Generating various motion paths of single-mass vibratory system equipped with symmetric planetary-type vibration exciter

Vitaliy Korendiy1 , Volodymyr Gurey2 , Volodymyr Borovets3 , Oleh Kotsiumbas4 , Vasyl Lozynskyy5

1, 2, 3Department of Robotics and Integrated Mechanical Engineering Technologies, Lviv Polytechnic National University, Lviv, Ukraine

4Department of Motor Vehicle Transport, Lviv Polytechnic National University, Lviv, Ukraine

5Department of Electronics and Information Technology, Lviv Polytechnic National University, Lviv, Ukraine

1Corresponding author

Vibroengineering PROCEDIA, Vol. 43, 2022, p. 7-13. https://doi.org/10.21595/vp.2022.22703
Received 14 May 2022; received in revised form 22 May 2022; accepted 29 May 2022; published 13 June 2022

57th International Conference on Vibroengineering, Istanbul, Turkey, June 13, 2022

Copyright © 2022 Vitaliy Korendiy, 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.
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Abstract.

Vibration exciters are of the most important parts of vibratory technological equipment. Among a great variety of exciters, the inertial ones are currently the most widely used due to their design simplicity, well-studied control techniques, and relatively large efficiency. The present paper deals with a prospective type of inertial exciters based on a planetary mechanism. The main purpose of this research consists in substantiating the possibilities of providing triangular, rectangular, hexagonal, and other paths of oscillations of a single-mass vibratory system driven by a symmetric planetary-type vibration exciter. The mathematical model of the system motion is developed using the Euler-Lagrange equations, and the following numerical modeling is carried out with the help of the Runge-Kutta methods integrated in the Mathematica software. Virtual experiments are conducted in the SolidWorks software using the 3D-model of the vibratory system. The obtained results are presented in the form of time response curves and motion paths of the oscillating body under different operational conditions. The major scientific novelty of the paper consists in substantiating the parameters of the symmetric planetary-type vibration exciter allowing for generating triangular, rectangular, hexagonal oscillations of the single-mass vibratory system. The obtained results can be effectively used while designing new and improving existent vibratory technological equipment, e.g., conveyors, screens, feeders, sieves, etc.

Generating various motion paths of single-mass vibratory system equipped with symmetric planetary-type vibration exciter

Highlights
  • The possibilities of providing triangular, rectangular and hexagonal paths of oscillations of a single-mass vibratory system with a symmetric planetary-type vibration exciter are substantiated.
  • The mathematical model of the system motion is developed and the following numerical modeling is carried out in the Mathematica software. Virtual experiments are conducted in the SolidWorks software.
  • The obtained results are presented in the form of time response curves and motion paths of the oscillating body under different operational conditions.
  • The parameters of the symmetric planetary-type vibration exciter allowing for generating triangular, rectangular, hexagonal oscillations of the single-mass vibratory system are considered.

Keywords: vibratory technological equipment, planetary mechanism, mathematical model, operational conditions, numerical modeling, 3D-model, simulation.

1. Introduction

Vibratory technological equipment is widely used in various industries in order to efficiently perform the conveying, feeding, screening, sieving, compacting, polishing, and a wide range of other technological operations. In order to improve the operational efficiency of vibratory machines, numerous researchers and designers work out the possibilities of developing the enhanced excitation mechanisms. Among a great variety of vibration exciters, the inertial ones are currently of the most widely used due to their design simplicity, well-studied control techniques and relatively large efficiency [1]-[5]. In order to provide the controllable motion paths of the vibratory equipment working members, the multi-motor drives are sometimes used. For example, the paper [1] investigates the possibilities of changing the vibration direction angle of the elliptical vibrating screen driven by two motors. The rectilinear oscillations of the five-mass vibratory system excited by two counter-rotating unbalanced rotors are studied in [2]. The dynamic behavior of the vibratory machine equipped with the eccentric self-regulating unbalanced rotor and driven by an induction motor is investigated in [3]. The paper [4] presents the motion equations of the single-, double- and three-mass vibratory systems performing rectilinear oscillations excited by passive auto-balancers. In [5], the authors studied the dynamics of the vibration machine excited by an unbalanced rotor driven by an electric motor with limited power.

On the other hand, the operational efficiency of the vibratory technological equipment can be significantly improved by implementing the planetary-type inertial vibration exciters [6]-[11]. The paper [6] analyses the dynamics and substantiates the occurrence of the self-resonance operational conditions of the symmetric planetary-type vibration exciter. In [7], the author proposed the enhanced design of the vibration exciter allowing for generating the rectilinear (directed) oscillations. The planetary-type adjustable exciter with two unbalanced rotors synchronized by the chain transmission is studied in [8]. The paper [9] is dedicated to investigating the operational conditions of the self-regulating unbalanced rotor used for exciting oscillations of vibration machines with changeable technological load. The dynamic and efficiency parameters of the asymmetric planetary-type vibrations exciters are thoroughly investigated in [10] and [11].

Considering numerous scientific publications related with inertial exciters, in particular, those [1]-[11] mentioned above, it can be concluded that the problems of implementing the planetary-type exciters for providing the controllable kinematic and dynamic parameters of the vibratory equipment are not thoroughly investigated. Therefore, the present paper continues the authors’ previous investigations presented in [12]-[14] and devoted to improving the controllable vibration exciters able to ensure the efficient operation of various vibratory equipment under the changeable loading conditions. The major scientific novelty of the paper consists in substantiating the parameters of the symmetric planetary-type vibration exciter allowing for generating triangular, rectangular, hexagonal, and other paths of oscillations of the single-mass vibratory system.

2. Research methodology

2.1. Dynamic diagrams of vibratory systems with symmetric planetary-type exciters

Let us consider the single-mass vibratory system able to oscillate in two mutually perpendicular directions (Fig. 1). The system is set into motion due to the action of the inertial forces upon the oscillating body. These forces arise when the planet gear rolls on the outside of the sun gear pitch circle, or on the inside of the ring (annual) gear pitch circle (see Fig. 1). In the considered cases, the corresponding sun gear or ring gear is fixed to the oscillating body. The driving motor shaft is located at the hinge O and rotates the carrier OD in clockwise direction. Considering the symmetric planetary-type vibration exciter, the distance AO is equal to the pitch circle radius R1 of the corresponding fixed gear. If the radius of the planet gear pitch circle is denoted as R2, the length lOD of the carrier OD can be determined as lOD=R1±R2, where the “plus” sign is used in the case of the fixed sun gear, and the “minus” sign is applied when the ring gear is fixed to the oscillating body. The mass of the oscillating body is equal to m1, whilst m2, m3 denote the masses of the planet gear and the additional disturbing body rigidly connected with the planet gear at the distance lDE=R3 from the hinge D.

Fig. 1. Dynamic diagrams of the single-mass vibratory systems with planetary-type exciters

Dynamic diagrams of the single-mass vibratory systems with planetary-type exciters

The oscillating body performing the periodic plane-parallel motion is restrained by the system of horizontal and vertical spring-damper elements characterized by the corresponding stiffness and damping coefficients kx, cx, ky, cy. If the direction of the carrier OD rotation is characterized by the angle φ and is considered to be clockwise, the direction of the planet gear and the disturbing body rotation around the hinge D depends on the exciter type: with fixed sun gear or with fixed ring gear. The corresponding directions are defined in Fig. 1 by the angle γ that can be determined by the following expression: γ=γ0+φR1/R2.

2.2. Mathematical model describing the system motion

Considering the angle φ as a controllable parameter, let us use the coordinate system xOy to define the hinge O position in a vertical plane. In this case, the hinge O is assumed to be coincident with the oscillating body’s mass center. Therefore, it is enough to adopt two generalized coordinates x, y to uniquely describe the system motion. Using the Euler-Lagrange equations, the mathematical model of the system dynamics can be derived as follows:

(1)
m1+m2+m3x¨+cxx˙+kxx=m2+m3R1+kR2φ˙2cosφ+φ¨sinφ-m3R3kR1+R2R2φ˙2kR1+R2R2cosφ+kγ0+R1R2φ+φ¨sinφ+kγ0+R1R2φ,
(2)
m1+m2+m3y¨+cyy˙+kyy=m2+m3R1+kR2φ˙2sinφ-φ¨cosφ+m3R3kR1+R2R2φ˙2kR1+R2R2sinφ+kγ0+R1R2φ-φ¨cosφ+kγ0+R1R2φ,

where k is the coefficient defining the type of the planetary gear mechanism: k= 1 in the case of the fixed sun gear; k= –1 when the ring gear is fixed to the oscillating body.

2.3. Simulation model of the vibratory system developed in the SolidWorks software

In order to carry out the virtual experiments aimed at analyzing the correctness of the derived mathematical model, the corresponding 3D-design of the vibratory system is developed in the SolidWorks software (see Fig. 2). The system consists of the oscillating body 1 suspended from the unmovable base 3 by the spring-damper elements 2. The carrier (crank) 4 is set into motion by the motion drive 5, and uniformly rotates around the horizontal axis fixed in the mass center of the oscillating body 1. The planet gear 6 rolls on the outside of the sun gear 7 that is connected to the body 1. The unbalanced (disturbing) mass 8 is fixed on the planet gear 6.

Fig. 2. Simulation model of the vibratory system equipped with the planetary-type exciter

Simulation model of the vibratory system equipped with the planetary-type exciter

3. Results and discussion

3.1. Numerical modeling of the system motion in the Mathematica software

Let us consider the case of steady-state oscillations of the vibratory system equipped with the symmetric planetary-type vibration exciter in which the sun gear is fixed (k=1). The forced frequency is constant: ω= 157 rad/s. Therefore, the motion of the carrier is performed according to the following law: φ=φ0+ωt. To carry out further numerical modeling, the following input parameters are introduced: φ0= 0, γ0= 3.14, m1= 30 kg, R1= 0.088 m, R3= 0.04 m, kx=ky= 3∙106 N⁄m, cx=cy= 100 (N∙s)/m. The masses m2, m3, and radius R2 are considered as controllable parameters defining the paths (trajectories) of the oscillating body.

The results of numerical modeling (Fig. 3) are presented in the form of time dependencies of the basic kinematic characteristics of the system motion: horizontal and vertical displacements, velocities, accelerations. In addition, the motion paths (trajectories) of the oscillating body are plotted under different inertial and geometric parameters of the planetary-type vibration exciter. For example, the triangular path of the body oscillations is obtained at: m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m (Fig. 3(a)). The rectangular path is observed at: m2= 1.1 kg, m3= 0.08 kg, R2= 0.044 m (Fig. 3(b)). The hexagonal path is drawn at: m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m (Fig. 3(c)). The corresponding analytical relations between inertial and geometric parameters of the symmetric planetary-type vibration exciter providing certain motion paths of the oscillating body will be derived in further investigations. In the present paper, let us consider the kinematic characteristics of the body at the mentioned parameters.

Fig. 3. Kinematic characteristics of the system motion at different design parameters of the planetary-type vibration exciter: a) m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m; b) m2= 1.1 kg, m3= 0.08 kg, R2= 0.044 m; c) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

Kinematic characteristics of the system motion at different design parameters of the planetary-type vibration exciter: a) m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m; b) m2= 1.1 kg, m3= 0.08 kg,  R2= 0.044 m; c) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

a)

Kinematic characteristics of the system motion at different design parameters of the planetary-type vibration exciter: a) m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m; b) m2= 1.1 kg, m3= 0.08 kg,  R2= 0.044 m; c) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

b)

Kinematic characteristics of the system motion at different design parameters of the planetary-type vibration exciter: a) m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m; b) m2= 1.1 kg, m3= 0.08 kg,  R2= 0.044 m; c) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

c)

All the motion paths considered above (triangular, rectangular, hexagonal) are characterized by the largest horizontal and vertical displacements (swings, peak-to-peak values) of about 3 mm. The oscillating body’s horizontal and vertical speeds vary in the range of –0.35,…, 0.35 m/s, while the accelerations change within –80,…, 80 m/s2. All the characteristic differences between displacements, velocities and accelerations of the oscillating body at different inertial and geometric parameters of the planetary-type vibration exciter can be observed in Fig. 3.

3.2. Simulation of the system motion in the SolidWorks software

Applying the same geometric, inertial, damping, and stiffness parameters of the vibratory system as the ones used for carrying out numerical modeling, let us conduct virtual experiments of the system motion in the SolidWorks software. The obtained simulation results are presented in Fig. 4. The starting (transient, unsteady) conditions lasts about 1,…, 1.5 s. Under the steady-state oscillations, the rectangular and hexagonal motion paths of the body, as well as its other kinematic characteristics satisfactorily agree with the ones obtained by numerical modeling.

Fig. 4. Kinematic characteristics of the system motion simulated in the SolidWorks software at different design parameters of the planetary-type vibration exciter: a) m2= 1.1 kg, m3= 0.08 kg, R2= 0.044 m; b) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

Kinematic characteristics of the system motion simulated in the SolidWorks software at different design parameters of the planetary-type vibration exciter: a) m2= 1.1 kg,  m3= 0.08 kg, R2= 0.044 m; b) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

a)

Kinematic characteristics of the system motion simulated in the SolidWorks software at different design parameters of the planetary-type vibration exciter: a) m2= 1.1 kg,  m3= 0.08 kg, R2= 0.044 m; b) m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m

b)

4. Conclusions

The paper studies the dynamics of the single-mass vibratory system equipped with the symmetric planetary-type vibration exciter. The mathematical model of the system motion is derived. The results of numerical modeling performed in the Mathematica software satisfactorily agree with the simulation results obtained in the SolidWorks software. The starting conditions lasts 1,…, 1.5 s. Under the steady-state oscillations of the body, the triangular path is obtained at: m2= 0.8 kg, m3= 0.03 kg, R2= 0.088 m; the rectangular path – at: m2= 1.1 kg, m3= 0.08 kg, R2= 0.044 m; the hexagonal path – at: m2= 1.3 kg, m3= 0.04 kg, R2= 0.022 m. All the motion paths are characterized by the largest horizontal and vertical displacements of about 3 mm. The oscillating body’s horizontal and vertical speeds vary in the range of –0.35,…, 0.35 m/s, while the accelerations change within –80,…, 80 m/s2. The obtained results can be effectively used while designing new and improving existent vibratory technological equipment, e.g., conveyors, screens, feeders, sieves, polishing machines, compactors, etc.

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