Coupled-Nonlinear Elastic Structure: An Innovative Parameterization Scheme of the Motion Equations ()

S. A. David^{}

Department of Biosystems Engineering, University of São Paulo, São Paulo, Brazil.

**DOI: **10.4236/am.2014.521324
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Department of Biosystems Engineering, University of São Paulo, São Paulo, Brazil.

In this paper, I applied the Euler-Lagrange equations in order to obtain the coupled-nonlinear motion equations for an elastic structure. The model is composed of six coupled and strongly nonlinear ordinary differential equations. The new contribution of this work arises from the fact that a convenient and innovative parameterization of the motion equations for the elastic system was developed with all mathematical nonlinearities taken into account, without the usage of any simplifying linearization procedure, as found in most of the works presented in the literature. The results can be used as a source for conducting experiments and can be useful for a better understanding and control of such nonlinear elastic systems.

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David, S. (2014) Coupled-Nonlinear Elastic Structure: An Innovative Parameterization Scheme of the Motion Equations. *Applied Mathematics*, **5**, 3460-3473. doi: 10.4236/am.2014.521324.

1. Introduction

The use of the lightweight structural elements in space applications, underwater interventions as well as in robotic manipulators under the requirement for precise positioning, easier transportation, less power consumption, has increased the interest in having a precise model that closely represents such mechanical systems for all their conditions. The position and velocity vector obtained, after imposing the inextensibility conditions, are used in kinetic energy expression while the curvature is used in the potential energy. The Lagrangian dynamics [1] in conjunction with the assumed modes method [2] are utilized in order to obtain the non-linear [3] equations of motion that are treated with all non-linearities taken into account, without the usage of any simplifying linearization procedure, as found in most of the works found in the literature. The resulting non-linear model is composed of six coupled and strongly non-linear ordinary differential equations are discussed, simulated and some results of this simulation are presented. The way in which the motion equations were treated in this paper, allows the monitoring of each contributing factor for the system elasticity. The main goal of this work is to treat the motion equations according to a general approach, without the usage of any linearization procedure, and this way to permit assesses the system behavior through controlled simulations.

2. Problem Description

In this work the dynamic modeling is performed for a system that contains two elastic beams and two rotational joints.

A convenient parameterization of the terms of the motion equations, which makes it easier to compare the simulation results for the rigid and for the elastic structure [4] is also developed. The studied elastic system is assumed to have a planar movement. Even with this assumption, the complexity of the resulting dynamic equations for this system is large when compared to the equations for rigid structures [5] .

The model is established basically by the superposition of the elastic movement with the movement of a hypothetical rigid body. A convenient mathematical set of equations is developed for this purpose. The elastic [6] movement of the beams is truncated in the second mode, that is, it is considered that the amplitudes of all higher order vibration modes [7] are much smaller than the amplitude of vibration of the first mode. In such a case, a non-linear model with six degrees of freedom is obtained.

I outline that, one of the tasks of this work is to treat the motion equations according to a general approach, without simplifying linearizations procedure.

3. The Model

The physical model for the elastic system is established in accordance to the schematic drawing shown in the Figure 1.

The following assumptions are made: the system has planar movement and the relative movement between the two links is resulting from the torques applied in each joint of the system.

At the terminal of the beam 1, a concentrated mass represents both the servo-motor and the joint masses. At the terminal of the beam 2, a discrete mass is used to represent the load to be handled between two points of the plane.

In order to describe the movement, three reference systems are defined:

―inertial referential system with origin in joint 1;

―referential system with origin in O and the x_{1} axis tangent to beam 1 at point O;

―referential system with origin in joint 2 and with the x_{2} axis tangent to beam 2 at point O_{2}.

Two angles are defined:

is the angle between the x_{1} and x axes; is the angle between the x_{1} and x_{2} axes.

It is also defined a new system that is formed by the two segments OO_{1} and O_{1}O_{3}, with angle in O_{1}. The global (total) movement may be understood as being the movement of an hypothetical rigid system OO_{1}O_{3} and a

Figure 1. Physical model.

flexible movement of the beams 1 and 2 with respect to this mobile system.

3.1. Kinematics Description

The position can be described by a convenient description of a set of coordinates. Any point P_{i} may be specified if a new variable is defined as being the coordinate of the flexible movement with respect to the reference system.

In order to simplify the notations, a matrix representation form of the reference frames can be introduced. Let them be:

, is the unit vector of the frame OXY;

, is the unit vector of the frame;

, is the unit vector of the frame.

Then,

(1)

and

(2)

where and are the rotational transformation matrices and can be written:

(3)

and

(4)

with,

Figure 2 shows defined like a coordinate of the elastic motion of the beam with respect to the frame.

The (generic) position vector (Figure 2) will be:

(5)

Figure 2. Vector (beam i).

where means the transpose matrix.

With the usage aformentioned equation, can be written the vector position of any point on the beam 1 of the following manner:

Beam 1

(6)

where and means the transpose matrix.

Beam 2

In order to define the vector position of any point on the beam 2, it will be convenient to assume that the displacements of the elastic beams with respect to reference frames and be small enough to consider the paths of points O_{2} and O_{p} as straight lines normal to the respective reference frames. Then, the position vector of any point P_{2} on the beam 2 is established in accordance to the schematic drawing shown in Figure 3. It is also possible to note that,

(7)

If now, u_{1E} = elastic linear displacement at the end of the beam 1; L_{1}, L_{2} = lengths of the beam 1 and 2, then,

(8)

(9)

(10)

(11)

and thus,

(12)

Consequently,

(13)

and

(14)

Similarly, one can obtain and, for a mass concentrated at the joint 2 and for the payload, respectively, and will be shown in the next section.

3.2. Kinetic Energy

By means of the velocity vectors previously mentioned, the total kinetic energy of the system may be expressed by the following equation:

(15)

where, is the kinetic energy of the beam 1 and it is given by:

(16)

Similarly, is the kinetic energy of link 2 and it is given by:

(17)

The same procedure can be applied to both: a mass concentrated at the joint 2 and a load with moment of inertia (J_{xp}) with respect to an axis normal to the plane of motion and through the center of gravity. By doing this for a mass in the joint 2, the expression (13) can be modified to

(18)

and

(19)

is the kinetic energy related to the concentrated mass that represents the servo-motor and the joint. The mass is located at point O_{2}, in joint 2;

Note that:

1) x_{1} was replaced by L_{1}, in which case we are not at any point on the first link, but at its end;

2) u_{1} has been replaced by u_{1E}, because u_{1E} is the linear displacement at the end of the elastic beam 1.

Similarly too,

(20)

Note, yet

1) The load is located at the end of the beam 2 and therefore, was replaced by.

2) and were replaced, respectively by and, emphasizing that the displacement considered due to the flexibility at the end of the beam 2.

3) Considering and the moment of inertia of the load with respect to an axis through of the

point O_{2} defined by J_{p}, then

(21)

is the kinetic energy related to the mass of the load and the rotational kinetic energy of the load due to its movement around the axis that passes through point O_{2} and that is perpendicular to the plane shown in Figure 1. With these facts in mind, one can obtain the following final expression for the total kinetic energy of the system:

(22)

3.3. Potential Energy

In the calculation of the total potential energy of the system it is assumed an energy associated to the rigid movement (gravitational potential energy), plus the elastic potential energy of the links. Ox is taken as reference and the potential energy of the system (assuming u_{1} and u_{2} sufficiently small) is given by:

(23)

where:

g is the gravitational acceleration constant;

L_{1} and L_{2} are the lengths of the links 1 and 2, respectively;

EI_{1} and EI_{2} are the rigidity of the links 1 and 2, respectively, which in this model are assumed to be constants. In fact, the elastic displacements u_{1} and u_{2} (Figure 2 and Figure 3), were considered sufficient small. However, I would like to outline that the assumption that the deformation is sufficient small do not implies, necessarily, that the angles are small.

3.4. Motion Equations

In order to write down the motion equations of the system it will be used the assumed modes method. For the

Figure 3. Position vector (beam 2).

elastic displacements of the beams 1 and 2, it is possible to assume that

(24)

(25)

where the admissible functions must satisfy the geometrical boundary conditions with respect to the representation of the links in the reference systems and. Hence the system becomes represented by degrees of freedom.

If it is assumed that the amplitudes of the higher order vibration modes are very small when compared to the first vibration mode, the system may be truncated with n equal to 2, resulting in a problem involving six degrees of freedom.

Besides this, if it is assumed that are eigenfunctions of the problem of a clamped free beam and due to the ortogonality of this functions we will have:

(26)

With this equation, one can assess each one of the integrals in the equations for both the kinetic and the potential energy considering the generalized coordinates and the non-conservative torques acting at the joint of the system, it is possible to write the equations of the movement―with convenient parameterization of the terms and without the usage linearization procedure―using the Lagrange equations for non-conservative systems,

(27)

where: Q_{r} are the time dependent generalized non-conservative forces (or torques).

The equations assume the final form,

(28)

(29)

(30)

(31)

(32)

(33)

where

(34)

(35)

(36)

(37)

(38)

(39)

(40)

(41)

(42)

(43)

(44)

(45)

(46)

(47)

(48)

(49)

(50)

(51)

The coefficients of these equations are presented as follows: general coefficients are relative of the rigid system. Table 1 and Table 2 show the specific coefficients for the elastic system. Thus,

General coefficients:

(52)

(53)

(54)

(55)

Table 1. Coefficients of the first three equations of motion.

Table 2. Coefficients of the last three equations of motion.

(56)

and,

(57)

This convenient parameterization of the terms of equations of motion allows us a comparison with pre-estab- lished methods and the contribution of each elastic term of the parameterized system.

4. Some Numerical Simulation Results

The simulations are performed considering sinusoidal excitation. Some results are presented, according to the following methodology:

1) The elastic system was simulated with all its contributions taken into account. Full elastic system, equations simulated (28) to (33) and Figure 4 to Figure 7.

2) After that, the effects are individually and cumulatively subtracted and the system behavior is analyzed. Elastic system, Equations (28) to (33) subtracted flexibility in the J-term; (Figure 8 and Figure 9) and after subtracted flexibility in the term (Figure 10 and Figure 11).

3) The effects are subtracted until the limit condition in which the elastic system is reduced (mathematically) to a rigid one by means of vanishing the flexibility related terms, and the system response converges―as expected―for the case of the rigid system modeled separately. Equations reduced (28) to (33) and Figure 12 and Figure 13.

Figure 4. Angular position x time (beam 1).

Figure 5. Angular position x time (beam 2).

Figure 6. Angular velocity x time (beam 1).

Figure 7. Angular velocity x time (beam 2).

Figure 8. Subtracted flexibility in J-term (beam 1).

Figure 9. Subtracted flexibility in J-term (beam 2).

Figure 10. Subtracted flexibility in T_{perturb} (beam 1).

Figure 11. Subtracted flexibility in T_{perturb} (beam 2).

Figure 12. Elastic system reduced to a rigid one (beam 1).

Figure 13. Elastic system reduced to a rigid one (beam 2).

5. Conclusions

The Lagrangian dynamic in conjunction with the assumed modes method were utilized in order to obtain the non-linear equations of motion.

A convenient parameterization of the terms of the motion equations, which makes it easier to compare the simulation results for the rigid and for the elastic system, was also developed.

About the comparison with other equations of motion in current literature, I outline that the approach here formulated is innovative. The works founded in the literature involving dynamic modelling of the elastic structures uses some kind of the linearization procedure and presents your equations of motion in most cases like a matrices formulation, i.e., mass matrix, damping matrix, stiffness matrix and elasticity matrix. In this paper, equations are treated with all non-linearities taken into account and the approach entails parameterization of the nonlinear dynamics without the usage of any simplifying linearization procedure. The elastic structure may be mathematically reduced to a rigid one by means of vanishing the flexibility related terms. The same procedure may be extended to the simulations, which makes it possible to find a mathematical frontier between both systems.

The effects of the flexibility are explored by comparing the resulting simulation results.

Besides, the way in which the motion equations are treated in this paper allows the monitoring of each contributing factor for the system elasticity. Thus, one can be taught about the efficient controllers which can make compensation about the flexible (elastic) physical effects.

Nomenclature

Latin Letters

geometric vectors

matrices

Young’s modulus

stiffness

mass

payload mass

joint mass

gravity

length

generalized coordinate

time

kinetic energy

elastic displacement at the end of the beam (・)

potential energy

first time derivative of A, a, ∙∙∙

second time deriv. of A, a, ∙∙∙

stiffness

Greek Letters

admissible functions

angles

torques

Abreviations

・^{T} transpose of the matrix (・)

Tr trace of a matrix

Conflicts of Interest

The authors declare no conflicts of interest.

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[2] | Nayfeh, A. and Mook, D.T. (1979) Nonlinear Oscillations. Wiley & Sons, New York. |

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[4] | Balthazar, J.M. and Fenili, A. (2009) Some Remarks on Nonlinear Vibrations of Ideal and Nonideal Slewing Flexible Structures. Journal of Sound and Vibration, 282, 543-552. |

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[7] |
Nayfeh, A.H. and Pai, P.F. (2004) Linear and Nonlinear Structural Mechanics. John Wiley & Sons, Inc., New York.
http://dx.doi.org/10.1002/9783527617562 |

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