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7SCIENTIFIC PROGRESS VOLUME 3 I ISSUE 4 I 2022
ISSN: 2181-1601
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THEORETICAL STUDY OF ACTIVITY CONVEYOR DRIVING
Bahodir Husanovich Ergashev
Fergana Polytechnic Institute
ANNOTATION
This paper aims to address the problems that can be encountered in the transportation of dolomite raw materials, in particular, such as the belt deviating from its direction under the influence of forces generated by dolomite loading. Keywords: conveyor, dolomite, pulley, shear force, belt, transport
Depending on the frequency and power of the electric motor, the calculated speed of movement on pulleys of different diameters is determined as follows:
v =iIDi-n, v = (1)
1 60 2 60 Where D 1 , D 2 are the diameters of the drive and driven pulleys.
rotational force F t and the equally acting F V forces are determined from the formula in house q according to the scheme of forces in belt extensions (Fig. 1):
FB = ^ (2)
%• D • n
Where P is the required power of the electric motor; k is the coefficient taking into account the type of belt.
The force that moves the belt according to the force scheme FCfl, is formed by the non-parallel position of the axes of rotation of the pulleys and is determined as follows:
60 • k • P .
Fcs =—;;—sin P (3)
%• D • n
Where □ Dis the angle of inclination of the drive and driven pulleys relative to the axes of rotation.
We now determine the formula for the shear force resulting from the non-parallel position between the axes of rotation of the drums conveying the dolomite.
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The formula for the force that moves a conveyor belt that carries limestone
F
Cfl
k • PT rç-V
sin P
(4)
Here □ □ is the general F.I.K.;
V is the linear speed of the belt conveyor; P T - required power on drum shaft:
p = ^Ts
T 1000 (5) Where □ Dis the coefficient taking into account the performance characteristics of the conveyor . Drum torque :
T6 - (SHE SCE )
D(
2
Here S nb , S sb - tensile strength of the conveyor escape and traction parts:
Sm = S! + (q. + q >. ) • m • L
S1
TT
SCE ~ qn •m •LTP
£
(6)
(7)
Where □ Dis the coefficient of resistance to bending of the drums; q l is the weight of the tape pogon meter;
q xl is the weight per meter of the load falling on the loaded part of the belt conveyor;
m is the coefficient taking into account the operating conditions of the conveyor; L TR - conveyor length.
(q * + q ™) • ^
S1 -
,2 p
8 • f
f - 0,02 • /
(8)
f is the magnitude of the strain at the point of loading the tape; Here I p - the distance between the roller bearings;
q x
Q
3,6 • V' = 10 • B-(§• z + ^ +S2); Where Q is the conveyor productivity , t / h; Uzbekistan www.scientificprogress.uz
(9)
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B - width of the conveyor belt, m; z is the number of gaskets;
□ □ □ - thickness of rubber gaskets, mm;
□ □ □ □ □- thickness of the lining on the working part, mm;
□ □□□□- is the thickness of the lining on the idle part, mm.
When analyzing the results of the shear force calculation, it was found that the change in force value is affected not only by the angle of inclination between the axes of rotation of the drums, but also by the speed mode and belt types.
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