Russian Journal of Applied Chemistry, 2008, Vol. 81, No. 6, pp. 1128−1131. © Pleiades Publishing, Ltd., 2008.
Original Russian Text © A.A. Garabazhiu, 2008, published in Khimicheskaya Promyshlennost’, 2008, Vol. 85, No. 2, pp. 88−92.
MODELLING AND CALCULATION
OF TECHNOLOGICAL PROCESSES
Simulation of Optimum Thickness of Acceleration Blades
of a Rotary Centrifugal Grinder
A. A. Garabazhiu
Belarussian State Technological University, Minsk, Belarus
Received March 19, 2007
Abstract—We developed a method of optimum thickness simulation for the acceleration blades of the rotary cen-
trifugal grinder. We also deduced an empirical relation that sufﬁ ciently exactly determines a minimum thickness
of the acceleration blade in dependence on a currents grinder radius.
The energy-saving rotary centrifugal grinder with
continuously ﬂ ow-through classiﬁ cation of a product
was developed in the Belarussian State Technological
University ten years ago and was still in great demand in
various branches of industry of Belarus. Today research
workers of the university under Prof. E. I. Levdanskii
developed a line of energy-saving rotary centrifugal
devices of analogues operation principles and of various
applications [1, 2].
Design features and principle of operation of the
energy-saving rotary centrifugal grinder with con-
tinuously ﬂ ow-through classiﬁ cation of product were
set out in [2−5].
At developing the industrial sample of this grinder a
simulation of the optimum thickness of the main (or the
most important) design elements arouse great practical
interest. An algorithm and results of a strength design of
a grinder rotary disk and a bearing plate were presented
in . Estimation of the optimum thickness of the main
design elements of the rotary centrifugal grinder allows
acquisition of high reliability and wear life of the device
as a whole.
A rotor of the energy-saving grinder with continuously
ﬂ ow-through classiﬁ cation of a product [2−5] has eight
acceleration radial blades that are ﬁ rmed to the rotary disk
of the grinder at a right angle to its upper end surface
Fig. 1. A scheme for the strength design of the acceleration blade of the rotary centrifugal ginder. r
= 0.12 m, r
= 0.3 m,
δ = 0.005 m, h = 0.08 m, ω = 314 rad s
, α = 45°.