Experimental determinations concerning the weaving machine vibrations.
Vigaru, Cosmina ; Luca, Gheorghe ; Rusu, Lucian 等
1. INTRODUCTION
In the case of weaving machine it is difficult to identify each
source of vibration. In weaving process all mechanisms are working
simultaneously and generate vibrations having different amplitudes and
directions. There are many theoretical studies regarding the influence
of the vibrations on the weaving process (Reicher & Dragoi, 1985),
(Demeulare, 2004), but few experimental results. Most of the studies
consider only one mechanism of the machine or vibrations on a single
direction in space. The used methods for these studies are based on the
classical vibration theory or finite element method (Deger, 2000).
The aim of the whole study was to experimentally evaluate the
resultant vibrations of a weaving machine on a set of points and each
direction. Based on the experimental results the final goal is to reduce
the vibrations level. In the framework of the performed experimental
study of vibration influence, the measurements were effectuated by
placing the transducer on different elements of the machine, to record
longitudinal, transversal and vertical vibrations. The paper presents
only the vertical vibrations obtained from the transducer fixed on the
launch box.
2. THEORETICAL AND EXPERIMENTAL STUDY
The most important sources of vibrations for the weaving process
are: the slay mechanism, the launching mechanism, the shedding mechanism
and the warp regulator.
For the experimental study of vibrations, the measurements were
effectuated by placing a Bruel&Kjaer accelerometer on different
elements of the machine, to record longitudinal, transversal and
vertical vibrations. The experimental data were analyzed following the
cyclical diagram for the most important mechanism for the weaving
process (Stefanuta, 1997).
2.1 Cyclical diagram for the shedding mechanism
During the weaving process, the cycle of shedding mechanism motion
corresponds to two complete rotations of the main shaft.
The time interval corresponding to shedding mechanism motion was
determinate based on the main shaft rotations: [[alpha].sub.1]--the
rotation angle of main shaft, corresponding to warp thread lifting;
[[alpha].sub.2]--the rotation angle of main shaft, corresponding to the
upper shedding mechanism stationary position; [alpha]3--the rotation
angle of main shaft, corresponding to warp thread during the descending
motion; [[alpha].sub.4]--the rotation angle of main shaft, corresponding
to the lower stationary position of the shedding mechanism.
Considering that the angular velocity of main shaft is constant it
can be written:
[[alpha].sub.1] + [[alpha].sub.2] + [[alpha].sub.3] +
[[alpha].sub.4] = [720.sup.0] (1) [t.sub.1] + [t.sub.2] + [t.sub.3] +
[t.sub.4] = T
where: [[alpha].sub.1], [[alpha].sub.2], [[alpha].sub.3],
[[alpha].sub.4]--represent the main shaft rotation angles corresponding
to each phase; [t.sub.1], [t.sub.2], [t.sub.3], and [t.sub.4] represents
the corresponding time intervals, for each phase; T--represents the
total duration of two rotations of the main shaft.
During the movement of the shedding mechanism, the main shaft
rotation angles corresponding to the warp thread lifting and descent are
equals: [[alpha].sub.1] = [[alpha].sub.3] = [180.sup.0]; also, the
angles of stationary shedding mechanism in superior and inferior
positions [[alpha].sub.2] = [[alpha].sub.4] = [40.sup.0] are equals.
The obtained values of the considered time intervals are: [t.sub.1]
= [t.sub.3] = 0.120s; [t.sub.2] = t4 = 0.027 s.
2.2 Cyclical diagram for the warp regulator
In the case of warp regulator the cyclogram is given by the angle
of the main shaft rotation: [[alpha].sub.1] = [215.sup.0]--the main
shaft rotation angle of the weaving machine corresponding to warp
regulator which released the necessary amount of warp; [[alpha].sub.2] =
[85.sup.0]--the main shaft rotation angle of the weaving machine
corresponding to return of warp regulator; [[alpha].sub.3] =
[290.sup.0]--the main shaft rotation angle of the weaving machine
corresponding to stationary warp regulator.
2.3 Cyclical diagram for the slay mechanism
For the Sulzer weaving machine the cyclogram of the slay mechanism
is given by the following angles: [[alpha].sub.1] = [70.sup.0]--the
rotation angle of main shaft, corresponding to the moment when the slay
is moving in extreme frontal position; [[alpha].sub.2] = [70.sup.0] the
rotation angle of main shaft, corresponding to the moment when the slay
is moving in extreme posterior position; a3 = [220.sup.0]--the rotation
angle of main shaft, corresponding to the moment when the slay is in
extreme posterior position.
2.4 Cyclical diagram for the launching mechanism
The cyclical diagram of the launching mechanism is obtained
following the four phases of a complete rotation of the main shaft. A
complete cycle for the launching mechanism is characterized by the phase
angles:
[[alpha].sub.1] + [[alpha].sub.2] + [[alpha].sub.3] +
[[alpha].sub.4] = [360.sup.0] (2)
where:
--[[alpha].sub.1] = [306.sup.0]--the rotation angle of the main
shaft, corresponding to energy potential stored by the torsion bar;
--[[alpha].sub.2] = [45.sup.0]--the rotation angle of the main
shaft, corresponding to projectile lifting on carrier;
--[[alpha].sub.3] = [1.sup.0]--the rotation angle of the main
shaft, corresponding to the launching mechanism;
--[[alpha].sub.4] = [8.sup.0]--the rotation angle of the main
shaft, corresponding to projectile launching.
In this experimental study of the weaving machine vibrations, the
amplitudines of accelerations were analyzed as function of time. This
study was realized taking into account the movement of each mechanism
for only one rotation of the main shaft.
The functioning of each mechanism and the way of vibration
transmission to the whole machine were analysed. The following aspects
were observed:
* slay generates vibrations on vertical and longitudinal
directions;
* shedding mechanism generates vibrations on vertical and
longitudinal directions;
* warp regulator generates vibrations on longitudinal and vertical
directions;
* launching mechanism generates vibrations on vertical an
transversal directions.
Since weaving machine represents an assembly of many mechanisms,
the resulting vibrations are transmitted to the frame and to the other
machine elements.
There were setted up the following directions:
* longitudinal direction corresponds to the sense of the warp
threads;
* transversal direction coincides with the shaft machine direction;
* vertical direction is perpendicular to the floor.
3. RESULTS AND DISCUSSIONS
The experimental measurements were performed in an educational
laboratory. The weaving machine under study was a Sulzer model
(Luca&Vigaru, 2009).
The elaborated study was focused on the vibration evaluation based
on measurements on an old weaving machine.
The transducer positioning on the vertical direction is presented
in figure 1.
In the case of vertical vibration the recorded signal is presented
in figure 2. The maximum value of acceleration a= 0.9m/[s.sup.2] was
obtained for t = 0.350 s.
By applying the Fourier Transform, it results the vibration
amplitudes as a function of frequencies (figure 3).
[FIGURE 1 OMITTED]
[FIGURE 2 OMITTED]
[FIGURE 3 OMITTED]
[FIGURE 4 OMITTED]
The spectrum representation of acceleration amplitudes as function
of frequency (figure 3), do not offer information about the time period
corresponding to each maximum amplitude.
In order to obtain the maximum value of acceleration amplitude and
the corresponding moment, shown in figure 4, the amplitude was
represented as function of time. The maximum value was correlated with
the functioning of mechanism during the (0 - 0.1) s interval.
Analyzing the mentioned graphics it is observed that in (0.01-0.02)
s interval appears a peak value for acceleration a = 75 m/[s.sup.2]. The
mechanisms that transmit vertical vibration are: the shedding mechanism
in t = (0-0.12) s and the slay mechanism moving in extreme frontal
position in t=(0-0.046) s.
4. CONCLUSION
The experimental study allowed to evaluate the vibration amplitudes
and each mechanism influence on the general vibrations acting on the
Sulzer weaving machine, but do not offer information for identifying the
vibration source of the mechanism.
The launching mechanism does not transmit the vibration on vertical
direction on the launch box. The peak amplitude is mainly due to the
shedding mechanism and slay mechanism in the moment when starts the
movement toward extreme frontal position.
5. REFERENCES
Deger, Y., (2000). Structural dynamics of weaving machines:
combined use of experimental modal analysis and FE simulation as an
optimization tool. International Conference on Noise &Vibration
Engineering, 13-15 September, Leuven, Belgium
Demeulenare B., (2004). Dynamic balancing of reciprocating
machinery with application to weaving machines International Conference
on Noise & Vibration Engineering, 20-22 September, Leuven, Belgium
Luca, Gh. &Vigaru C., (2009). Weaving machines, Editura
Politehnica Timisoara, ISBN 9789736268183, Timisoara
Reicher F. & Dragoi L., (1985). Basic design of weaving
machines, Polytechnic Institut, Iasi
Stefanuta I., (1997). Weaving technology, The Editure of Lucian
Blaga University, Sibiu