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A New Model for Control of Systems with Friction

CHUN-CHAU LIN,MEMBER,IEEE AND MICHAEL T .MANRY ,MEMBER, IEEE. A New Model for Control of Systems with Friction . IEEE TRANSACTIONS ON ACOUSTICS, SPEECH, AND SIGNAL PROCESSING, VOL. 37, NO. 3, MARCH 1989. Professor: Ming- Shyan Wang Student: Cai Wei Chun. Outline. Introduction

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A New Model for Control of Systems with Friction

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  1. CHUN-CHAU LIN,MEMBER,IEEE AND MICHAEL T .MANRY ,MEMBER, IEEE A New Model for Control of Systems with Friction IEEE TRANSACTIONS ON ACOUSTICS, SPEECH, AND SIGNAL PROCESSING, VOL. 37, NO. 3, MARCH 1989 Professor:Ming-Shyan Wang Student: Cai Wei Chun

  2. Outline • Introduction • A New Friction Model • Model Proerties • Conclusions • Dynamical Model Behavio

  3. Abstract In this paper we propose a new dynamic model for friction. The model captures most of the friction behavior that has been observed experimentally. This includes the Stribeck effect, hysteresis, spring-like characteristics for stiction, and varying break-away force. Properties of the model that are relevant to control design are investigated by analysis and simulation. New control strategies, including a friction observer, are explored, and stability results are presented.

  4. Introduction(1/2) Friction is an important aspect of many control sys- F tems both for high quality servo mechanisms and simple pneumatic and hydraulic systems. Friction can lead to tracking errors, limit cycles, and undesired stick-slip motion. Control strategies that attempt to compensate for the effects of friction, without resorting to high gain control loops, inherently require a suitable friction model to predict and to compensate for the friction. These types of schemes are therefore named model-based friction compensation techniques. A good friction model is also necessary to analyze stability, predict limit cycles, find controller gains, perform simulations, etc. Most of the existing model-based friction compensation schemes use classical friction models, such as Coulomb and viscous friction.

  5. Introduction(2/2) In applications with high precision positioning and with low velocity tracking, the results are not always satis- factory. A better description of the friction phenomena for low velocities and especially when crossing zero velocity is necessary. Friction is a natural phenomenon that is quite hard to model, and it is not yet completely understood. The classical friction models used are described by static maps between velocity and friction force. Typical examples are different combinations of Coulomb friction, viscous friction, and Stribeck effect [l].

  6. A NEW FRICTION MODEL The qualitative mechanisms of friction are fairly well understood (see, e.g., [l]). Surfaces are very irregular at the microscopic level and two surfaces therefore make contact at a number of asperities. We visualize this as two rigid bodies that make contact through elastic bristles. When a tangential force is applied, the bristles will deflect like springs which gives rise to the friction force; see Fig. 1.

  7. MODEL PROPERTIES(1/2) The properties of the model given by (1) and (3) will now be explored. To capture the intuitive properties of the bristle model in Fig. 1, the deflection z should be finite. This is indeed the case because we have the following property.

  8. MODEL PROPERTIES(2/2) Proof: Let V = z2/2, then the time derivative of V Iz(t)l 5 a v t 2 0. evaluated along the solution of (1) is CANUDAS DE WIT et al.: CONTROL OF SYSTEMS WITH FRICTION

  9. DYNAMICAL MODEL BEHAVIO(1/3) As a preliminary assessment of the model we will investigate its behavior in some typical cases. They correspond to standard experiments that have been performed. In all the simulations the function g has been parameterized according to (4) and the parameter values in Table I have been used. The parameter values have to some extent been based on experimental results [l]. The stiffness 00 was chosen to give a presliding displacement of the same magnitude as reported in various experiments. The value of the damping coefficient 01 was chosen to give a damping of < = 0.5 for the linearized equation (9) with a unit mass. The Coulomb friction level FC corresponds to a friction coefficient p M 0.1 for a unit mass, and Fs gives a 50% higher friction for very low velocities. The viscous friction u2 and the Stribeck velocity U, are also of the same order of magnitude as given in [I].

  10. DYNAMICAL MODEL BEHAVIO(2/3) The different behaviors shown in the following subsections cannot be attributed to single parameters but rather to the behavior of the nonlinear differential equation (1) and the shape of the function g. The presliding displacement and the varying break-away force are due to the dynamics. This behavior is also present in the Dah1 model. The Stribeck shape of g together with the dynamics give rise to the type of hysteresis observed in the subsection on frictional lag.

  11. DYNAMICAL MODEL BEHAVIO(3/3)

  12. CONCLUSIONS A new dynamic model for friction has been presented. The model is simple yet captures most friction phenomena that are of interest for feedback control. The low velocity friction characteristics are particularly important for high performance pointing and tracking. The model can describe arbitrary steady- state friction characteristics. It supports hysteretic behavior due to frictional lag, spring-like behavior in stiction and gives a varying break-away force depending on the rate of change of the applied force. All these phenomena are unified into a first- order nonlinear differential equation. The model can readily be used in simulations of systems with friction.

  13. CONCLUSIONS Some relevant properties of the model have been investigated. The model was used to simulate position control of a servo with a PID controller. The simulations predict hunting as has been observed in applications of position control with integral action. The model has also been used to construct a friction observer and to perform friction compensation for position and velocity tracking. When the parameters are known the observer error and the control error will asymptotically go to zero. Sensitivity studies, parameter estimation andadapta- tion are natural extensions of this work.

  14. REFERENCES(1/2) • [ 11 B. Armstrong-Htlouvry, Control of Machines with Friction. Boston, • MA: Kluwer, 1991. • [2] B. Armstrong-Htlouvry, P. Dupont, and C. Canudas de Wit, “A survey • of models, analysis tools and compensation methods for the control of • machines with friction,” Automatica, vol. 30, no. 7, pp. 1083-1138, • 1994. • [3] P. Dahl, “A solid friction model,” Aerospace Corp., El Segundo, CA, • Tech. Rep. TOR-01 58(3 107-1 8)- 1, 1968. • [4] P.-A. Bliman, “Mathematical study of the Dahl’s friction model,” • European J. Mechanics. AISolids, vol. 11, no. 6, pp. 835-848, 1992. • [5] P.-A. Bliman and M. Sorine, “Friction modelling by hysteresis operators. • Application to Dahl, Sticktion, and Stribeck effects,” in Proc. Con6 • Models of Hysteresis, Trento, Italy, 1991. • [6] C. Walrath, “Adaptive bearing friction compensation based on re- • cent knowledge of dynamic friction,” Automatica, vol. 20, no. 6, pp. • [7] N. Ehrich Leonard and P. Krishnaprasad, “Adaptive friction compen- • sation for bi-directional low-velocity position tracking,” in Proc. 31st • ConfDecisContr, 1992, pp. 267-273.

  15. REFERENCES(2/2) • [8] J. R. Rice and A.L. Ruina, “Stability of steady frictional slipping,” J. • Applied Mechanics, vol. SO, no. 2, 1983. • 191 P. Dupont, “Avoiding stick-slip through PD control,” lEEE Trans. • Automat. Contr., vol. 39, pp. 1094-1097, 1994. • [IO] D. Haessig and B. Friedland, “On the modeling and simulation of • friction,” in Proc. I990 Amer. Conrr. Conf., San Diego, CA, 1990, pp. • 1256-1261, • [I 11 P. Dahl, “Solid friction damping of spacecraft oscillations,” in PI-OC. • AIAA Guidance and Conrr. Conf, Boston, MA, Paper 75-1 104, 1975. • [ 121 J. Willems, “Dissipative dynamical systems part I: General theory,” • Arch. Rational Mech. Anal., vol. 45, pp. 321-51, 1972. • [I31 J. Courtney-Pratt and E. Eisner, “The effect of a tangential force on the • contact of metallic bodies,” in Proc. Royal Society, vol. A238, 1957, • [ 141 D. P. Hess and A. Soom, “Friction at a lubricated line contact operating • at ocillating sliding velocities,” J. Tribology, vol. 112, pp. 147-152, • 1990. • [ 151 V. I. Johannes, M. A. Green, and C. A. Brockley, “The role of the rate • of application of the tangential force in determining the static friction • coefficient,” Wear, vol. 24, no. 381-385, 1973. • [I61 R. S. H. Richardson and H. Nolle, “Surface friction under time- • dependent loads,” Wear, vol. 37, no. 1, pp. 87-101, 1976. • 1171 H. K. Khalil, Nonlinear Systems. New York: Macmillan, 1992.

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