Abstract
A coal mine hoisting system includes two parts, one is a constant-length cable system, and the other is a variable-length cable system. In this paper, the nonlinear dynamic modeling of a coal mine hoisting system is established through Hamilton’s principle. The nonlinear partial differential equations of the coal mine hoisting system are discretized into ordinary differential equations by the fourth-order Galerkin truncation. The nonlinear dynamic responses and four key kinematic and structural parameter analysis of the coal mine hoisting system in the acceleration phases, constant velocity phases, and deceleration phases are given. The results show that the axial vibration displacements of the constant-length cable are an order of magnitude smaller than that of the variable-length cable. The load has the greatest effect on the axial vibration displacement of the hoisting cable. Adversely, the speed has the least effect on the axial vibration displacement of the hoisting cable.
Highlights
E parameter optimization criterion is proposed for the suspension rope collision phenomenon of the multirope friction hoist [8]
E length of the constant-length cable is much shorter than the variable-length cable in coal mine hoist. erefore, the axial vibration displacements of the constant-length cable are at an order of magnitude smaller than the variable-length cable. e axial vibration characteristics of the constantlength cable in lifting and lowering are similar because the length of the constant-length cable is constant. e length of the variable-length cable is time-varying; axial vibration characteristics of the variable-length cable in lifting and lowering process are different. e axial vibration frequency of variable-length cable in lifting process is greater than that in lowering process. is shows that the axial vibration of the lifting process is intense compared to the lowering process
The maximum axial vibration displacement of the variable-length cable in the lifting process is similar to the downward process, which occurs near the bottom of the shaft
Summary
E parameter optimization criterion is proposed for the suspension rope collision phenomenon of the multirope friction hoist [8]. According to Equation (7), the axial vibration equations of the hoisting cable are obtained as follows: ρzu2cz(tx2 , t) zu2c (x, zxzt t) In the three operating phases of acceleration, constant velocity, and deceleration, the axial vibration responses of the hoisting cable is different.
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