformation energy and yield deformation energy are also omitted. The material of the link is adopted as metal. Therefore, the kinetic energy and potential energy, respectively, are as follows: where is the average mass density of beam element, is the cross-section area function, and and are, respectively, the longitudinal displacement and the transversal displacement of any point in the beam element (see the appendix). is the modulus of elasticity, is the moment of inertia distribution function of the element. and are the mass matrix and stiffness matrix of the beam element, respectively, and they are matrix (see the appendix).

We regard the links BC and CD as two beam elements, respectively, and regard the crank AB and DE as one element respectively as shown in Figure 1. โโโ*โข*โ, โโโ*โฃ*โ, โโโ*โค*โ, โโโ*โฅ*โ, โโโ*โฆ*โโโโandโโโ*โง*โโโโare the serial number of the beam element as shown in Figure 5. , ,,, , , , , , and are elastic displacement, ,, , , , , , , , and are elastic rotational angle, , , , and are the curvature. The serial numbers of the controllable motor elements areโโโ*โ *โโโandโโโ*โก*โ.

The global coordinate system is established, and the system elastic displacement vector in the global coordinate system is defined as . Assume that โโis the transformation matrix of the th element between the element coordinates and the global coordinates, and โโis the coordinate matrix of the th element between the local numbering and the system numbering (see the appendix).

The linear viscous damper damping is adopted in this paper, according to the second Lagrange equation

The electromechanical coupling nonlinear dynamic equation of the system can be obtained as where is the generalized coordinates array of the system, and are, respectively, the mass matrix and damping matrix of the system, and are the stiffness matrixes in connection with the structural parameters of system, and are the stiffness matrixes in connection with the electromagnetic parameters of system, is the orders array in connection with the electromagnetic parameters of system, is the external force array of the system, is the rigid acceleration array of system in the global coordinates, is an array in connection with the eccentricity of rotor, is the nonlinear term and also is a small parameter, and and are the matrixes in connection with the structural parameters of the linkage mechanism,

โ is the number of the elements, and here . are the shape functions (see the appendix).

In (2.7), are periodic terms. They can be expanded to the form of Fourier series as follows [12]: where is the working frequency of rotor of controllable motor 1, is the working frequency of rotor of controllable motor 2, and is the smallest common multiple of and . , , is the rotation frequency of magnetic field of stator of the controllable motor 1, is the rotation frequency of magnetic field of stator of the controllable motor 2, is the smallest common multiple of and , and is the smallest common multiple of, ,, and . express the amplitude values, are the corresponding phase angles, and is the number of terms of the Fourier expansion formula.

#### 3. First Approximate Solutions

Substituting (2.10) into (2.7) and assuming that the linear transfer functions are where is the modal transfer matrix, is the modal coordinate vector corresponding to . Substituting (3.1) into (2.7), and premultiply the equation by , then (2.7) can be transferred as where

, , , ,โ, , , . and are the -order damping ration mean and the -order instantaneous natural frequency mean of the -order canonical mode of the system in a period of motion, and can be obtained through experiment.

Equation (3.2) also can be expressed as where, and are the coefficients of , and , respectively. is the th-order vector, and the th element of is 1 and the other elements are zero. Therefore, the system is affected by multifrequency excitations.

The method of multiple time scales is employed to study the nonlinear (3.4), and the frequent factors of system can be obtained. and some resonance phenomena will take place in the system under certain conditions.(1)On condition that , the primary resonance will take place in the system. (2)On condition that , the ultra-harmonic resonance will take place in the system.(3) On condition that or , the subharmonic resonance will take place in the system.(4) On condition that , the inner resonance will take place in the system.(5)On condition that or , the combination resonance will take place in the system.(6) On condition that two types of the resonance take place in the same time, the multiple resonance of the system will take place in the system.

Considering the first two orders modal of vibration, the first approximation solutions of the multi-DOF nonlinear coupling system in the generalized coordinate are also obtained by the method of multiple scales as follows: where and can be resolved by the method of Newton-Raphson, is the -order instantaneous natural frequency mean of the system, and and .

Therefore, the resonance characteristics of the multi-DOF nonlinear coupling system can be analyzed using the method of multiple scales, and the first approximate solutions of the dynamic model of the system also can be obtained by that method.

#### 4. Newmark Stable Numerical Solution

Because the implicit Newmark integration method can calculate the unconditioned stable solution when the Newmark parameters and are specific constants [13, 14], the method is adopted to obtain the stable solution of the multi-DOF nonlinear coupling system. Therefore, the stable solutions can be obtained using the implicit Newmark integration method based on the first approximate solutions calculated by the method of multiple scales.

In order to calculate the dynamic response of the system as shown in (2.7), the period of motion of the system is divided into time steps under given trajectory, that is to say, And the first approximate solution of dynamic response of the system is solved by the multiple-scales method firstly as shown in (3.7). The first approximate solution when is at a moment is looked as the initial value,and then the dynamic response of system is solved by immediate integration implicit Newmark method.

When we calculate the response of the system by implicit Newmark method, the hypothesis about the response of some moment must be taken as where and are the Newmark parameters, namely, the constant of integration and and .

Because the multi-DOF nonlinear coupling dynamic (2.7) is time variant, the equation at the moment of can be expressed as

Substituting calculated according to (4.3) into (4.4), the expressed by , and can be obtained. The calculation accuracy is related to time step.

#### 5. Simulation and Experimental Results

Every link of the linkage mechanism is homogeneous. The width and thickness are 30โmm and 2โmm, respectively. The lengths of each links are, crank and , coupler , and frame as shown in Figure 1. The material of link is aluminium. The density of aluminium and the Youngโs modulus . The lumped mass of the intersection between the crank and the coupler is . The lumped mass of the intersection between the two couplers is . The controllable motor 1 is 90ZYT motor and motor 2 is YS8024 motor. The motors are custom made by motor manufacturer. The parameters of motors are offered by the manufacturer.

The parameters of the motors are as follows:

*โ *โโโ*The Parameters of the Control Motor 1. *The rated power of the 90ZYT motor, , the rated voltage, , the rated rotational speed of the motor is 1500โr/min, and the stall torque is . The static-geometric eccentricity of the motor, and the rotational eccentricity, . The magnetic permeability coefficient of air is , the length of the even air is gap , and the saturation is . The number of excitation windings of the motor is , and the coefficient is . The peak value of field current, . The number of magnetic pole-pairs of the motor is and are the number of phases of the stator and rotor, respectively. The reactance of field windings is . The reduction value of resistance and equivalent self-induction reactance of rotor, respectively, are and . The slide ratio is . The control voltage is . The mass of the motor rotor is . The moment of inertia of the motor rotor is . The length of the motor shaft is , and, the effective length of the rotor , and the inner radius of the motor stator is .

*โก*โโโ*The Parameters of the Control Motor 2. *The rated power of the YS8024 motor is , the rated current is , the rated voltage is , and the rated rotational speed is . The static-geometric eccentricity is and the rotational eccentricity is . The magnetic permeability coefficient of air is the length of the even air gap is , and the saturation is . The number of excitation windings of the motor is and the coefficient is . The peak value of field current is . The number of the magnetic pole-pair of compounded magnetic field is . and are the number of phases of the stator and rotor respectively. The reactance of field windings is . The reduction value of resistance and equivalent self-induction reactance of rotor, respectively, are and . The slide ratio is . The control voltage is . The mass of the motor rotor is . The moment of inertia of the motor rotor . The length of the motor shaft , and , the effective length of the rotor and the inner radius of the motor stator is .

As shown in Figure 1, The initial angles of the two cranks are 0ยฐ. The calculation initial value of the response is the one when the two cranks move to the initial position of them after the system comes to the stabilized state. Given and , the period of motion of the linkage mechanism is divided into time steps.

The responses of transversal and longitudinal displacement of the midpoints of the links , and can be calculated by the method of multiple-scales Newmark mentioned above, then the dynamic responses on the direction perpendicular to the linksโ axis can be simulated by the Multiple-Scales-Newmark method mentioned above as shown in Figure 6, and the corresponding experimental curve of dynamic response of the linksโ midpoint on the same parameter conditions can be obtained through experiment as shown in Figure 6. The dynamic responses of midpoints of the links are measured by the dynamic test system in experiment. Comparing the simulation with experimental figures, one can find that the multiple-scales Newmark method studied in this paper is correct and practicable.

#### 6. Conclusions

The numerical method can calculate the dynamic responses, but that method could not analyze internal relationship between the dynamic characteristics and the scale and electromagnetism parameters. Though the multiple-scales method can analyze the dynamics mechanism, it usually adopt first approximations and second, or higher-order approximation is very complex. An evolutionary analytic method of multiple-scales Newmark is firstly presented in this paper to study the dynamic characteristics of such kind of multi-DOF nonlinear coupling system synthetically using the property that the implicit Newmark method can calculate the unconditioned stable solution when the parameters of Newmark are specific constants with the features of the multiple scales method. The numerical simulation and experimental results indicate that the multiple-scales Newmark method mentioned in this paper is correct and practicable. The study provides the basis of further study on the dynamic control of such kind of mechanism.

#### Appendix

#### โ

According to the finite element method, and can be expressed as

where are the shape functions, where , , , , , and are, respectively, the length between point 1 and point 2, point 2 and point 3, point 3 and point 4. is the nodal displacement as shown in Figure 2.

The mass matrix of the electromotor element is matrix,

and the other components are equal to zeros.

The stiffness matrixes of the electromotor element are

According to the finite element method, and can be expressed as

where is the coordinate of beam element in local coordinate system, and the shape functions are as follows: where , is the length of the beam element.

The mass matrix and stiffness matrix of the beam element are as follows:

where is the moment of inertia of cross-section.

The positive-sequence and negative-sequence components of the magnetomotive amplitude of stator and rotor, respectively, are

where , is the number of turns of field winding, is the coefficient of field winding, is the number of pole pairs, is the peak value of field current. is the effective signal coefficient, is the rated voltage, and is the actual control voltage. and are the number of phases of the stator and rotor, respectively, is the reactance of field windings, and are respectively the reduction value of resistance and equivalent self-induction reactance of rotor windings, and the slip ratio is the difference between the rotor speed and forward revolving field. is the slip ratio between the rotor speed and backward revolving field.

The transformation matrix of the th element โis as follows

โ

where is the position angle of the link with the level position.

The coordinate matrix of the th element and is matrixes, and , , , , , and are matrixes, and

and the other components of are 0.

#### Acknowledgments

This research was supported by the National Natural Science Foundation of China (Grant no. 51075077), the Scientific Research Foundation of Guangxi University (Grant no. X081018), and the Teams for Innovation in the Construction of Talent Highlands in Guangxi Institutions of Higher Learning. The authors gratefully acknowledge the supporting agencies.

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