Basis of the parameters of the spin extractor tool on the interned spinning machine

. The article presents an effective new constructive scheme and the principle of operation of the exhaust device of the ring spinning machine. The mathematical model and the results of solving the problem of oscillations of the axis of the composite squeezing roller of the drawing apparatus of the spinning machine have been determined. The recommended values of the roller parameters are given. Based on the analysis of the research results and the conditions for obtaining high-quality yarn, the recommended parameter values for each squeezing rollers were determined.


Introduction
On a ring spinning machine, the fiber is stretched on a spinning machine and sufficient twists are given [1]. According to the existing technology, in the elongation zone, the fibrous strands are stretched due to the difference in velocities between the three rifle and three elastic-coated compression (loading) pairs, the rifles perform the corresponding twists [2].
The load on each load roller is carried out separately by means of springs mounted on a single lever. Each stretch juf T installed separately before the gaskets. To control the movement of the fibers, two bands are installed in the second elongation zone : upper and lower. The lower belt tension is done using a spring bracket. The spacing between the upper and lower bars of the strips can be changed depending on the thickness of the product [2,3]. The change in distance between the slats is changed by means of interchangeable supports. The disadvantage of the stretching device considered is that the fiber product is not evenly distributed in the stretching zones, moreover, the flexible interchangeable bushings do not allow the fibers in the yarns to have the same elongation [4].

Analysis of the oscillations of the loading roller shaft of the stretching tool
We construct a differential equation that represents the oscillations of the axis of the flexible bushing shaft of each loader with a loading device: (1) where is the amplitude and frequency of change of the external force acting on the roller shaft from the -pin.
-rubber and outer bushing virginity coefficients, the coefficient of virginity of -pin are the dissipation coefficients of the rubber and outer bushings and the plug, respectively.
-target mass; -rubber bushing mass; is the mass of the elongated plug in the part corresponding to the width of the roller.
The solution of the obtained differential equation (1) using the existing analytical method we obtain the following expression: (2) where, is the spatial shift of the impact force.
To obtain a numerical solution of the problem, the initial calculated values of the parameters were obtained in the following intervals: kg; kg; kg; kg; ; ; Based on the numerical solution of the problem, the law of vibration of the axis of the elongated tool shaft on the ring spinning machine was obtained in different parameters, as a result of which graphs of the interaction of system parameters were constructed. Based on the analysis of the graphs shown in Figure 2, it was found that the oscillation coverage of the roller axis of the first loading elastic element increases linearly with the amplitude of the impact force. In particular, when the amplitude of the impact force increases from 0.29 N to 2.84 N, the vertical oscillation coverage of the third loading roller axis increases in a linear connection from 0,18·10 -3 m to 1,06·10 -3 m, while the vibration of the second loading roller axis increases. coverage increases from 0,25·10 -3 m to 1,52·10 -3 m.
Respectively, we can see that the oscillation coverage of the first loading roller axis increases from 0,31·10 -3 m to 2,51·10 -3 m ( Figure 2, Figures 1, 2, 3). Given the experimental results and the unevenness of the elongated shaft, the impact force is in the range of (2.  Figure 3 shows graphs of the change in vibration coverage of the axes of the elongated rollers relative to the stiffness of the flexible bushings. The coupling graphs are obtained at the calculated value, when the outer bushing coefficient of the inner bushing of the first loading roller changes, the inner bushing coefficient does not change. This procedure is the same for rollers with all three loading components. The graphs in Figure 3 are constructed based on the given virginity coefficients of both rubber bushings, i.e., where the virginity has a nonlinear rigid characteristic. Based on the analysis of the graphs in Figure 3a, the oscillation coverage of the roller axis is 2.27 · 10-when the applied mass of the first roller is increased from 0.6 · 10 -3 N / m to 3 · 10 -3 N / m when the applied mass is 0.15 kg. Decreases in nonlinear regularity from 3 m to 1.23 · 10 -3 m. If the given mass is taken as 0.2 kg, the vibration coverage is reduced from 2.5 · 10 -3 m to 0.67 · 10 -3 m. To ensure that the vibration coverage for the first roller does not exceed (0.7 ÷ 1.1) · 10 -3 m, it is recommended that the coefficient of virginity of the rubber bushings be in the range (1.68 ÷ 2.7) · 10 3 N / m. The recommended coefficients for the rubber bushings of the second and third loading rollers, respectively, are in the range of Сk2=(1,85÷2,8)·10 3 N / m and Сk3=(2,6÷3,75)·10 3 N / m.
It is known that the frequency of specific vibrations with the frequency of change of force acting on the load compressing the rollers leads to resonance modes, the unevenness of the mutual compression of the fibers. Therefore, it is important to determine the limits of variation of specific and forced oscillation frequencies.
While the rotational frequencies of the rollers are mainly (120 ÷ 180) rpm in existing spinning machines, the vibration frequencies of the roller shafts are reciprocating (2.0 ÷ 5.0) in the range of с -1 .    Figure 4 shows the dependence of the change in the specific vertical vibration frequencies of the loading rollers of the spinning machine stretching tool on the coefficients of elasticity given by the flexible bushings. According to the analysis of the graphs in Figure 4a, the coefficient of virginity of the flexible loading bushings of the first loading roller increased from 0.3 · 10 -3 N/m to 2.8 · 10 -3 N / m and the specific oscillation frequency of the roller was 1, when mk1 = 0.185 kg. Increases in linear regularity from 6 с -1 to 7.7 с -1 . When the applied mass of the roller is 0.115 kg, its axial vertical oscillation frequency increases in the range of 6.05 с -1 to 2.02 с -1 . It is recommended that the specific vibration frequency of the first roller be in the range of (1.1 ÷ 1.8) с -1 to ensure the recommended Ck = (1.68 ÷ 2.7) · 10 -3 N / m values.
Correspondingly, according to the analysis of Figure 4b, when the coefficient of virginity of the flexible rollers of the composite roller is increased from 0,31·10 3 Н/м to 3.8 · 10 3 N / m, the vertical specific oscillation frequency of the axis is from 5.1 c -1 to 29c -1 . increases in nonlinear regularity. In this case, the specified mass of the roller was taken as 0.13 kg. If mk2=0,20 kg, the specific oscillation frequency increases from 2,7 с -1 to 21.7с -1 . Similarly, when the specified mass of the third roller is taken as 0.22 kg, its specific oscillation frequency f1=(6,5÷32)с -1 when the applied virginity coefficient increases to Ck = (0.75 ÷ 5.

Conclusion
A differential equation and an analytical solution representing the oscillations of the axis of the loading rollers of the ring spinning machine are obtained. A graph of the dependence of the vertical oscillation coverage of the shafts of the elongated tool shafts on the change in the amplitude of the resistance to elongation of the shaft and on the stiffness of the flexible bushings was constructed. Graphs of the dependence of the vertical specific vibration frequencies of the axes of the loading rollers on the change of the coefficients of virginity given by their rubber bushings are obtained. The recommended values of the parameters are based.