Study on Online Analysis of Transfer Function of Variable-Speed Rolling Mill Motor with Shaft Torsional Vibration Systems

Tamaoki, Toshifumi; Takanezawa, Makoto; Kimoto, Masahide; Morita, Noboru; Hoshino, Takeo; Hashizume, Kenji

doi:10.1541/ieejias.131.844

Cited by 7 publications

(4 citation statements)

References 0 publications

Supporting

Mentioning

Contrasting

Order By: Relevance

“…The basic parameters of side cutter drive motor were as follows: rated voltage U e = 24 V, rated current I e = 9.19 A, rated speed n e = 3600 r/min, rated power P e = 180 W, moment of inertia J = 0.003 kg m 2 . According to empirical formula, motor rotating voltage coefficient C e = 0.058, electric time constant T a = 0.012 s, and mechanical time constant T m = 0.24 s. 15 The transfer function between the motor speed and the input voltage is as follows H(s) = 17:24 0:0029s 2 + 0:24s + 1 ð11Þ…”

Section: Control Parameter Turningmentioning

confidence: 99%

Cutting speed follow-up adjusting system of bidirectional electric drive side cutter for rape combine harvester

Guan

et al. 2020

Science Progress

View full text Add to dashboard Cite

In rape combine harvester, side cutter must be equipped to cut off tangled rapeseed twigs. Inappropriate cutting speed would increase the repeated cutting and missing cutting of side cutter, which lead to serious header loss. In allusion to the problems mentioned above, bidirectional electric drive side cutter and a cutting speed follow-up adjusting system were proposed. The kinematic law of side cutter blades was analyzed. The trajectory, velocity, and acceleration of the two blades were the same, but the phase difference is π. Numerical simulation of cutting areas at different cutting speed ratios was carried out and the best cutting speed ratio was determined to be 1.1. Cutting speed follow-up adjusting system was designed based on matching relationship between combine harvester forward speed and side cutter cutting speed. Cutting speed follow-up adjusting system was designed with proportional–integral–derivative (PID) algorithm. The control parameters were determined to be Kp = 1.3, Ki = 4.3, Kd = 0.007. Simulation showed that the maximum overshoot of the system was 4.3%, steady-state error was 0.24%, and the rise time was 0.036 s. The cutting speed follow-up adjusting system was applied to the 4LZ-6T-type rape combine harvester. Experimental results showed that the side cutter cutting speed error was within 1.5%. When forward speed changed, the cutting speed response delay time was 1.5 s. The rape combine harvester header average loss was 2.96% and side cutter average loss was 0.81%. Compared to the fixed speed cutting, header loss was reduced by 14.05% and side cutter loss was reduced by 34.76%. The research can reduce the loss of rapeseed combine harvester and provide theoretical basis for the design of rapeseed combine harvester.

show abstract

Section: Control Parameter Turningmentioning

confidence: 99%

Cutting speed follow-up adjusting system of bidirectional electric drive side cutter for rape combine harvester

Guan

et al. 2020

Science Progress

View full text Add to dashboard Cite

show abstract

“…The traditional research about four-high and six-high plate mill vibrations, including a single mode vibration or a coupling mode vibration, belongs to a simplified onedimensional or two-dimensional/planar vibration analytical mode. Meanwhile, for the traditional coupling mode vibration analysis, including the vertical-torsional vibrations studied by some researchers [5][6][7], vertical-horizontal vibrations studied by some researchers [8][9][10], mechanical-hydraulic coupling vibrations studied by Ma [11], mechanical-electrical coupling vibrations studied by Zhong et al [12] and mechanical-electrical-hydraulic coupling vibrations studied by Yan [13], it is all done based on some coupling conditions. In reality, the true mill vibrations take place in six degrees of freedom (DOF), i.e., there are spatial vibration behaviours for a mill according to some recent research studied by our team [14][15][16][17][18].…”

Section: Introductionmentioning

confidence: 99%

Spatial vibration characteristics of six-high cold strip rolling mills

Zheng

Shen

et al. 2017

Ironmaking & Steelmaking

View full text Add to dashboard Cite

The vibration characteristic technical indexes of six-high cold strip rolling mills are not given, and thus the chatter vibrations cannot be predicted and prevented. The strip rolling mills can be divided into the non-statically determinate and statically determinate mills according to the statically determinate theory of mechanism. This statically determinate characteristic of the mill does not be distinguished in the traditional mill vibration analysis. In this paper, for these two distinct mill configurations, a complete spatial vibration characteristic analysis involving six degree of horizontal, vertical, axial, torsional, cross and swinging vibration will be presented based on the modified multi-body Riccati transfer matrix method. The results demonstrate that the vibration characteristics of the statically determinate mills are much better that that of nonstatically determinate ones, which significantly indicates the perniciousness of the offset distance and uncontrolled side clearance, and clarifies the necessity of upgrading of the traditional mills.

show abstract

“…The torsional vibration problem of lathe spindle system with unbalanced workpiece was studied [9]. Torsional vibration analysis about axis of the rolls on the transfer function of variable-speed rolling mill motor with shaft systems was studied [10]. The nonlinear torsional vibration characteristics caused by the strip rolling mill's drive trains with angular and radial backlash were investigated, and the torsional vibration fault feature caused by backlash was analyzed under static and dynamic rolling load [11].…”

Section: Introductionmentioning

confidence: 99%

Nonlinear Torsional Vibration Dynamics Behaviors of Rolling Mill’s Multi-DOF Main Drive System under Parametric Excitation

Han

Shi

Xia

2014

Journal of Applied Mathematics

View full text Add to dashboard Cite

Considering the influence caused by joint angle, nonlinear damping, and nonlinear rigidity, the nonlinear torsional vibration dynamical modeling of the multi-DOF rolling mill’s main drive system is established. To analyze the coupled equations by analytic method, the equations are decoupled by transforming them into principal coordinates. The amplitude-frequency characteristic equations are obtained by multiscale method. Furthermore, numerical example based on the 1780 rolling mill’s main drive system of some Steel Co. is given to illustrate the effects of the resonance on the response of the system. The relationship between amplitude and frequency varies according to the parameters changes of nonlinear stiffness, nonlinear friction damping, torque disturbance, and joint angle. During the rolling process, the limited joint angles range is obtained and the variation rules of the joint angle caused by the nonlinear damping, nonlinear stiffness, and the disturbance torque are gained. The results present that the rolling mill can work more stably with the joint angle at a range from 2° to 8° by controlling the value of parameters. The research results provide a theoretical basis and reference for analyzing torsional vibration of rolling mill’s transmission system caused by joint angle.

show abstract

Study on Online Analysis of Transfer Function of Variable-Speed Rolling Mill Motor with Shaft Torsional Vibration Systems

Cited by 7 publications

References 0 publications

Cutting speed follow-up adjusting system of bidirectional electric drive side cutter for rape combine harvester

Cutting speed follow-up adjusting system of bidirectional electric drive side cutter for rape combine harvester

Spatial vibration characteristics of six-high cold strip rolling mills

Nonlinear Torsional Vibration Dynamics Behaviors of Rolling Mill’s Multi-DOF Main Drive System under Parametric Excitation

Contact Info

Product

Resources

About