Design and development of two degree of freedom model with PID controller for turning operation
P. Suresh Prabhu^{1} , R. Prathipa^{2} , B. Shanmugasundaram^{3}
^{1, 3}Karpagam University, Coimbatore – 21, India
^{2}Sree Sakthi Engineering College, Coimbatore, India
^{3}Corresponding author
Journal of Measurements in Engineering, Vol. 4, Issue 4, 2016, p. 224231.
https://doi.org/10.21595/jme.2016.15762
Received 23 December 2015; received in revised form 25 February 2016; accepted 23 December 2016; published 31 December 2016
JVE Conferences
The objective is to develop a two degree of freedom model with PID controller for turning process to reduce regenerative chatter with the aim of improving productivity, quality of surface finish, tool life and reducing environmental noise caused by chatter. A system model consists of a workpiece subsystem and a cutting tool subsystem. The workpiece subsystem consists of mass, stiffness and damper. The cutting tool subsystem consists of mass, stiffness and damper. A Piezo actuator and sensor was embedded into the tool holder. A Mechatronic system has been proposed and developed for reducing tool vibration in lathe tool during machining. It consists of electrical and mechanical components; the controller is designed to control the chatter that occurs between the tool and the workpiece. The controller is used to send a feedback to the actuator. The controller is designed so that it suppresses the settling time and dampens the tool. The effective cutting stiffness and effective cutting damping are modeled as a spring and damper during machining. The original response of the system is modeled using transfer function method. Their output responses were obtained using Mat lab software.
Keywords: selfexcited vibration, PID controller, dynamic cutting process, transfer function, step response.
1. Introduction
Developments in machine tools during the past few decades have raised a growing number of vibration problems. These give risk to undulations on the machined surface and excessive variations of the cutting force, which endanger the life of the tool and of the machine. The importance of dynamic performance is also increasing with proliferation of flexible manufacturing systems and unmanned operation of machine tools.
The system investigates the stability of manufacturing with slender tools and improvement of stability by optimal tool parameters using Genetic Algorithm. The objective is to suppress the chatter vibration and bring better stability during cutting process by designing a damped tool holder for existing machine tools. It is noted that the higher negative magnitude of stability boundary corresponds to best stability margin [1]. The system investigates an active vibration control of a beam using virtual instrumentation software. A single degree of freedom spring, mass damper system is actively controlled using piezoelectric elements. The optimal control is arrived at all frequencies using virtual instrumentation software. The intelligent optimal control with varying parameters is found to be more effective than a control with a fixed parameter control system [2]. The model provides a systematic approach for identifying optimum surface roughness performance in endmilling operations. The purpose of their research was to demonstrate a systematic procedure of using Taguchi parameter design in process control of individual milling machines and also to demonstrate a use of the Taguchi parameter design in order to identify the optimum surface roughness performance with a particular combination of cutting parameters in an endmilling operation [3]. Signal parameters characterizing Acoustic Emission (AE) detected during metal cutting have been theoretically correlated in a simple manner, to the work material properties, cutting conditions, and tool geometry [4]. The vibration of a toolworkpiece system in a straight turning process is induced by random disturbances and their effect on a product surface. It is noticed that for large enough level of noise, the tool and a workpiece start to vibrate due to random forcing [5]. The system utilized vibration signals to set up a multiple regression model that was capable of predicting the inprocess surface roughness of a machined workpiece using a turning operation [6].
1.1. Selfexcited vibration
Selfexcited vibration occurs when a steady input of energy is in some way modulated into vibration. Some examples of selfexcited vibration are a whistle, a violin, and chatter. As seen in Fig. 1, the amplitude of this type of vibration increases with time. Chatter is a violent relative vibration between the workpiece and the cutting tool. In metal cutting, chatter is a selfexcited vibration that occurs between a tool and a work piece. Chatter can be detrimental to the surface finish, as well as the tool life.
Fig. 1. Selfexcited vibration
1.2. PID Controller
PID controller combines the advantages of Proportional, Derivative and Integral control actions. The block diagram of PID controller is shown in Fig. 2. In Proportional control the actuating signal for the control action in a control system is proportional to the error signal. For the Derivative control action the actuating signal consists of derivative of the error signal. It is also called as rate control. For the Integral control action the actuating signal consists of integral of the error signal. It is also called as reset control. For PID controller the actuating signal consists of proportional error signal added with derivative and integral of the error signal. The actuating signal is given by Eqs. (12):
Fig. 2. Proportionalintegralderivative control
The dynamics of the control object is the largest source of difficulty in implementing control. Tuning refers to the process of setting parameter values so as to achieve satisfactory performance. Effects of each of controllers ${K}_{P}$, ${K}_{D}$ and ${K}_{I}$ on a closedloop system are summarized in the Table 1.
Table 1. Effects of controller
CL response

Rise time

Overshoot

Settling time

${K}_{P}$

Decrease

Increase

Small change

${K}_{I}$

Decrease

Increase

Increase

${K}_{D}$

Small change

Decrease

Decrease

2. Modeling of active vibration control system
Active vibration control technique is very important for increasing life of various components and structures; this results in lower fatigue, better accuracy and low maintenance. A Piezo actuator and sensor was embedded into the tool holder. The PID controller is used to send a feedback to the actuator. The PID controller is designed so that it suppresses the settling time and dampens the tool. The active method of controlling tool setup is shown in Fig. 3.
Fig. 3. Tool holder with PID controller
2.1. Mathematical modeling of dynamic cutting process
The expression for dynamic cutting force under regenerative chatter condition is given by Eq. (3):
The dynamic cutting force can be modeled, as spring representing effective cutting stiffness and damper representing effective cutting damping. As the value of effective cutting stiffness increases the stability increases and conversely if the value of effective cutting damping decreases then stability increases and settling time decreases. The twodegree of freedom system of cutting toolworkpiece is shown in Fig. 4.
Fig. 4. Mathematical model of the cutting system
a)
b)
Considering the system displacements, ${X}_{W}\left(t\right)$ and ${X}_{t}\left(t\right)$ from the static equilibrium position are positive in the downward direction, the equations of motion of the system is given by Eqs. (45):
The active control of the cutting tool is obtained by introducing a feedback from the output to the cutting tool by means of PID controller. The actuation force for the cutting tool is given by the feedback signal. The twodegree of freedom system with controller is as shown in Fig. 5.
Fig. 5. Mathematical model of the active control cutting system
The equation of motion of the system with controller is given by Eqs. (67):
2.2. Transfer function
Taking Laplace Transform of the above equations can express the dynamic equations in the form of transfer functions. Considering ${F}_{a}$ as input, the transfer function $G\left(s\right)$ is given by Eqs. (810):
where:
$+\left(cw*cc\right)+\left(cc*ct\right)+mt*(kw+kc)\left)\right(cw*kc+cw*kt+cc*kt$
$+cc*kw+ct*kw+ct*kc\left)\right(kw*kt+kw*kc+kc*kt\left)\right].$
The effect of effective cutting stiffness on system stability and values are tabulated as shown in Table 2. A generalized program is written by transfer function method using Matlab. By substituting the tabulated values in the Mat lab program, the step response obtained is shown in Figs. 615.
Table 2. Cutting tool parameters
S. No.

${K}_{c}$ (kN/m)

${C}_{c}$ (kN s/m)

${K}_{t}$ (kN/m)

Values of other parameters

1

300

–0.1983

2000

${M}_{w}=$ 1.604 kg,
${K}_{w}=$ 563 kN/m,
${\xi}_{w}=$ 0.0647,
${M}_{t}=$ 2.48 kg,
${\xi}_{t}=$ 0.3254

2

800

–0.6218

3000


3

1300

–0.8754

4500


4

1800

–0.9186

5500


5

2300

–1.0396

7000

3. Step response (without PID Controller)
Fig. 6. Step response for ${K}_{t}=$ 2000 kN/m, ${K}_{c}=$ 300 kN/m and ${C}_{c}=$ –0.1983 kN s/m
Fig. 7. Step response for ${K}_{t}=$ 3000 kN/m, ${K}_{c}=$ 800 kN/m and ${C}_{c}=$ –0.6218 kN s/m
Fig. 8. Step response for ${K}_{t}=$ 4500 kN/m, ${K}_{c}=$ 1300 kN/m and ${C}_{c}=$ –0.8754 kN s/m
Fig. 9. Step response for ${K}_{t}=$ 5500 kN/m, ${K}_{c}=$ 1800 kN/m and ${C}_{c}=$ –0.9186 kN s/m
Fig. 10. Step response for ${K}_{t}=$ 7000 kN/m, ${K}_{c}=$ 2300 kN/m and ${C}_{c}=$ –1.0396 kN s/m
4. Step response (with PID Controller)
Fig. 11. Step Response for ${K}_{t}=$ 2000 kN/m, ${K}_{c}=$ 300 kN/m and ${C}_{c}=$ –0.1983 kN s/m
Fig. 12. Step response for ${K}_{t}=$ 3000 kN/m, ${K}_{c}=$ 800 kN/m and ${C}_{c}=$ –0.6218 kN s/m
Fig. 13. Step response for ${K}_{t}=$ 4500 kN/m, ${K}_{c}=$ 1300 kN/m and ${C}_{c}=$ –0.8754 kN s/m
Fig. 14. Step response for ${K}_{t}=$ 5500 kN/m, ${K}_{c}=$ 1800 kN/m and ${C}_{c}=$ –0.9186 kN s/m
Fig. 15. Step response for ${K}_{t}=$ 7000 kN/m, ${K}_{c}=$ 2300 kN/m and ${C}_{c}=$ –1.0396 kN s/m
5. Result
The values of Settling Time and Peak Amplitude for different values with and without using PID Controller are tabulated in Table 3.
Table 3. Step response values
Figure

Without PID controller

With PID controller


Settling time (sec)

Peak amplitude
(microns)

Settling time (sec)

Peak amplitude (microns)


Fig. 6 and 11

2.28

1.16

0.98

–0.01

Fig. 7 and 12

1.44

1.06

0.62

–0.01

Fig. 8 and 13

1.26

1.06

0.51

–0.01

Fig. 9 and 14

1.05

1.01

0.46

0.01

Fig. 10 and 15

0.96

1.01

0.36

0.01

6. Conclusions
The effect of effective cutting stiffness on system stability has been analyzed using Matlab. The Modeling is performed by transfer function method. The controller is used to reduce the settling time. It is observed that settling time and peak amplitude is considerably decreased when PID controller is used than that of without PID controller.
References
 Alwarsamy T., Balasubramanian R., Raja Kumar K., Sankarasubramanian B. Improvement of stability by optimal parameters using genetic algorithm. Advances in Vibration Engineering, Vol. 2, Issue 4, 2003, p. 388404. [Search CrossRef]
 Singh Harpreet, Singh S. P., Agarwal V. P. Active vibration control of a beam using virtual instrumentation software. International Conference on Smart Materials, Structures and Systems, India, 1999, p. 443448. [Search CrossRef]
 Yang John L., Chen Joseph C. A systematic approach for identifying optimum surface roughness performance in endmilling operations. Journal of Industrial Technology, Vol. 17, Issue 2, 2001. [Search CrossRef]
 Keraita J. N., Oyango H. J., Misoi G. K. Lathe stability charts via acoustic emission monitoring. African Journal of Science and Technology, Science and Engineering Series, Vol. 2, Issue 2, 2001, p. 8193. [Search CrossRef]
 Lipski J., Litak G., Rusinek R., Szabelski K., Teter A., Warminski J., Zaleski K. Surface quality of a work material influence on vibrations in a cutting process. Journal of Sound and Vibration, Vol. 252, Issue 4, 2002, p. 729737. [Publisher]
 Huang Luke, Chen Joseph C. A multiple regression model to predict inprocess surface roughness in turning operation via accelerometer. Journal of Industrial Technology, Vol. 17, Issue 2, 2001. [Search CrossRef]
 Karkosch H. J., Preumont A. Recent advances in active damping and vibration control. 8th International Conference on New Actuators, Germany, 2002, p. 248253. [Search CrossRef]
 Mauri E., Kato S., Hashimoto M. The mechanism of chatter vibration in a spindleworkpiece system: Part 1 – Properties of selfexcited chatter vibration in spindleworkpiece system. Journal of Engineering for Industry, Vol. 110, 1988, p. 236241. [Publisher]
 Mauri E., Kato S., Hashimoto M. The mechanism of chatter vibration in a spindleworkpiece system: Part 2 – Characteristics of dynamic cutting force and vibration energy. Journal of Engineering for Industry, Vol. 110, 1988, p. 242247. [Publisher]
 Mauri E., Kato S., Hashimoto M. The mechanism of chatter vibration in a spindleworkpiece system: Part 3 – Analytical considerations. Journal of Engineering for Industry, Vol. 110, 1988, p. 248253. [Publisher]
 Lago T. L., Hakansson Lars Performance of a chatter control system for turning and boring applications. 4th GRACM Congress on Computational Mechanics, 2002. [Search CrossRef]
 Andren L., Hakansson L., Claesson I. Active Vibration Control of Boring Bar Vibrations. Blekinge Institute of Technology, Sweden, 2004, p. 139196. [Search CrossRef]
 Tobias S. A. Machine Tool Vibration. John Wiley, New York, 1965. [Search CrossRef]
 Willis M. J. ProportionalIntegralDerivative Control. University of Newcastle, 1999. [Search CrossRef]
Cited By
Acta Mechanica
L. Cveticanin, A. Dregelyi, R. Horvath, M. Zukovic

2021

Journal of Vibroengineering
Yang Daolong, Li Jianping, Wang Yanxiang, Jiang Hongxiang

2017

Science Evolution
Sergey Pachkin, Sergey Pachkin, Roman Kotlyarov, Roman Kotlyarov

2017
