Note: Descriptions are shown in the official language in which they were submitted.
CA 02260074 2005-11-09
PROCESS AND WINDING MACHINE FOR CONTINUOUS
WINDING OF A MATERIAL WEB
The invention relates to a process for continuous winding of a material web in
particular a paper or cardboard web and a winding machine for continuous
winding of
a material web, in particular a paper or cardboard web.
Processes and winding machines of the type mentioned here are known (EP 0
561 128 Al). They are employed, for example, at the end of a machine for
manufacturing a material web and are used for continuous winding of the
material
web onto a reel. The known winding machine includes a horizontally movable
pressing drum, also called a Pope drum, over part of whose circumference the
material
web is guided. The material web is wound into a winding roll on a reel,
wherein
during the entire winding operation, the winding roll forms a winding gap with
the
pressing drum. In order to prepare for a change of the reel, an empty reel is
pressed
against the circumference of the pressing drum, by means of which another, new
winding gap is formed. During this winding phase, the material web is guided
through
both the nip between the new reel and the pressing drum and the closed nip
between
the almost-finished winding roll and the pressing drum. Then, in the region
disposed
between the full winding roll and the new reel, the material web is cut
directly on the
pressing drum and the new web beginning is wound onto the new reel. It has
turned
out to be disadvantageous that the transfer and winding of the new web
beginning
onto the empty reel is very difficult. In many instances, a number of attempts
are
necessary for this, which in turn leads to a relatively high percentage of
waste.
The present invention, therefore, is directed toward the creation of a process
and a winding machine 5 that do not exhibit these disadvantages.
In accordance with one aspect of the present invention, there is provided
process for continuous winding of a material web, in particular a paper or
cardboard
web, to form a winding roll on a reel, comprising a plurality of steps.
The process takes place in the following steps: The material web is guided by
way of a movable pressing drum, which forms a winding gap with the winding
roll,
which is rotatably secured in a secondary transport device, wherein the line
force in
the
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winding gap is controlled/regulated during this winding phase by means of a
shifting of the
pressing drum. In order to prepare for a reel change when a desired winding
roll diameter is
reached, the winding roll is moved away from the pressing drum by means rrf
the secondary
transport device so that the material web runs freely from the pressing drum
to the winding
roll. A new reel rotating at web speed is moved by means of a primary
transport device into
the free draw and is brought into a reel-changing position in which the new
reel forms a new
winding gap with the pressing drum. After this, the material web is cut
crosswise over its
width and with its new web beginning, is wound onto the new reel. During this
winding
phase, the control/regulation of the line force in the winding gap between the
pressing drum
and the new reel is in turn carried out by means of a shifting of the pressing
drum. Finally,
the new reel with the new winding roll is taken over by the secondary
transport device,
wherein the control/regulation of the line force occurs by means of a shifting
of the pressing
drum, even when the new reel is guided by the secondary transport device.
Since the empty
reel is partly wrapped by the material web before the transfer and winding-on
of the new web
beginning, i.e. the material web is guided over a circumference region of the
new reel while
the material web is still being wound onto the nearly finished winding roll, a
reliable transfer
of the web and start of winding of the winding roll onto the new reel can be
assured. The
process is distinguished by means of a high degree of change-over reliability.
It is furthermore advantageous that the line force in the winding gap during
the entire
winding process is adjusted exclusively by means of a relative movement of the
pressing
drum in relation to the winding roll. The pressing drum can be rapidly shifted
due its
relatively light weight in comparison to the weight of the growing winding
roll.
Consequently, jumps and fluctuations in the sine force can be compensated for
very rapidly.
As a result of this, an exact, uniform line force in the winding gap can be
adjusted/regulated
during the entire, i.e. a complete, winding process so that on the whole, a
favorable winding
quality can be achieved. Furthermore, it is particularly advantageous that a
direction change
of the shifting movement of the pressing drum can be carried out very rapidly
due to the
relatively low weight of the pressing drum in relation to the winding roll.
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In a particularly preferred embodiment of the process, the provision is made
that with
the removal of the winding roll from the pressing drum, this pressing drum
follows the
winding roll until reaching a stop and that the new reel is subsequently
brought into the reel-
changing position, wherein before the reel change, the new reel
forces the pressing drum back from the stop. By means of this, it can be
assured with a
relatively low controUregulation cost, that the line force during a complete
winding process,
i.e. from the start of winding to the final winding of the winding roll, can
be exactly adjusted
or maintained at a desired value by means of a shifting of the pressing drum.
Finally, an embodiment of the process is also preferable, which is
distinguished by
virtue of the fact that the empty reel is brought into a position disposed
above
a pressing drum. After this, a winding gap is formed between the pressing drum
and the
empty reel by means of a relative movement between the pressing drum and the
reel. The
disposition of the empty reel in relation to the pressing drum is chosen so
that the pressing
plane, which is defined by means of the winding gap and by means of the
longitudinal axes
of the empty reel and-the pressing drum, is inclined in relation to an
imaginary horizontal by
an angle a, which lies in a range of 5 ° s a s 40°, preferably
10° s a s 35 °, in particular 15 °
s a s 30 °. In this position of the empty reel, the material web is cut
and its free end is wound
onto the empty reel. Since the winding gap during the winding-on lies in the
inclined
pressing plane, the deflection resulting from the pressing force and the
component of the
deflection resulting from the tare weight of the reel, which component lies in
the pressing
plane, cancel each other out, preferably completely, but at least
significantly. As a result, a
line force in the winding gap can be adjusted that is uniform viewed in terms
of the web
width, which in tum leads to an improvement of the-winding quality.
Furthermore, an exemplary embodiment of the process is preferable, which is
distinguished by virtue of the fact that after the secondary transport device
takes over a reel,
a compensation for the diameter increase of the winding roll occurs by means
of a preferably
horizontal or at least nearly horizontal shifting of the secondary transport
device. The
adjustment of the line force and consequently the shifting of the pressing
drum occurs
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independently of the compensation movement of the growing winding roll. The
load
in the winding gap can therefore be modulated or adjusted very precisely. The
fluctuations or jumps in the line force that previously occurred on an
occasional basis
in the winding gap are avoided at least to a large extent. By means of this, a
definite,
uniform winding hardness can be adjusted; in particular, an exact core winding
can be
assured.
In accordance with another aspect of the present invention, there is provided
winding machine for continuous winding of a material web, in particular a
paper or
cardboard web, onto a winding roll having a movable pressing drum, which forms
a
winding gap with the winding roll, having at least one primary transport
device by
means of which the roll can be moved along a first guide track, and having at
least
one secondary transport device which guides the roll along a second guide
track. This
machine is distinguished in that in order to prepare for a reel change, the
new reel is
shifted by means of the primary transport device into a reel-changing position
in
which a new winding gap is formed between the new reel and the pressing drum,
and
that in the reel-changing position, the material web is guided over a
circumference
region of the new reel. Since the material web that is wound on the almost
finished
winding roll is already wound part of the way around the new reel before the
reel
change, a high degree of change-over reliability can be assured.
An exemplary embodiment of the winding machine is particularly preferred in
which the reel-changing position is provided above the position in which the
secondary transport device takes over the new reel. In an advantageous
embodiment,
during the winding-on process, the new winding gap is disposed in a pressing
plane
that is defined by the longitudinal axes of the empty reel and the pressing
drum and is
inclined in relation to an imaginary horizontal by an angle a, which lies in a
range of
5° _< a <_ 40°, preferably 10° <_ a _< 35°, in
particular 15° <_ a _< 30°. The component of
the deflection resulting from the tare weight of the reel, which component
lies in the
pressing plane, and the deflection resulting from the pressing force cancel
each other
out, at least approximately. As a result, during the start of winding, a
uniform line
force in the winding gap can be assured over the entire web width so that a
definite
building up, first of the winding core and then of the remaining winding roll,
is
possible. The improvement of the winding quality in the core thus permits an
exact
winding of the entire winding roll.
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In an advantageous embodiment of the winding machine, the provision is made
that
the diameter increase can be compensated for by a shifting of the secondary
transport device
and the line force in the winding gap can be adjusted, preferably regulated~y
means of a
shifting of the pressing drum while the winding roll is guided by the
secondary transport
device. The compensation for the growing winding roll diameter and the
adjustment of the
line force are therefore provided by two separate devices that can be actuated
or function
separately from each other, the secondary transport device and the pressing
drum. Due to the
weight of the pressing drum, which is relatively light in comparison to the
weight of the
growing winding roll, the pressing drum can be rapidly shifted and
consequently, jumps and
fluctuations in the line force can be compensated for very rapidly. It is
particularly
advantageous that a direction change of the shifting movement can be carried
out very
rapidly by means of the pressing device due to the relatively low weight of
the pressing
drum. A preferably uniformly favorable winding result can be achieved by means
of the
independent shifting movements of the pressing drum and the secondary
transport device.
An exemplary embodiment of the winding machine is also preferable in which the
at least one pressing device, with the aid of which the pressing drum can be
shifted, is
embodied as a preferably hydraulic piston and cylinder unit. In a first
embodiment, the
maximal stroke of the piston is less than half the material layer thickness of
the finished
winding roll. Despite the relatively small stroke, i.e. the distance that the
pressing drum can
be shifted in one direction, the pressing system is not changed during the
winding process.
The movable pressing drum remains in practically constant contact with the
winding roll
except for a few seconds during the reel change. The winding machine is
distinguished by
means of a simple and reasonably priced design. In another, second embodiment,
the
provision is made that the maximal stroke of the piston is at least greater
than or equal to the
layer thickness of a finished winding roll. By means of this, it is possible
to replace the
movable secondary transport device with a secondary support which is disposed
in stationary
fashion and in which the reel is rotatably secured. With a stationary support,
an optimal
rigidity of the reel mount can be assured so that vibrations that possibly
occur inside the
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winding machine have practically no effect on the line force/line force
progression. A
continuous reel tracking is therefore not necessary so that the machine design
can be
simplified.
Finally, another exemplary embodiment of the winding machine is preferable
in which the primary and secondary transport devices are each associated with
only
one individual drive, preferably a central drive, with the aid of which a
torque can be
exerted on the reel. The drive associated with the primary transport device is
preferably also used to accelerate an empty reel to the travel speed of the
material
web.
The invention will be explained in more detail below in conjunction with the
drawings:
Figs. 1 to 4 each show a schematic diagram of an exemplary embodiment of the
winding machine according to the invention, in different winding phases;
Fig. 5 shows a schematic diagram of the winding machine according to Figs. 1
to 4,
with an embodiment of a control for the line force in the winding gap;
Fig. 6 shows a schematic diagram of another exemplary embodiment of the
winding
machine, with a regulating device for adjusting the reel-changing position;
Fig. 7 shows a schematic diagram of a reel shown in Fig. 3, in a reel-changing
position;
Figs. 8a to 8e each show a very schematically depicted schematic
representation of
the winding machine according to Figs. 1 to 5, in different winding phases;
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Figs. 9 to 11 each show a detailed schematic representation of a third
exemplary
embodiment of the winding machine;
Figs. 12 to 13 each show a schematic representation of other exemplary
embodiments of
the winding machine and
Figs. 14a to 14e each show a very schematic representation of a sixth
exemplary
embodiment of the winding machine.
The winding machine described below can be generally employed for the winding
of a material web. The winding machine can be disposed at the end of a machine
for
manufacturing or upgrading a material web, for example a paper web, in order
to wind the
finished material web into a winding roll. The winding machine can, however,
also be used
to re-roll finished winding rolls. Purely by way of example, it is assumed
that, in this
instance, it concerns a winding machine for the winding of a continuous paper
web.
Figs. 1 to 4 each show a schematic representation of a first exemplary
embodiment
of a winding machine 1, which serves the winding of a paper web, which will be
generally
referred to below as the material web 3, onto a reel, winding core, or the
like. A sequence of
operational steps of the winding machine 1 emerges from the Figs. 1 to 4. The
winding
machine 1 in this exemplary embodiment includes two secondary transport
devices 5 and 7,
which each include a secondary block 11 that can travel on second rails 9. The
rails 9 are
disposed parallel to an imaginary horizontal and are fastened to a machine
frame 13. The
secondary transport devices 5, 7 are used to rotatably secure and guide a reel
along a second,
horizontally extending guide track 14, which lies in an imaginary plane E--
depicted with
dashed lines. This plane spans an area that is disposed perpendicular on the
plane of the
drawing of Fig. 1. Furthermore, guide rails 15 are attached to the machine
frame 13, which
are disposed parallel to an imaginary horizontal. A reel exhibiting bearing
pins can be stored
on the guide rails 15 and is carried by them, i.e. the weight of the reel and
the weight of the
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winding roll wound onto the reel are supported by the guide rails 15. In a
particularly
preferable exemplary embodiment of the winding machine 1, not shown in Figs. 1
to 4, only
a single secondary transport device is provided, which simplifies the
desigrr'ttf the winding
machine.
The winding machine 1 furthermore comprises a pressing drum 19, which can be
driven by means of a central drive 17 indicated with a symbol and is rotatably
secured on a
guide block 21, which can be moved on first rails 22. In this exemplary
embodiment, the rails
9 and 22 are disposed parallel to one another. The distance between the guide
rails 15 and
the longitudinal axis 23 of the pressing drum 19, which lies in the plane E,
is therefore
constant. The guide block 21 is associated with a pressing device 25 that is
embodied here
as a hydraulic piston and cylinder unit, which is fastened to the machine
frame 13. The
pressing device 25 exhibits a piston 29 that is guided in a cylinder 27 and is
connected to a
piston rod 31 that engages the guide block 21. When the piston rod 31 travels
outward, the
guide block 21 and consequently, the pressing drum 19, which is also called a
Pope drum,
are shifted toward the right in Fig. 1, in the direction of an arrow 33. When
the piston rod 31
travels into the cylinder 27, a shifting of the pressing drum 19 toward the
left in Fig. 1
occurs. The maximal stroke of the piston 29, i.e. how far the piston rod 31
can travel out of
or into the cylinder 27, is preferably less than half the material layer
thickness S of a finished
winding roll. In another exemplary embodiment, the provision is made that the
stroke of the
piston 29 is greater than or equal to the material layer thickness S of a
finished winding roll.
In another advantageous embodiment, the pressing device includes two hydraulic
piston and
cylinder units in order to shift the pressing drum and to generate a desired
line force.
As is apparent from Fig. l, the pressing drum 19 forms a winding gap-with a
winding
roll 37 that has been wound onto a reel 35, i.e. the pressing drum 19 forms a
nip together
with the winding roll 37. The pressing drum 19 thus touches the circumference
of the
winding roll over its entire length. The reel 35, which is rotatably secured
and guided by the
secondary transport device 5 in this winding phase, is engaged by a secondary
drive 39,
which is indicated with a symbol and is embodied in this instance by a central
drive. With
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the aid of the secondary drive 39, a torque can be exerted on the reel that is
resting on the
guide rails 15 and is secured by the secondary transport device 5.
The guide rails 15 are attached to the machine frame 13 in suel3 a way that
the
longitudinal axis 41 of the reel 35, which rests with its bearing pins on the
guide rails 15, lies
in the same plane E as the longitudinal axis 23 of the pressing drum 19. In
another
advantageous exemplary embodiment of the winding machine 1, the pressing drum
19 and
the reel resting on the guide rails 15 are disposed at different heights
(Figs. 9, 12, 13), which
nevertheless has no influence on the advantageous operation of the winding
machine 1.
The material web 3 is guided by way of the pressing drum 19 and is wound onto
the
winding roll 37. The line force in the winding gap is controlled by means of
the pressing
device 25 associated with the pressing drum 19, i.e. the pressing drum 19 is
pressed with a
definite force against the circumference of the winding roll 37, by means of
which a desired
winding hardness of the winding roll or a uniform winding hardness progression
can be
adjusted. In another exemplary embodiment, the provision is made that the line
force in the
winding gap is regulated, i.e. the pressing device 25 is part of a regulating
circuit that
automatically maintains or adjusts the line force to a desired value.
Fluctuations in the line
force can be reliably compensated for or avoided by means of the shifting of
the pressing
drum 19 by the pressing device 25 so that a desired winding hardness can be
continuously
produced. By means of this, the line force can be maintained at a--for example
constant--
value even if there is a malfunction in the winding process. A malfunction
can, for example,
be a not-entirely-precise movement of the secondary transport device so that
the position of
the winding gap formed by the pressing drum 19 and the winding roll 37 shifts
slightly, or
can be a balance error in the pressing drum and/or the winding roll.
The growing diameter of the winding roll 37 is compensated for by means of a
shifting of the winding ro~137 to the right in the direction of the arrow 33.
To this end, the
secondary transport device 5 is moved toward the right, which brings about a
slaving of the
reel 35 and consequently of the winding roll 37. For the moving of the
secondary transport
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devices 5 and 7, a stroke device 43 is provided here, which includes a
threaded spindle 47
driven by a motor 45.
An empty reel 49, which is secured by a primary transport devicernot shown, is
disposed in a ready position above the pressing drum 19 (Figs. l and 2). For
the preparation
of a reel change, the reel 49 is shifted with the aid of the primary transport
device from the
ready position into a reel-changing position in which this reel is secured in
a stationary and
rotatable fashion by the primary transport device, whose design is described
in more detail
below (Fig. 3). While the empty reel 49 is disposed in the reel-changing
position, a winding
gap is formed by means of a relative movement between the pressing drum 19 and
the empty
reel 49, i.e. the pressing drum and the empty reel touch each other on their
circumference
over their entire length. After the cutting of the material web by means of an
intrinsically
known cutting device, not shown, (symbolically depicted in Figs. 8c and 14c by
means of an
arrow T), the web is wound with its new web beginning onto the empty reel 49,
which is
disposed in the reel-changing position. By means of the primary transport
device, the reel 49
1 S can be moved along a first guide track from the ready position into the
reel-changing position
and from this into a finished winding position (Fig. 4). In connection with
the present
invention, the "finished winding position" is understood to mean a position of
the reel 49 in
which it rests with its bearing pins on the guide rails 15. The first guide
track can have a
curved, preferably arc-shaped and/or linear course. The primary transport
device is associated
with a central drive, not shown, which is also called the primary drive and is
for the reel or
winding roll held by this transport device, by means of which the reel can be
acted on with
a driving and/or a braking moment.
In Fig. 3, the empty reel 49 is disposed in the reel-changing position in
which after
a cutting procedure, the new web beginning is wound onto the reel 49. The reel
49 forms a
winding gap with the pressing drum 19 and this gap lies in a pressing plane P,
which is
inclined in relation to an imaginary horizontal by an angle a, which lies in a
range of 5 ° <_
a <_ 40°, preferably 10° <_ a s 35°, in particular
IS° <_ a _< 30°. In this instance, purely by
way of example, the angle a amounts to approximately 32°. Angles a that
lie in the range
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from 15° to 30° have turned out to be particularly advantageous.
Since the winding
gap lies in the inclined pressing plane P, the deflection resulting from the
pressing
force and the component of the deflection resulting from the tare weight,
which
component lies in the pressing plane P, cancel each other out, so that a
uniform line
force can be adjusted in the winding gap over the width of the web. A
favorable
winding quality thus can be achieved.
Beneath the pressing drum 19, a pressing element is provided, which in this
exemplary embodiment is constituted by a press roll 51 that extends over the
entire
width of the winding roll 37 and is also called a squeeze roll. By means of a
guide
device that is not shown, the press roll 51 can he pressed against the
circumference of
the winding roll that forms a winding gap with the pressing drum 19. The press
roll S 1
serves to prevent air from slipping in between the winding layers of the
winding roll,
for example when the material web 3 travels in a free draw from the pressing
drum to
the winding roll. The press roll 51 can be acted on with a torque and
accelerated to
web speed by a drive, for example a central drive. In another exemplary
embodiment
not shown in the Figs., the pressing element is constituted by a stationary
pressing
brush, which is affixed to at least one bar extending over the entire width of
the
winding roll. By means of a shifting of the bar, the pressing brush is placed
against
the winding roll, by means of which the air that has slipped between the
winding
layers is virtually stroked out. In comparison to the press roll, the pressing
brush has a
simplified and therefore more reasonably priced design since it does not
rotate and
consequently, an additional drive is not required. This is also true for a so-
called air
brush, which is an air blower nozzle that extends over the width of the web
and acts
on the winding roll in a contact-free manner after the fashion of an air
squeezing
device.
In the following, the function of the winding machine 1 will be explained in
more detail in conjunction with a winding process: The material web 3 is
guided by
way of the pressing drum 19 and wound onto the winding roll 37 that is guided
by the
secondary transport device 5 (Fig. 1). Before the winding roll 37 reaches its
final
diameter, the press roll 51 is pressed against the circumference of the
winding roll 37
(Fig. 2). The material web 3 is consequently guided both through the winding
gap
between the pressing drum 19 and the
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winding roll 37, and through the winding gap between the press roll 51 and the
winding roll
37. For the transfer of the continuously supplied material web 3 onto the
empty reel 49, the
winding roll 37 is moved by means of the secondary transport device 5 along-
the guide rails
15 in the direction of the arrow 33, by means of which the distance increases
between the
longitudinal axis 23 of the pressing drum 19 and the longitudinal axis 41 of
the winding roll
37, which in this instance both lie in the plane E, and an intermediary space
53 is formed
between the pressing drum 19 and the winding roll 37 (Fig. 3). In the region
of the
intermediary space 53, the material web 3 is transferred in a free draw from
the pressing
drum 19 onto the winding roll 37. While the secondary transport device 5 is
moved along
with the winding roll 37, the press roll 51 is guided after the winding roll
37 in such a way
that the line force in the winding gap between the press roll S 1 and the
winding roll 37
maintains a desired value until the pressing drum 19 comes into contact with
at least one stop
54. In this exemplary embodiment, the stop 54 is produced by virtue of the
fact that the
piston 29 of the pressing device 25 strikes against the inner wall of the
cylinder 27, i.e.
reaches its rightward end position, in the depiction according to Fig. 3, in
which the piston
29 rests against the inner wall of the cylinder 27. The pressing drum 19 thus
has a fixed
position.
Then from above, the empty reel 49, which is disposed in the ready position
and has
been accelerated to the travel speed of the material web 3, is shifted
downward along the first
guide track and brought into the reel-changing position in the intermediary
space 53 between
the pressing drum 19 and the winding roll 37 (Fig. 3). The pressing drum 19
that has been
moved against the stop 54 is disposed in the first guide track so that when
the empty reel 49
is moved into the reel-changing position, this reel is brought into contact
with the pressing
drum 19. As a result, the reel 49 forces the pressing drum 19 back from the
stop 54 counter
to the direction of the arrow 33 (not shown), which finishes the formation of
the nip/winding
gap. Then, by means of a cutting device, not shown, which is disposed, for
example, in the
region of the intermediary space 53, the material web is cut crosswise over
the width and the
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new web beginning is wound onto the reel 49. The reel 49 remains in the reel-
changing
position for a variable duration of time, for example until the winding of the
core of the new
winding roll has been finished. Then, the reel 49 that is rotatably secured
h~the primary
transport device is guided along the first guide track from the reel-changing
position into the
finished winding position and is lowered directly onto the guide rails 15
(Fig. 4). The reel
49 is taken over, i.e. is guided and held, by the second secondary transport
device 7, which
is disposed in the take-over position. In the winding phase shown in Fig. 4, a
few layers of
the material web 3 that are not shown are already wound onto the reel 49 that
is still being
driven by the primary drive or by a central drive associated with the
secondary transport
device 7.
After the finished winding roll 33 has been braked, for example with the aid
of the
secondary drive 39 and/or the press roll, it can be removed from the secondary
transport
device 5, while the press roll 51 is shifted back into its position shown in
Fig. 1. As.long as
the secondary drive 39 is associated with both secondary transport devices 5
and 7, after the
braking of the full winding roll, now the secondary drive is effectively
connected to the reel
49, and the primary drive and the primary transport device are released from
the reel 49. The
growing diameter of the winding roll that is wound onto the reel 49 and is not
shown in Fig.
4 is compensated for by a shifting of the secondary transport device 7 along
the guide rails
15 in the direction of the arrow 33. The line force in the winding gap between
the pressing
drum 19 and the winding roll wound onto the reel 49 is maintained at a desired
value during
the entire winding process by means of a shifting of the pressing drum '19 by
the pressing
device 25.
A web guide roll 55 is represented in Fig. 1, which is disposed below the
pressing
drum 19 and is rotatably attached to the machine frame 13. By means of a unit
57, which is
disposed before the web guide roll 55 in terms of the travel direction of the
material web and
which in this instance, purely by way of example, is a pressing device 59, the
material web
3 is guided to the web guide roll 55, deflected by this roll, and conveyed
further to the
pressing drum 19. The material web 3 is wound around the web guide roll SS,
preferably in
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a circumference range from 155 ° to 205 °. The winding angle is
at least 150°, even when the
pressing drum 19 is being shifted during the winding process. It is hereby
assured that the
line force in the winding gap is not influenced by a change of the web
longi~dinal stress in
the region between the unit 57 and the pressing drum 19. The pressing device
59 comprises
two press rolls that form a nip, at least one of which is driven, as shown in
Fig. 1.
In order to uncouple the winding process to a large extent from the
fluctuations of the
production process of the material web, the material web guidance is
preferably embodied
so that the material web 3 is wound around the pressing drum 19 by
approximately 180°.
Since the material web is guided over a relatively large circumference region
of the pressing
drum, fluctuations in the draw have practically no influence on the pressure
of the pressing
drum against the winding roll and consequently have practically no influence
on the line
force. Furthermore, small movements of the pressing drum are compensated for
so that they
cause no draw fluctuations; the pressing drum is therefore reactionless. As a
result of the
relatively large winding angle, a further assurance can be made that a
slightly inclined
position of the pressing drum does not lead to an undesirable wrinkle
formation. It is
furthermore possible to connect only stationary guide rolls and spreader rolls
before the
pressing drum, which do not have to be guided after the movable pressing drum,
by means
of which the design of the winding machine can be simplified.
The above-mentioned process can be readily inferred from the description of
Figs.
1 to 4. This process provides for the fact that the material web is guided by
way of a
preferably horizontally movable pressing drum, which forms a winding gap with
the winding
roll that is rotatably secured in a secondary transport device, wherein the
line force in the
winding gap is controlled or regulated by means of a shifting of the pressing
drum. In order
to prepare for a reel change when a desired winding roll diameter is reached,
the winding roll
is moved away from the pressing drum by means of the secondary transport
device so that
the material web travels freely from the pressing drum to the winding roll; a
free draw is thus
produced. A primary transport device brings a new reel, i.e. an empty one,
which is rotating
at web speed, into a reel-changing position in which the new reel forms a
winding gap with
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the pressing drum. Then, the material web is cut crosswise over its width and
the new web
beginning is wound onto the new reel. In this winding phase, the
control/regulation of the
line force in the winding gap between the pressing drum and the new reel
or.the winding roll
wound onto it is in tum carried out by means of a shifting of the pressing
drum. Finally, the
secondary transport device takes over the new reel with the new winding roll,
wherein the
control/regulation of the line force continues to be carried out by means of a
shifting of the
pressing drum.
The formation of a winding gap between the pressing drum 19 and the empty reel
can
be realized by virtue of the fact that the empty reel is moved along the first
guide track and
strikes against the pressing drum disposed in the first guide track. In
another embodiment,
the provision is made that the winding gap is formed by means of a shifting of
the pressing
drum 19 with the aid of the pressing device 25 in the direction of the reel
disposed in the
reel-changing position. Naturally, both the reel 49 and the pressing drum 19
can be moved
toward each other in order to form a winding gap. Independent of how the
winding gap is
formed, abrupt fluctuations in the line force of the kind that occur, for
example, at the
moment the reel is transferred from the primary transport device to the
secondary transport
device, can be compensated for or prevented with the aid of the movable
pressing drum. The
line force can thus be continuously maintained exactly at a desired value.
As is shown in Figs. 3 and 4, the pressing drum 19 can be embodied as a
deflection
adjusting roll 140 whose roll jacket 141 is supported on a stationary yoke 143
by means of
a series of support elements 142, which produces a bulging outer contour of
the pressing
drum 19. Only one of the support elements 142 that act in the direction toward
the winding
gap can be seen in the view according to Figs. 3 and 4. The design of the
deflection adjusting
roll 140 is intrinsically known (DE-OS 25 55 677) so that this is not
described in more detail.
The support elements 142 can preferably be controlled individually, i.e.
independently of one
another, whereby a desired bulging of the roll jacket 41 can be adjusted. The
yoke 143 can
be rotated around a fixed axis, in this instance, the longitudinal axis 23.
The support elements
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142 that cooperate with the yoke 143 are pivoted in such a way during a
rotation of the yoke
143 that the direction in which they act follows the wandering motion of the
winding gap.
Through the adjustment of a desired bulging of the outer contour.ofthe
pressing
drum, the material web guided by way of it can, viewed crosswise to the travel
direction of
the web, be definitely stretched, preferably before the material web travels
into the winding
gap. By means of this, a wrinkle formation of the winding layers wound onto
the winding roll
can be prevented and consequently, the winding result can be improved. In
terms of the
longitudinal direction of the drum, the deflection of the pressing drum can
preferably be
adjusted in sections, as described above. As a result, the desired spreading
of the material
web can be influenced, preferably adjusted, by varying the outer contour of
the pressing
drum. In an advantageous exemplary embodiment, the pressing drum 19 is part of
an active
vibration damping system, i.e. the pressing drum is oscillatory. In connection
with the current
invention, the tem "oscillatory" is understood to mean that the pressing drum
can execute
a rapid shifting motion toward the winding roll and in the opposite direction.
The pressing
device 25, i.e. the hydraulic piston and cylinder unit represented in Figs. 1
to 4, can therefore
very rapidly execute a direction change in the shifting motion of the pressing
drum 19.
Fig. 5 shows a schematic representation of the winding machine according to
Figs.
1 to 4, with an embodiment of a control. Parts that coincide with those in
Figs. 1 to 4 are
provided with the same reference numerals so that in this regard, reference
will be made to
the descriptions of Figs. 1 to 4. For the control of the winding machine 1, a
control unit 61
is provided, which controls the motor 45 of the threaded spindle as a function
of the speed
of the diameter increase of the winding roll 37. The diameter increase of the
winding roll 37
is measured by means of a measuring device 63. The position of the secondary
transport
device 5 thus changes solely, i.e. exclusively, in accordance with the
increase of the winding
roll diameter. The magnitude of the line force in the winding gap formed
between the
pressing drum 19 and the winding roll 37 is solely, i.e. exclusively,
determined by means of
a moving of the guide block 21 holding the pressing drum 19, preferably
regulated by means
of a regulating device 65. This includes a measuring device 67 for the line
force, a regulator
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69, a set point transmitter 71, and a control unit 73. The measuring device 67
is connected
by way of a measurement line 75 to the regulator 69 or feeds into this. The
set point
transmitter 71 is connected by way of a line 75' to the regulator 69 and
indicates the desired
set point to the this regulator 69. The regulator 69 is in turn connected by
way of a line 77
to the control unit 73.
In the event that the value of the line force, which is measured by the
measuring
device 67 and disposed in the winding gap formed between the pressing drum 19
and the
winding roll 37, diverges from the set point predetermined by the set point
transmitter, the
regulator 69 sends a signal to the control unit 73 by way of the line 77. This
control unit then
changes the pressure in the cylinder 27 of the pressing device 25 in such a
way that the
measured value of the line force approaches the set point. By means of this,
the line force can
be kept at a for example constant value even in the event of a malfunction in
the winding
process. A malfunction can, for example, be a not-entirely-precise movement of
the
secondary transport device 5 so that the position of the winding gap formed by
the pressing
drum 19 and the winding roll 37 guided by the secondary transport device 5
shifts slightly.
In a preferred exemplary embodiment, the provision is made that in order to
control
the line force, the pressing drum 19 can be shifted independently of the
travel speed of the
secondary transport device. Furthermore, it is possible that the stroke device
43 that
cooperates with the secondary transport device, i.e. the motor 45 that drives
the threaded
spindle 47, can be controlled in such a way that the position of the winding
gap formed
between the pressing drum 19 and the winding roll 37 is essentially constant
while the
winding roll 37 is resting on the guide rails 15. The "constant position" of
the winding gap
is understood to mean its position inside the winding machine l, i.e. the
winding roll 37 is
shifted in the direction of the arrow 33 by means of the secondary transport
device 5 with a
speed such that only the diameter increase of the winding roll 37 is
compensated for.
In another exemplary embodiment, the provision is made that the stroke device
43
associated with the secondary transport device 5, 7 can be controlled in such
a way that the
position of the winding gap formed between the pressing drum 19 and the
winding roll 37
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shifts with an increasing winding roll diameter during the winding process,
for example in
a range from 50 mm to 200 mm.
Fig. 6 shows a schematic representation of another exemplary embodiment of the
winding machine 1. Parts that coincide with those in Figs. 1 to 5 are provided
with the same
reference numerals so that in this regard, reference will be made to the
descriptions of Figs.
1 to 5. A part of an exemplary embodiment of the primary transport. device 79
is shown in
Fig. 6. This includes two primary pivoting levers 81, only one of which is
depicted in this
view. The primary pivoting levers 81 to which the new reel 49 is rotatably
secured can be
pivoted around an axle 83 that runs parallel to the longitudinal axis of the
reel 49. The
primary pivoting levers 81 are disposed in a stationary manner inside the
winding machine
1; i.e., the axle 83 has a fixed, unchangeable position in the machine frame
13, at least during
a complete winding operation. The primary pivoting levers 81 are associated
with a stroke
device 85, which is assigned, for example, to the machine frame 13, and this
stroke device
includes at least one--preferably hydraulic--piston and cylinder unit
associated with a primary
pivoting lever. The piston and cylinder unit comprises a piston 89 that is
guided in a cylinder
87 and is connected to a piston rod 91 that engages at least one of the
primary pivoting levers
81. When the piston rod 91 travels outward out of the. cylinder 87, the
primary pivoting
levers 81 are pivoted counterclockwise around the axle 83 and when the piston
rod 91 travels
inward, they are pivoted clockwise. Naturally, the stroke device 85 can also
include, for
example, two piston and cylinder units, which are each associated with a
primary pivoting
lever 81.
In this winding phase, the primary pivoting levers 81, which hold the empty
reel 49
in the reel-changing position, as shown in Fig. 6, are inclined in relation to
an imaginary
horizontal H, represented with a dashed line, by an angle w, which in this
instance amounts
to approximately 26°. The angle w can be adjusted by means of the
stroke device 85. In order
to adjust the angle w, a regulating device 93 is provided, which includes a
regulator 69', a
set point transmitter 71', and a measuring device 67' for determining the
position of the
primary drive levers 81. The set point transmitter 71' is connected to the
regulator 69' by
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way of a signal line 95 and the measuring device 67' is connected to the
regulator 69' by way
of a signal line 97. In order to change the angle w and consequently to change
the location
of the reel-changing position, a new set point is input into the set point-
tr~nsmitter 71'. A
variance comparison is executed with the aid of the regulator 69'. In the
event of a deviation,
the regulator 69' sends a signal by way of a line 77' to a hydraulic
regulating valve 99, which
then opens up the through flow between a pump 101 and a medium line 103
leading from
the regulating valve 99 to the cylinder 87. The medium supplied by the pump,
for example
a hydraulic fluid or a gas, can alternatively be introduced into one of the
partial chambers of
the cylinder 87 that are divided from each other by the piston 89. If the
medium is introduced
into the upper partial chamber in the depiction according to Fig. 6, as
indicated with an
arrow, then the piston rod 91 travels into the cylinder 87, which reduces the
angle w. If
medium flows into the lower partial chamber of the cylinder 87, the piston rod
91 travels out
of the cylinder, which increases the angle w. After the desired angle w has
been set, the
regulating valve 99 interrupts the connection between the pump 101 and the
line 103. A
check valve 105 is provided in order to prevent a return flow of the medium
from the
cylinder 87 in the direction of the regulating valve 99.
With the aid of the regulating device 93, a definite angle w can be set at any
time
during the winding operation. Moreover, it is particularly advantageous that
the location of
the reel-changing position can be predetermined before the next reel change,
wherein for
example if needed, an angle w can also be adjusted that is equal to zero (for
example
according to Fig. 14c).
Fig. 7 shows a view of the reel 49 in the winding phase shown in Fig. 3, in
which the
reel 49 is disposed in the reel-changing position and forms a winding gap with
the pressing
drum 19. The viewing direction of the reel 49 is indicated in Fig. 3 with an
arrow 107. In this
exemplary embodiment, the force with which the pressing drum 19 is pressed
against the
circumference of the reel 49 leads to a deflection of the reel 49 that is
represented with a
double arrow 109. The curvature of the outer contour of the reel 49 that is
caused by the
deflection is schematically represented with a line 111. The component of the
deflection,
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which results from the tare weight of the reel 49, located in the pressing
plane P, is
represented with a double arrow 113. The curved outer contour of the
unsupported reel is
schematically represented with a line 115. ---
As is apparent from Fig. 7, the deflections act in opposite directions,
wherein they are
at least basically equal in magnitude. The deflections therefore cancel each
other out
preferably completely, but at least significantly so that a uniform line force
in the winding
gap can be adjusted over the entire width of the material web.
Figs. 8a to 8e each show a very schematically depicted schematic
representation of
a part of the winding machine 1 described in conjunction with the preceding
Figs., in
different winding phases. The reel-changing procedure already described
briefly above will
be explained in more detail below in conjunction with Figs. 8a to 8e.
Before the reel change, an empty reel 49 is taken over by the stationary
winding
station, namely by the primary transport device 79, which in this instance
includes primary
pivoting levers 81 (Fig. 8a). To this end, the primary pivoting levers 81 are
pivoted counter-
clockwise upward into the empty reel take-over position shown in Fig. 8a. The
empty reel
49 is accelerated by means of the primary drive to a synchronous speed; i.e.,
the
circumference speed of the empty reel 49 corresponds to the travel speed of
the material web
3. The pressing element, in this instance the press roll S 1, is pressed
against the
circumference of the almost full winding roll 37. The winding roll 37, which
is secured by
the secondary transport device, not shown, and is driven by means of the
secondary drive,
is moved together with the press roll S 1 away from the pressing drum 19 in
the direction of
the arrow 33. The pressing drum 19 is guided after the winding roll 37 in
order to maintain
a desired line force in the winding gap until the pressing drum 1-9 runs up
against a stop 117,
whereby its shifting motion is stopped. The winding roll 37 travels farther in
the direction
of the arrow 33, whereby a free draw between the pressing drum and the winding
roll is
formed.
Since the pressing drum comes into contact with a stop 117 before a reel
change, the
pressing drum has a fixed, definite position before each reel change. If the
distance between
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the pressing drum and the full winding roll 37 has reached at least a minimal
value,
the new reel 49 is moved into the reel-changing position in which the reel
rests
against the circumference of the pressing drum (Fig. 8c). The forming of the
nip/winding gap occurs automatically since the pressing drum resting against
the stop
117 is disposed in the movement path of the empty reel 49 at this time. The
nip is
considered to be closed when the pressing drum has been forced by the empty
reel 49
so far back from the stop 117 in the opposite direction from the arrow 33 that
the
pressing drum exerts the desired pressing force against the empty reel 49, for
example
by means of the regulating device 65 (Fig. 5).
For clarity, in Figs. 8a to 8c, the distance x of the longitudinal axis 23 of
the
pressing drum 19 from the stationary axle 83 of the primary pivoting levers
81, which
is disposed on an imaginary vertical V, is shown immediately before the reel
change
(Fig. 8a), during the reel change (Fig. 8b), and after the reel change (Fig.
8c). In the
winding phase according to Fig. 8b, in which the pressing drum 19 has already
come
into contact with the stop 117, the distance x2 exists, which is greater than
the
distance x3, which is set after the pressing drum is forced back by means of
the reel
49, which has been shifted into the reel-changing position. It is furthermore
apparent
that before the pressing drum comes into contact with the stop 11 7, it has a
distance
xl to the axle 83, which is less than the distance x2.
After the formation of the winding gap, the material web is cut in the region
of
the free draw using one of the known methods and the new web beginning is
guided
onto the reel 49. It is particularly advantageous that the empty reel 49
disposed in the
reel-changing position is already wound around by the material web over a
small
circumference region before the cutting, which facilitates the change-over
process
considerably so that a high degree of reliability can be assured in the reel
change.
After the reel change, the reel 49 is preferably held in the reel-changing
position until
the formation of the winding core of the new winding roll 119 wound onto the
reel 49
has been finished, for example until the winding roll 119 exhibits a layer
thickness S
of 20 mm to 100 mm.
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During the core winding, i.e. when the reel 49 is rotatably secured on the
primary
pivoting levers 81, the pressing drum 19 moves away from the longitudinal axis
of the reel
49 in accordance with the diameter increase of the winding roll 119. In
termgef amount, the
shifting of the pressing drum corresponds exactly to the horizontal component
of the radius
increase. During the winding-on of the new winding roll 119, the full winding
roll 37 is
braked and removed from the variable winding station, i.e. the secondary
transport device.
In a preferred exemplary embodiment in, which only one secondary transport
device is
provided, the secondary transport device is shifted to the left in the
direction of the pressing
drum in order to take over reel 49 stored on the guide rails 1 S. In the
exemplary embodiment
of the winding machine, in which two secondary transport device are provided,
they are used
alternatingly for the guidance of a new winding roll. The two secondary
transport devices
therefore only respectively guide every other winding roll. While the reel
with the new
winding roll wound on it is being guided by the secondary transport device,
the radius
increase of the winding roll is compensated for by means of a corresponding
shifting of the
reel with the aid of the secondary transport device. In terms of amount, the
shifting of the reel
in the horizontal direction corresponds exactly to the radius increase.
In another embodiment of the process that can be carried out using the winding
machine described in conjunction with Figs. 8a to 8e, the provision is made
that the winding
roll 37 guided by the secondary transport device is continuously moved without
an
intermediate stop from the position shown in Fig. 8a into the position shown
in Fig. 8d. At
the same time, the primary pivoting levers 81 and the new reel 49 move from
the position
shown in Fig. 8b to the position shown in Fig. 8e, preferably also without an
intermediate
stop. The reel change takes place when the new reel 49 being moved by means of
the primary
pivoting levers passes through the position shown in Fig. 8c. The speed of the
movements
of the winding roll 37, which is guided by the secondary transport device, and
the reel 49,
which can be moved with the aid of the primary pivoting levers, can be
constant or can
change at preferably at least one arbitrary point. The movement course of the
primary
pivoting levers 81 securing the new reel 49 can be simply controlled by means
of a time-
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dependent change of the set point for the angle w, which set point is supplied
by the set point
transmitter 71' (Fig. 6).
Figs. 9 to 11 each show a side view of a part of another exemplary embodiment
of
the winding machine l, in different winding phases. The design of the winding
machine 1
corresponds essentially to the winding machine described in conjunction with
Figs. 1 to 8.
The differences will be addressed in more detail below. Parts that are the
same are provided
with the same reference numerals so that in this regard, reference will be
made to the
descriptions of the preceding Figs.
First, the function of the winding machine 1 should be explained in more
detail below
in conjunction with a winding operation: The material web 3 is guided by way
of the pressing
drum 19 and is wound onto the winding roll 37, which is guided by the
secondary transport
device 5 and is driven by the secondary drive 39 (Fig. 9). Before the winding
roll 37 reaches
its final/desired diameter above the pressing drum 19, the empty reel 49 is
rotatably attached
to the primary pivoting levers 81, i.e. the movement of the empty reel 49 is
limited to a
rotation around its longitudinal axis, and is moved into the reel-changing
position.
It is apparent from Fig. 9 that the reel 49 disposed in the reel-changing
position is
spaced apart from the pressing drum 19 in such a way that no winding gap is
formed yet. In
the reel-changing position, the center point of the empty reel 49 is disposed
on an imaginary
second straight line G2, which is represented with dashed lines and is
disposed essentially
parallel to an imaginary first straight line G1 and is disposed on a higher
level in relation to
it. As is apparent from Fig. 9, the center point of the pressing drum 19 is
disposed on the
straight line G1 extending parallel to the guide rails 15. In a reel change,
before the transfer
of the material web 3, the empty reel 49 is accelerated by the primary drive
121 associated
with the primary pivoting levers 81 and is brought to the travel speed of the
material web 3.
In order to transfer the continuous material web 3 onto the empty reel 49, the
travel speed of
the secondary transport device S guiding the winding roll 37 is increased by
means of a
corresponding control of the motor 45 driving the threaded spindle 47. The
pressing drum
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19 remains in constant contact with the winding roll 37, i.e. when the winding
roll 37 is
shifted along the linear second guide track 14, the pressing drum is guided
after it so that the
line force in the winding gap is maintained at a desired value. ---
As is apparent from Fig. 9, the distance between the straight lines G1 and G2
is less
than the sum of the radii of the pressing drum 19 and the reel 49. As a
result, in a shifting
toward the right in Fig. 9, the pressing drum 19 comes into contact with the
reel 49 that is
disposed in the reel-changing position. This corresponds to the winding phase
shown in Fig.
10. At the moment in which a winding gap is formed beriveen the pressing drum
19 and the
empty reel 49, or at least shortly after this, the reel change is triggered.
In the reel change, the
material web 3 is cut by means of a cutting device not shown in Figs. 9 to 11,
and the new
web beginning is wound onto the reel 49. At the moment of the reel change,
i.e. just before
the cutting and transfer of the material web 3 onto the empty reel, an
intermediary space is
already formed between winding roll 37 and the pressing drum 19.
It must be stressed that the pressing drum does not assume any fixed position
before
1 S a reel change, i.e. does not come into contact with a stop, as in the
exemplary embodiment
described in conjunction with Figs. 1 to 8, but comes directly into contact
with the empty reel
49, which is held in a fixed position (reel-changing position) by the primary
pivoting levers
81.
As shown in Fig. 10, the piston 27 of the pressing drum 25 is spaced apart
from the
inner wall of the cylinder 29 at this moment; the piston 27 is therefore not
disposed in an
end/stop position.
After the new web beginning is wound onto the reel 49, this reel is
transported along
the first guide back 122, which is arc-shaped here, into the finished winding
position by a
pivoting of the primary pivoting levers 81 clockwise around the axle 83.
During the pivoting
procedure, the reel 49 is rotatably secured and supported by the primary
pivoting levers 81.
The reel 49 is continuously driven by the primary drive 121, i.e. is likewise
moved along the
first guide track 122.
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In Fig. 11, the new reel 49 is shown in its finished winding position, i.e. it
rests with
its bearing pins on the guide rails 1 S which support the weight of the reel
49 and the winding
roll that is wound on it, not shown, which only has a few winding layers.
Daring the transfer
of the reel 49 from the reel-changing position (Figs. 9 and 10) into the
finished winding
position (Fig. 11), the pressing drum 19 is moved along the straight line G1
by means of the
pressing device 25 so that the line force in the winding gap is maintained at
a desired value
during the entire transfer.
In Fig. 11, the winding roll 37 is disposed in a removal position in which the
winding
roll can be lifted from the guide rails 1 S by means of known devices and
removed from the
winding machine 1. In the exemplary embodiment of the winding machine 1 shown
in Figs.
9 to 11, only a single secondary transport device and only one secondary drive
39 are
provided. In Fig. 11, they are already shifted toward the left in the
direction of the pressing
drum 19 in order for the primary transport device 79 to take over the reel 49.
In this
connection, the secondary transport device 5 and the secondary drive 39 can be
shifted into
the take-over position jointly or independently of each other. While the
secondary transport
device S is taking over the reel 49 from the primary pivoting levers 81, the
secondary drive
39 is coupled to the reel 49 so that temporarily, both drives 39 and 121 are
coupled to the reel
49. After this, the primary drive 121 is uncoupled from the reel 49 and moved
counterclockwise back along the first guide track into the reel-changing
position. The
diameter increase of winding roll, not shown, which is wound on the reel 49
guided by the
secondary transport device 5, is now compensated for during the finishing
winding by means
of a shifting of the secondary transport device 5 and consequently the reel 49
toward the right
in the direction of the arrow 33. The line force in the winding gap between
pressing drum 19
the winding roll wound on the reel 49 the and is controlled by means of a
shifting of the
pressing drum 19, as described above.
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For the sake of clarity, only one control of the winding machine 1 is shown in
Fig.
10, which includes a regulating device 65. For the explanation of the design
and the
operation of the regulating device 65, reference is made to the description-of
Fig. 5.
In a preferred exemplary embodiment, the provision is made that the pressing
drum
19 can be moved independent of the travel speed of the secondary transport
device 5, in order
to control the line force. It is furthermore possible that the stroke device
43 associated with
the secondary transport device 5, i.e. the motor 45 driving the threaded
spindle 47 can be
controlled in such a way that the position of the winding gap formed between
the pressing
drum 19 and the winding roll 37 is essentially constant. The "constant
position" of the
winding gap is understood to mean its position inside the winding machine 1.
The winding
roll 37 is thus shifted in the direction of the arrow 33 by means of the
secondary transport
device S with a speed that compensates for only the diameter increase of the
winding roll 37.
In another exemplary embodiment, the provision is made that the stroke device
43
associated with the secondary transport device S can be controlled in such a
way that the
position of the winding gap formed between the pressing drum 19 and the
winding roll 37
shifts with the increasing winding roll diameter during the winding process,
for example in
a range from 50 mm to 200 mm.
In a preferred exemplary embodiment, during the winding-on of an empty reel,
the
winding gap is always at the same location, i.e. its position inside the
winding machine
during a reel change is constant or at least basically constant. As a result,
during the winding
on of an empty reel, there are always equivalent angular ratios, for example
of the pressing
forces acting on the reel, so that the deflection of the empty reel can be
calculated and
correspondingly compensated for in order to adjust a desired line force
progression in the
winding gap. Naturally, in this exemplary embodiment it is also possible, with
a regulating
device 93 that is described for example in conjunction with Fig. 6, to shift
the reel-changing
position in which the winding gap is formed.
Fig. 12 schematically represents a side view of another exemplary embodiment
of the
winding machine 1. Parts that coincide with those described in conjunction
with Figs. 1 to
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11 are provided with the same reference numerals so that in this regard,
reference will be
made to the descriptions of Figs. 1 to 11. In this exemplary embodiment, the
primary
transport device 79 includes a securing device 127 that can be moved on third
rails 123 in
the direction of a double arrow 125 and the empty reel 49 is held in a
stationary and rotatable
fashion in this securing device 127. The securing device 127 thus permits a
rotary motion of
the reel 49 and hinders it from a translatory motion. By moving the securing
device 127, the
reel 49 can be moved from the reel-changing position (not shown), along the
straight first
guide track 14' realized by means of the rails 123, into the finished winding
position in
which the reel 49 rests on the guide rails 15. In addition, the reel 49 is
moved or lowered
from a higher level (G2) to a lower level (G1). The third rails 123 are
inclined in relation to
an imaginary horizontal H represented with a dashed line by an angle z, which
in the
exemplary embodiment shown in Fig. 12, lies in a range from 45° to
90°. Due to the
inclination of the rails 123, the travel path of the reel 49 from the reel-
changing position
downward into the finished winding position is similar to the travel path of a
reel that is
pivoted by means of primary pivoting levers around an axle 83 that is fixed in
relation to the
machine frame (Fig. 9).
Based on Fig. 12, a second embodiment of a control/regulation for adjusting
the line
force in the winding gap between the pressing drum and a reel or a winding
roll can be
inferred, which differs from the control/regulation described in conjunction
with Fig. 10 by
virtue of the fact that the travel speed of the secondary transport device 5
is adjusted or
changed as a function of the position of the piston 29 in the cylinder 27 of
the pressing device
25. The regulator 73 can control/regulate the pressure in the cylinder 27 and
consequently
the line force in the winding gap as a function of a number of parameters. The
parameters are
the longitudinal stress of the material web 3 (draw) measured with a measuring
device 129,
the diameter D of the winding roll 37, and an angle a, which indicates the
position of a reel
guided by the primary transport device 79. The diameter D of the winding roll
37 and the
angle a are inferred from a calculated and/or determined control curve, which
is shown by
way of example in Fig. 12.
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The angle a is measured between the straight line G1 and a plane 131 which
intersects the longitudinal axes of the pressing drum 19 and the empty reel
49.
The position of the piston 29 in the cylinder 27 is sent to the control unit
61 by way
of a signal line 133 and this unit controls the motor 45 of the stroke device
43, which motor
drives the threaded spindle 47.
Fig. 13 shows another exemplary embodiment of the winding machine 1 according
to the invention, with a control that is described in conjunction with Figs. 5
and 10. Parts that
are the same are provided with the same reference numerals so that in this
regard, reference
will be made to the descriptions of the preceding Figs. In this exemplary
embodiment, the
rails 22, upon which the guide block 21 which rotatably secures the pressing
drum 19 can be
moved, are inclined in relation to an imaginary horizontal by an angle (3,
which in this
instance lies between 0° and 45°. In a shift by means of the
pressing device 25 in the
direction of an arrow 135, the pressing drum 19 is raised from a lower-lying
level to a higher-
situated level, i.e. is moved obliquely upward. As is apparent from Fig. 13,
the pressing drum
19 is only in contact with the winding roll 37, but is not in contact with the
empty reel 49
disposed in the reel-changing position.
Also in the exemplary embodiment shown in Fig. 13, the weight of the pressing
drum
19 is still for the most part supported by the rails 22 so that a sufficiently
precise control of
the line force in the winding gap is readily possible. Only a small portion of
the weight of the
pressing drum influences the measurement precision and/or adjustment precision
of the line
force, namely only the slope descent component.
In another exemplary embodiment not shown in the Figs., the provision is made
that
the linear guidance, which is for the pressing drum 19 and is constituted by
the rails 22 and
the guide block 21, can be pivoted, for example with the aid of at least one
pivoting lever.
Figs. 14a to 14e each show a very schematic representation of a part of the
winding
machine 1 that has been described in conjunction with the preceding Figs. 1 to
11 and 13,
in various winding phases. Only the differences in operation are addressed in
detail below.
In the exemplary embodiment represented in Figs. 14a to 14e, before a reel
change, the new
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reel 49 is stored on the guide rails 15, not shown. In order to prepare for a
reel change, the
pressing drum 19 is moved into contact with a stop 117' which is positioned so
that when
the new reel 49 is brought into the reel change position, the pressing drum
l9is forced back
by the stop 117' while the reel 49 approaches the guide rails 15. The winding-
on of the new
reel 49 is thus carried out only after the reel is set down onto the rails, by
means of which
fluctuations and/or jumps in the line force progression that can occur when
setting the reel
down onto the guide rails during the winding-on operation are reliably
prevented.
Furthermore, the mechanical engineering costs of the winding machine described
in
conjunction with Figs. 14a to 14e can be simplified in relation to the other
exemplary
embodiments since for example, a stable lateral shaft for connecting the
primary pivoting
levers can be eliminated.
Also in the exemplary embodiment of the winding machine described in
conjunction
with Figs. 14a to 14e, the winding roll 37 can be continuously moved along the
second guide
track, i.e. without an intermediate stop. While the winding roll 37 in the
Figs. 14a to 14d is
guided toward the right, at the same time, the new reel 49 is lowered,
preferably
continuously, from the position shown in Fig. 14b into the position shown in
Fig. 14c. The
speed of the movements of the winding roll 37 and the new reel 49 in the
winding phases
shown in Figs. 14a to 14e can be constant or can change at least one arbitrary
point.
The above-mentioned process can be readily inferred from the description of
Figs.
1 to 14. It is comprised in that the material web is guided by way of a
pressing drum that can
be moved horizontally or at least essentially horizontally, which forms a
winding gap with
the winding roll that is rotatably secured in a secondary transport device.
During this winding
phase, the line force in the winding gap is controlled/regulated by means of a
shifting of the
pressing drum. When a desired winding roll diameter is reached, in order to
prepare for a reel
change, the winding roll is moved away from the pressing drum with the aid of
the secondary
transport device so that the material web travels freely from the pressing
drum to the winding
roll. A new reel, rotating at the web travel speed, is brought into a reel-
changing position by
means of a primary transport device and forms a new winding gap with the
pressing drum.
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Then, the material web is cut crosswise over its width and the new web
beginning is wound
onto the new reel. During this winding phase as well, the control/regulation
of the line force
in the winding gap between the pressing drum and the new reel is in turn
realized by means
of a shifting of the pressing drum. Finally, the secondary transport device
takes over the new
reel with the new winding roll. In this winding phase as well, i.e. when the
new reel is being
guided by the secondary transport device, the control/regulation of the line
force in the
winding gap is exclusively realized by means of a shifting of the pressing
drum. A desirable
winding result can be achieved by virtue of the fact that the line force is
adjusted by means
of a shifting of the pressing drum during the entire winding operation. A high
degree of
reliability during a reel change can be assured with the above-described
process since the
new reel, which is moved into the reel-changing position in the free draw, is
wound around
at least part of the way by the material web before the reel change takes
place.
From all of this, it becomes clear that in the above-described exemplary
embodiments
of the winding machine in which the primary drive can only be moved along the
first guide
track, whose design can therefore be simplified by virtue of the fact that the
primary drive
is mounted in a stationary fashion to a part of the primary transport device,
which can be
moved together with the reel along the first guide track. In another
embodiment of the
winding machine, the provision is made that the primary drive can be moved
both along the
first guide track and also part of the way along the second guide track.
Moreover, it is
naturally also possible that the secondary drive can be disposed in a
stationary fashion on the
secondary transport device, which further simplifies the design of the winding
machine.
In a particularly preferred exemplary embodiment that is not shown in the
Figs., the
stroke of the pressing drum, i.e. the maximal distance that the pressing drum
can be shifted
in one direction, is greater than or equal to the material layer thickness S
of a finished
winding roll. A secondary transport device that moves the reel during the
completion of the
winding process, in accordance with the diameter increase of the winding roll
can be
refrained from hereby. In this exemplary embodiment, the winding roll is thus
wound in two
fixed winding stations. A "fixed" winding station" is distinguished by the
fact that the reel
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is rotatably secured in such a way that both the diameter increase of the
winding roll wound
on it and the adjustment of the line force in the winding gap are realized
exclusively by
means of a shifting of the pressing drum. A fixed winding station has the-
advantage that it
offers an optimal rigidity of the reel mount so that a transmission of
possibly occurring
vibrations to the winding roll can be practically ruled out. Since the
shifting path of the
pressing drum is so great that the diameter increase can be completely
compensated for, a
constant reel tracking is not required, by means of which the design of the
winding machine
can be simplified.
It is common to all the exemplary embodiments of the winding machine that in
order
to prepare for a reel change, an intermediary space/a gap is foimed between
the almost
finished winding roll and the pressing drum. As a result, it can be assured
that before the reel
change, the material web is already guided over a circumference region of the
empty reel,
which is disposed in the reel-changing position. As a result, a high degree of
functional
reliability can be assured.
It is furthermore advantageous that as a result of the stationary, rotatable
securing of
the new reel at the beginning of the winding process in the primary transport
device, an
adj usting device of the kind that is frequently used in known winding
machines can be
eliminated. This adjusting device is employed to move the reel that is guided
by the primary
transport device radially in the direction of the pressing drum in order to
adjust the line force
in the winding gap. Because of this advantageous embodiment, an additional
control/regulation for the adjusting device can be omitted so that the costs
of the winding
machine are reduced.
It is common to all the exemplary embodiments of the winding machine that the
control/regulation of the line force in the winding gap can, according to the
invention, be
exclusively carried out during the entire winding process by a single device,
namely by
means of a shifting of the pressing drum with the aid of the pressing device
25.
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It is furthermore particularly advantageous that existing, i.e. already
assembled
winding machines can be retrofitted so that one of the above-described
processes for winding
the material web 3 can be realized. ---
Alternatively to the reel, the winding machine can be equipped with a winding
core
S to which a winding sleeve or a number of winding sleeves are attached. In
the latter case, the
winding machine can be preceded by a longitudinal cutting device. This cuts
the web into a
number of partial webs, wherein each partial web is wound onto a winding
sleeve.
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