Winding machines with contact roller control device

Winding machines having a traversing member, a contact roller, said roller or a winding tube chuck being mounted on a linearly movable carriage moved by piston-cylinder members, pneumatically operated control systems connected with said piston-cylinder members to move said carriage horizontally or vertically relative to the winding package or the contact roller, and frictionlessly operating membrane cylinder(s) mounting a support member for the carriage-mounted chuck or contact roller on the carriage, the pneumatic control system and membrane cylinder(s) maintaining constant pressure between the winding package and contact roller.

INTRODUCTION 
With the introduction of rapid spinning and spin-drawing of synthetic 
fibers it has become necessary also to increase the winding machines. 
However by increasing the winding speeds, the noise level of the machine 
has also been increased. Numerous investigations have shown that the noise 
level is a function of the magnitude of the pressure between the contact 
roller and the winding package (bobbin). 
A series of winding machines are known in which attempts were made to lower 
the pressure force between the contact roller and the package. Thus, for 
example, German Offenlegungsschrift No. 2,048,416 describes a device in 
which the pressure between the contact roller and the package is 
adjustable by means of a cylinder piston unit. This device, however, has 
the disadvantage that the pressure is applied simultaneously by the drive 
unit for the production of the carriage movement. Thus, irregularities in 
the carriage movement are reflected in the contact pressure so that it 
does not remain constant. In addition, the friction in the drive units has 
a disadvantageous effect on keeping the contact pressure constant. A 
further disadvantage is that irregularities in the carriage movement or in 
the winding package formation can lead to loads on the carriage. These 
must be damped because of the danger of resonant vibrations. Because of 
the large masses the necessary damping is complex. 
The same difficulties occur in the case of winding machines with bobbin 
revolvers. In addition, there is the added difficulty that, during bobbin 
changing, the first thread layers have already formed on the empty winding 
tube, which layers also should not be damaged. For this reason the above 
mentioned German Offenlegungsschrift No. 2,048,416 also describes a device 
for controlling the carriage movement. The control arrangement uses cam 
plates and sensing devices sliding thereon. This type of control has the 
disadvantage that in addition to a plurality of cam plates, sensing 
devices and relays, there is no indication of the correctness or 
completeness of the movement to be carried out or which has been carried 
out. In addition, these cam plates are limited to very specific bobbin 
diameters and bobbin sizes. A further disadvantage of the control 
arrangement is that control commands are tripped without any guarantee of 
the correctness of the moment of tripping. 
THE INVENTION 
An object of the invention is to provide a winding machine for winding 
synthetic threads which permits a precisely defined contact pressure, 
adjustable within wide limits, to be applied between the contact roller 
and the packages being formed. 
A "contact roller" is a roller which is in frictional contact with the 
bobbin (package) surface. In this arrangement it can serve as a friction 
roller and drive the bobbin directly or serve as a package-driven control 
roller which controls or measures the rotational speed of the bobbin 
drive. 
Another object of the invention is to provide a control device for a 
winding machine so that any alteration of the contact pressure is 
immediately stabilized during the winding time without having to interrupt 
the winding process. 
Yet another object of the invention is to design the means for applying the 
contact pressure so that it is transmitted without delay and without 
friction. 
A further object of the invention is to develop a control device for use in 
winding machines with bobbin revolvers, which device can also be used 
during the thread transfer from the wound bobbin to the empty tube. 
A further object of the invention is to design the above mentioned winding 
machine in such a way that the possible friction in the drive elements 
which depends on the "stick-slip" effect is reliably avoided. 
An advantage of the invention is that the contact pressure between the 
contact roller and the bobbin or package surface is applied by a separate 
machine element which is used simultaneously for the production of the 
actual value in the control circuit and which can be adjusted 
independently of the drive elements of the carriage. As a result it is 
possible for the machine to work with extremely low pressure forces e.g., 
1000 g. Even in the case of multi-level construction, i.e., with the 
traversing device and contact drum arranged above the winding spindle or 
vice versa, the contact pressure can be produced independently of the 
weight of the moving machine parts. Furthermore, it is advantageous that 
in the case of the winding machine according to the invention awkwardness 
or irregularities in the carriage movement or as a result of faults in the 
bobbin package build up are not transmitted to the carriage which carries 
either the bobbin or the contact roller but only to a support device 
having a low mass which can be easily damped. Additionally, by 
facilitating very low contact pressures, the danger of damage to the 
individual winding layers is avoided. Furthermore, as a result of these 
low contact pressures, profiled or textured threads can be wound without 
difficulty, which otherwise would be deformed by an excessively high 
contact pressure. 
The winding machine according to the invention has moreover the advantage 
that the element applying and transmitting the contact pressure is able to 
pick up friction influences and irregularities of the carriage drive and 
render them technically harmless. If, contrary to expectations, the 
element does not do this, then it is possible to avoid them in a 
development of the invention in which a hydraulically acting cylinder and 
piston unit which acts externally on the carriage. This dampening unit 
requires no additional external energy source such as a pump. It is not 
necessary to provide a new control circuit on the winding machine since 
only the control elements are modified. 
In order to be able to regulate or control at any time the contact pressure 
independently of design modifications, a membrane cylinder filled with gas 
and liquid is used as a force storage unit according to the invention. By 
a "membrane cylinder" is meant a cylinder in which no piston moves to and 
fro, but has a pressure chamber closed by a membrane or membranes. This 
membrane cylinder offers the advantage of having no sealing problems and 
being able to execute without friction the necessary small movements, 
typically of the order of 0.1 mm to 0.8 mm, required to determine the 
actual value described below. 
In order to prevent irregularities in the roundness of the bobbin or 
package surface from setting up vibrations, this membrane cylinder is also 
provided with a damping element. The damping is achieved by the membrane 
cylinder being filled with oil in its lower half and with air in its upper 
half. Additionally, it is advantageous with membrane cylinders that they 
should effect an absolutely rectilinear motion so that the elements held 
by them require no additional rectilinear guidance. Thus, it is 
particularly suitable for the production of an actual value since it is 
certain that any magnitude of fault will immediately produce a 
modification of the actual value. 
As the actual value is indicated very exactly and precisely, the regulator 
must possess the same working accuracy. Nozzles can be used as regulators 
in the sense of the invention, the nozzles being mounted on the carriage 
and at a distance from the support plate, thus forming a 
nozzle-impingement plate system. Contrary to expectations it has proved 
that the nozzle-impingement plate system is suitable in a very simple form 
as a highly effective working regulator. However, should the response 
sensitivity of this simple system not be sufficient, then it can be varied 
by the interconnection of suitable elements, e.g. throttles and force 
storage units. Control slide valves which are mechanically connected to 
the support device and thus can be activated in proportion to the change 
in the actual value can also be used as regulators. 
Since the force storage unit, for example, the membrane cylinder, is 
constructed so as to be vibration free and friction free, the change in 
the distance between the nozzle and the support device can be used very 
well as the control value, since this responds with very great accuracy 
and without delay, and without unwanted response to any fault value. 
The throttle for determining the desired value also has the advantage that 
with its use the sensitivity of the control system can be adjusted in such 
a way that, by exploiting the force-distance dependency of the force 
storage unit (for example, the membrane cylinder mentioned above), the 
contact pressure between the contact roller and the bobbin or winding can 
be adjusted. In addition, by the use of an adjustable throttle which can 
be controlled by a time or distance control as a function of the amount of 
axial movement, a constant or variable contact pressure can be achieved by 
simple means during winding time. The adjustment of the contact pressure 
is also possible if, when the force storage unit has a distance-dependent 
force characteristic, the nozzle is arranged so as to be axially movable 
in its mounting.

FIG. 1 shows a winding machine with a frame 1 and a carriage 2 mounted for 
slidable horizontal movement in guides 3. A chuck shaft 11 is mounted on a 
support member 9 which in turn is mounted on the carriage 2. A bobbin tube 
15 is fitted on and secured to the chuck shaft 11 in known manner. The 
suppport member 9 comprises an arm 6 and a yoke 10. The support member 9 
of FIG. 1 is like the double arm support member for the roller as shown in 
FIG. 3 -- only one arm 6, however, being used in order that bobbin tubes 
15 and wound bobbins or packages can be slipped onto and off the free end 
of the cantilever-mounted chuck shaft 11. 
The yoke 10 is attached via a force storage unit 27 to the carriage 2. The 
weight of the bobbin package is borne by a slide guide (not shown) in the 
carriage 2, e.g., a slide guide slidably supporting arm 6 for movement 
parallel to the direction of carriage travel. The carriage is moved by 
pneumatic cylinders 4 and 5 having their cylinders mounted on the frame of 
the machine 1. Their piston rods 7, 8 are attached in a suitable manner to 
the carriage 2. In order to ensure trouble-free working of the winding 
machine, the pneumatic cylinders 4 and 5 are both supplied with compressed 
air. 
A traversing device 12 is mounted in the machine frame 1, and comprises a 
reverse threaded shaft 13 and a thread guide 14 driven reciprocally by the 
shaft 13. The oncoming thread T runs over a grooved roller 15 and subtends 
a circumferential angle of roller surface contact of at least 60.degree.. 
The grooved roller 15 has a spiral groove (not shown) in its cylindrical 
surface. The running thread rides in the spiral groove and is traversed 
thereby in synchronization with the reciprocating guide 14 in a known 
manner. A friction drive roller (or a winding-driven control roller) 16 
having a fixed axis of rotation is mounted in the frame 1 below the 
grooved traverse roller 15. The two traversing members and the drive 
roller 16 are driven by conventional and known mechanisms in the desired 
speed synchronization. See U.S. Pat. No. 3,913,852. 
Two nozzles 17 and 18 are used to control the carriage movement, both 
nozzles being mounted on the carriage 2 adjacent the yoke 10. Nozzle 17 is 
connected by air pressure lines 19, 20 and 21 to the ends of cylinders 4 
and 5 which project the piston rods 6 and 7. The nozzle 18 is connected by 
air pressure lines 22, 23 and 24 to the opposite ends of cylinder 4 and 5. 
The compressed air supply lines for the cylinders and nozzles each have a 
throttle or choke 25 and 26. 
The support member 9 has its yoke 10 connected to a force storage unit, 
later described in detail, to provide controlled horizontal movement of 
the support device 9 and the package supported thereon. Compressed air for 
operating the force storage unit is supplied through compressed air line 
28. 
In the winding machine shown in FIG. 2, the carriage 32 is moved vertically 
in the guides 33 by the two pneumatic cylinders 34 and 35 mounted on the 
frame 31. In contrast to FIG. 1, the traversing mechanism consisting of 
the reciprocating thread guide 36, its reverse thread shaft 37 and the 
grooved roller 38, as well as the package friction drive roller 39 are 
mounted on the carriage. The drive roller 39 in this embodiment is 
supported in the support member 40 which consists of two arms 41 (c.f. 
FIG. 3) connected by a yoke 42. The yoke 42 is connected by the force 
storage unit 27 to the carriage. The chuck shaft 43 with the bobbin tube 
44 is positioned below the carriage 32. Since the carriage can travel 
downwards under its own weight the control device can be substantially 
simplified in this embodiment. The pneumatic cylinders 34 and 35 are 
therefore single-acting pressure cylinders supplied with pressure at their 
lower ends only by compressed air lines 45-47. The nozzle 48 is connected 
by compressed air line 49 in the compressed air system parallel to the 
pressure chamber of the cylinders. The throttle 25 is positioned between 
the cylinders and a pressure medium reservoir 51 in the supply line 50. 
The force storage unit 27 in FIG. 2 is adapted to move the drive roller 39 
vertically to a limited degree relative to the carriage 32. As described 
hereinafter, the nozzles 17, 18 (FIG. 1) and the nozzle 48 (FIG. 2) coact 
with a compressed air impingement surface or surfaces, e.g., the 
impingement plates 52 projecting from yoke 10 and yoke 42, respectively. 
FIG. 3 is a perspective view of the winding machine shown schematically in 
FIG. 2, showing more clearly the way in which the support device is 
mounted in the carriage 32. The yoke 42 is mounted in the carriage 32 by 
two force storage units 27 which extend through and are fixedly mounted in 
the slot 53 in the top plate 54 of the carriage 32. 
In the embodiment of FIG. 3, the impingement surface for compressed air 
issuing from the nozzle 48 (shown schematically in FIG. 2 as the plate 52) 
is the top surface of the yoke 42. The nozzle 48 is mounted fixedly or 
adjustably in the slot 53 between the two force storage units 27. The 
distance between the nozzles 17, 18 and 48 and the plate 52 or yoke 42 
(FIG. 3) is very small whereby a small movement of the plate or yoke 
materially changes the back pressure on the air exiting from the nozzle. 
The effects of such changes are discussed below. 
FIG. 4 shows a section through the force storage unit 27 used in the 
invention. The force storage unit 27 comprises a cylindrical body 60 with 
an upper membrane disc 61 and a lower membrane disc 62 smaller in 
pressure-exposed area than the membrane 61. The two membranes 61 and 62 
are clamped about their peripheries on the raised annular shoulders 63 and 
64 of the body 60 by means of clamping rings 65 and 66. A cylindrical 
member 67 is loosely positioned in an axial bore 68 in the cylindrical 
body 60, its diameter being slightly smaller than the diameter of the 
bore. An annular gap 69 is thus defined between the member 67 and bore 68. 
The end faces of the cylindrical member comprise coaxial cylindrical 
recesses 70 and 71 defined by ring walls 72 and 73 and the inside walls of 
the annular shoulders 63 and 64. These recesses provide annular chambers 
76 and 77 beneath each membrane, which chambers are connected by the 
annular gap 69. 
The center portion of each membrane 61 and 62 is covered by a rigid disc 74 
and 75. These discs are fixedly attached to respective opposite ends of 
the cylindrical member 67, with the central parts of the membrane clamped 
therebetween. The members 67, 74, and 75 are movable axially relative to 
the cylindrical body within limits -- their position being determined by 
the relative difference in total pressure force exerted on membrane 61 vs 
membrane 62. 
The total pressure-force-exposed area of membrane 61, which with disc 74 
forms the movable annular wall of chamber 76, is greater than that of 
membrane 62, which with disc 75 forms the movable wall of chamber 77. 
A compressed air passage 78 in the body 60 having a tapped inlet 79 for 
connecting a coupling of the compressed air line 28 communicates with the 
chamber 76. The other chamber 77 communicates with another passage 80 in 
the body 60, the outlet end of which passage is closed by the threaded 
plug 81. 
The force storage unit 27 is about half-filled with oil 82 through the 
passage 80. Preferably, the oil filled portion has a throttle or choke 
structure, which in the illustrated embodiment is provided by the narrower 
gap between the cylindrical member 67 and the ring 83 on the lower end of 
the axial bore 68. The resulting throttle or choke gap thereby is always 
immersed in oil. The lower disc 75 of each force storage unit 27 is 
fixedly attached to yoke 42. 
The operation of the aforesaid embodiments will now be described in more 
detail. Only the elements necessary for an understanding of the control 
system have been illustrated in the FIGS. 1 - 3, and other elements which 
are usual or necessary for safe winding but which are conventional in the 
case of winding machines have been omitted. 
When starting up the winding machine, the force storage unit 27 is supplied 
with compressed air at working pressure, usually 6 bars, through the inlet 
bore 78. Depending on the value of the pressure force area difference 
between the membranes 61 and 62, a predetermined holding force is produced 
by the unit 27. This holding force can be varied by interposing an 
adjustable pressure reducing element in the line 28. The pressure in the 
force storage unit 27 is adjusted in such a way that the weight of the 
support member 41, 42 and the contact roller supported therein (FIGS. 2 
and 3) is largely compensated. In FIG. 1 the pressure is adjusted so that 
the desired pressure is present between the contact roller and the bobbin 
package -- the oil 82 in the unit also being eliminated. 
If the winding machine shown in FIG. 1 is constructed in such a way that 
the carriage 2 moves vertically, a control device must be interposed in 
the supply line to the force storage unit 27 so that a constant residual 
force is always present to cause the bobbin to exert pressure on the 
contact roller. The control device can for example be in the form of a 
template, a control valve then being associated with the carriage, which 
valve scans the template attached to the machine frame. 
If the bobbin package grows in diameter in the case of the winding machine 
shown in FIGS. 2 and 3, the contact roller and the support device move out 
of their working position. Here the force storage unit 27 shown in FIGS. 2 
and 3 behaves as follows. The two membranes 61 and 62 curve upwards, as a 
result of which the oil 82 in the lower chamber 77 is pressed through the 
throttle gap at 83. This produces a slight damping effect and avoids the 
setting up of oscillations in the system. 
At the same time the gap between the nozzle 48 and the yoke 42 becomes 
smaller, so that the quantity of air flowing out of the nozzle also 
becomes smaller. As a result almost all of the air flowing through the 
throttle 25 is now supplied to the pneumatic cylinders 34 and 35. The 
carriage therefore moves upwards. As a result the support device 41, 42 
with its weight and that of roller 19 supported by the force storage units 
27, drops down again by the distance covered by the upward carriage 
movement and the gap between the nozzle 48 and the yoke 42 becomes greater 
again. The carriage remains stationary once the working gap has been 
reached again between the nozzle and the yoke. When the support device 
moves down into its working position the deflection of the membranes is 
reversed and the oil is pushed back through the throttle by the air 
pressure prevailing in the annular space 76. A reverse sequence occurs 
when the support device is moved downwards past its working position. 
In FIG. 1, as the bobbin package diameter increases, so does the gap 
between the nozzle 18 and the support device 9, while the gap between the 
nozzle 17 and the support device 9 is reduced. In this way the pneumatic 
cylinders 4 and 5 are supplied with compressed air in such a way that the 
carriage moves to the left. When the carriage moves, the air on the 
left-hand side of the pistons in the cylinders 4 and 5 can flow out at the 
nozzle 18. As a result of the carriage movement, the working gap readjusts 
itself between the nozzle 18 and the plate 52 on the one hand and the 
nozzle 17 and the plate 52 on the other hand until pressure equilibrium is 
reached and the carriage comes to a standstill. 
By incorporating an adjustable throttle or choke 25, 26 in the common 
supply line 20, 29 or 49 to the nozzle 17, 18 or 48 and the pneumatic 
cylinders 4 and 5, the response sensitivity of the system can be adjusted. 
If an adjustable pressure reducing is incorporated in the supply line 28 
to the unit 27, the pressure holding force applied by the unit 27 can be 
varied during the operation of the winding machine. A further way of 
adjusting the holding force is to mount the nozzles 17, 18 or 48 by 
adjustable means whereby their distance from the impingement plate 52 or 
yoke 42 can be varied. For any given gap between the respective nozzles 
and the impingement plate or yoke, the carriage adjusts itself so that it 
has a corresponding equilibrium position. In this way the relative 
position of the contact roller 16 or 39 can be adjusted in relation to the 
carriage, which position is then stabilized during the diameter increase 
of the bobbin by coaction of the nozzle(s) and yoke or plate. It is also 
possible to bring about a change of the pressure between the bobbin and 
the package being formed by adjusting the throttle or choke. The changing 
of the holding force during the winding operation has already been 
described above. 
As has been shown by exhaustive tests, oscillations induced during winding 
on the bobbin or contact roller and their respective support members 9 or 
41, 42, are immediately damped by the force storage units used in the 
invention. Because of the way in which movement of the carriage is 
controlled, sudden changes in load have no long lasting or significant 
influence on the movement of the carriage so that a constant pressure 
between the winding and the contact roller is ensured. 
FIG. 5 shows a winding machine which is similar to that of FIGS. 2 and 3 
except that a bobbin revolver is provided on which two chuck shafts 86 and 
87 are mounted, each shaft having a winding tube 88 and 89 respectively. 
Additionally, a thread transfer device 90 is provided on the machine. For 
further details, reference is made to U.S. Pat. No. 3,913,852. 
The winding machine of FIGS. 5 and 6 has a control device which works 
alternately with two regulators whose significance is explained further 
below. The regulator comprises discs 95, 96 and 97. These discs are 
designed as electrical contacts. The disc 95 is mounted coaxially with the 
axis of the grooved traversing roller 38. The other two discs 96 and 97 
are mounted on the chuck shafts 86 and 87, respectively, all three discs 
being in coplanar alignment with one another. All three discs are 
electrically insulated from the machine frame 31 and the bobbin revolver 
85. The diameter of the disc 95 is greater than the diameter of the 
grooved roller 38. In addition, the diameters of the discs 96 and 97 are 
slightly greater than the diameter of the winding tubes 88 and 89. 
At high winding speeds, in order to avoid backing-off, it may prove 
necessary to keep constant the length of thread between the point at which 
the thread leaves the grooved traversing roller 38 and the point at which 
the thread runs on to the bobbin winding. For this reason, as indicated in 
FIG. 6 by a broken line member 99, both the contact roller 39 and the 
grooved roller 38 are supported in the movable support device 41, 42 so 
that they move up and down together. 
The operation of the control device used in FIG. 6 for controlling carriage 
movement will now be illustrated in greater detail with reference to the 
schematic circuit diagram shown in FIGS. 7 and 15. The diagram shows only 
the elements necessary to understand the invention. Reference should also 
be made to the working positions of the bobbin revolver shown in FIGS. 9 
to 12. 
FIG. 9 shows the bobbin revolver 85 in its working position. It is stopped 
by stopping means (not shown) in known manner in this position (not 
shown), and a signal emitted by this stopping is designated in FIG. 15 by 
the numeral 127. With increasing bobbin diameter, the carriage 32 must be 
moved vertically upwards. This movement takes place under the control of 
the support device 41, 42 which is mounted in such a way as to be movable 
relative to the carriage. The growth of the winding W deflects the support 
device upwards via the contact roller 39. As a result a signal 125 (see 
FIG. 15) is emitted. As the axial discs 95 and 96 or 97 are not in contact 
with one another a signal 123 is also emitted. When these three signals 
127, 125, 123 are present, a signal appears at the output of the AND gate 
135 which switches a valve Db1 and, via the OR gate 141, switches a valve 
W1 into position "1". As a result, pressure medium, generally compressed 
air, passes from a pressure medium source (e.g., a pump) or from a storage 
container (not shown) via pipes 122, 122.1 and 122.4 into the pneumatic 
cylinders 34 and 35 (FIG. 7). The pistons and their rods in the pneumatic 
cylinders are thus moved out. Flow of pressure medium out of the pneumatic 
cylinders 34 and 35 is regulated by the position of the support device 41, 
42 via the valve Db1, which is incorporated in a pipe 122.7 connected via 
a pipe 122.5 to the pneumatic cylinders and via a pipe 122.9 to the valve 
W1. By the upward movement of the carriage 32, thus produced, the contact 
roller 39 is again lowered into its working position and the valve Db1 is 
closed. The carriage 32 thus comes to a standstill. As a result, the 
signal 125 ceases and a signal 126 is emitted. This causes a signal to 
appear at the output of the AND gate 136 which switches the valve W1 into 
the "0" position. 
If, because of some fault, the carriage 32 moves too far upwards, the 
support device 41, 42 after passing its working position is moved 
downwards. This causes the emission of a signal 124 which is applied to 
one input of the AND gate 137. As a result a signal appears at the output 
of the gate 137 which switches the valve Db2 and, via the OR gate 140, 
switches the valve W1 into position "2". Valves Db1, Db2 are like 
throttles which regulate continously the flow-through of the compressed 
air from 0 to maximum. As a result the direction of movement of the 
carriage 32 is reversed. The compressed air now passes via the pipes 
122.9, 122.6 and 122.5 into the upper part of the pneumatic cylinder (FIG. 
7). The outflow is regulated as a function of the particular position of 
the support device 41, 42 by the valve Db2, and the compressed air flows 
back through the pipe 122.4, 122.2 and 122 to the valve W1. The carriage 
32 moves downwards until the support device 41, 42 is back in its working 
position. In so doing the signal 124 ceases and the signal 126 is again 
present so that the AND gate 136 switches the valve W1 into position "0". 
The carriage 32 therefore comes to a standstill. 
Once the winding w on the tube 89 has reached its predetermined size, the 
bobbin change process is initiated via suitable sensing devices. To do 
this, means stopping movement of the bobbin revolver 85 are first of all 
released. As a result the signal 127 ceases and a signal is therefore 
present at the output of the NOT gate 138 and 131. 
A rotational moment is exerted by the full bobbin W on the drive of the 
bobbin revolver 85 which tends to cause the full bobbin to rotate suddenly 
downwards. In order to prevent such sudden rotational movement of the 
bobbin revolver 85, a braking moment is applied to the motor provided to 
drive the bobbin revolver 85. As a result the bobbin revolver rotates 
slowly. 
Simultaneously with the release of the stopping means of the bobbin 
revolver, the bobbin tube 88 is accelerated by drive applied to the axis 
thereof to the required circumferential speed. The support device 41, 42 
is moved downwards out of its working position by the rotation of the 
bobbin revolver. The signal 124 is emitted and, as the axial discs 95 and 
96 are still not in contact, the signal 123 continues to be emitted. Thus 
a signal appears at the output of the AND gate 133 so that the valve W1 is 
switched into position "2" via the OR gate 140, and the valve W2 is 
switched into position "1". The rate of flow through the valve W2 or W3 is 
chosen to be such that the carriage 32 can follow the rotational movement 
of the bobbin revolver 85 and is not too fast. Thus the carriage 32 
follows the downwards movement of the full bobbin W by the pneumatic 
cylinders 34 and 35 being supplied with compressed air via the pipes 
122.9, 122.6 and 122.5. Air flowing out of pneumatic cylinders passes out 
via the pipes 122.4, 122.3 and 122. 
The bobbin revolver 85 rotates until it reaches the position shown in FIG. 
10. At this point the AND gate 136 receives signals 123 and 126. A signal 
therefore appears at the output of the AND gate 136 which switches the 
valve W1 into position "0". This causes both the bobbin revolver and the 
carriage to be stopped. In this position the thread is transferred by the 
thread transfer device 90 from the full bobbin W to the empty tube 88. 
After the thread transfer the bobbin revolver continues to rotate. As a 
result the axial spacing discs 95 and 96 come into contact while at the 
same time the support device 41, 42 is moved downwards again out of its 
working position. 
The signal 123 now ceases and the signal 122 and the signal 124 and the 
inverted signal 127 are emitted. Consequently the signal 123 is missing 
from the AND gates 133, 134, 135, 136 and 137, so that the carriage 
control can only be operated via the AND gates 128 and 130. 
When the signals 122, 124 and the signal 127 inverted by the NOT gate 131 
are present, a signal is present at the output of the AND gate 128, and as 
a result the valve W1 and the valve W3 are switched into position "1" via 
the OR gate 132. As a result the pneumatic cylinders 34 and 35 are 
provided with compressed air via the pipes 122, 122.1 and 122.4, which 
leaves the cylinders via the pipes 122.5, 122.8 and 122.9. The carriage 32 
travels vertically upwards until the discs 95 and 96 move out of contact. 
At the same time the bobbin revolver 21 rotates further. The support 
device 41, 42 is moved completely downwards. 
FIG. 11 shows a position in which the carriage 32 must reverse its 
direction of movement. As long as the spacing discs 95 and 96 are in 
contact, the carriage 32 travels upwards. As a result of the continued 
rotation of the bobbin revolver past the position shown in FIG. 11, the 
spacing discs 95 and 96 cease to be in contact. Thus in FIG. 15 the signal 
122 ceases and the signal 123 reappears. Since now the signal 123, the 
signal 124 and the signal 127 inverted by the NOT gate 138 are all present 
at the inputs of the AND gate 133, a signal appears at the output thereof 
which causes the valve W2 to be switched into position "1" and via the OR 
gate 140 the valve W1 to be switched into position "2". The carriage 32 
moves downwards as the pneumatic cylinders 34 and 35 are supplied with 
compressed air via the pipes 122.9, 122.6 and 122.5. The air flowing out 
of the pneumatic cylinders passes out via the pipes 122.4, 122.3 and 122. 
As the bobbin revolver rotates continuously and the carriage 32 cannot 
change its direction of movement suddenly, there is a slight delay before 
the carriage 32 follows the rotation of the bobbin revolver 85 and moves 
downwards. As a result the spacing discs 95 and 96 remain out of contact 
with one another. 
The rotational speed of the bobbin revolver and the downward movement of 
the carriage are adapted to one another in such a way that, in the working 
position shown in FIG. 12, the support device 41, 42 is raised back into 
its working position via the contact roller 39. At the same time the 
spacing discs 95 and 96 again come into contact. The signals 122, 126 and 
the inversion of the signal 127 are thus present as the inputs of the AND 
gate 130 which thereby switches the valve W1 and the valve W3 into 
position "1" via the OR gate 132. The carriage 32 moves vertically upwards 
as the pneumatic cylinders 34 and 35 are supplied with compressed air via 
the pipes 122, 122.1 and 122.4, the air exiting via the pipes 122.5, 122.8 
and 122.9. 
However, the carriage 32 moves only slightly, since with rotation of the 
bobbin revolver or with upward movement of the carriage, the spacing discs 
95 and 96 are again immediately disengaged. Consequently the signal 122 
ceases and the signal 123 reappears. However since the bobbin revolver is 
rotated further into its working position, the support device 41, 42 is 
displaced upwards. As a result the signals 123, 125 and the inversion of 
the signal 127 are supplied to the inputs of the AND gate 134 so that it 
switches the valve W3 and via the OR gate 141, switches the valve W1 into 
position "1". The pneumatic cylinders 34 and 35 are supplied with 
compressed air via the pipes 122, 122.1 and 122.4 which leaves them via 
the pipes 122.5, 122.8 and 122.9. 
The support device 41, 42 is lowered into its working position by the 
upward movement of the carriage 32 and the signal 125 ceases. As the 
bobbin revolver 85 in the meantime has reached its working position (FIG. 
9), it is stopped. As a result, the signal 127 is emitted and a signal 
therefore applied to the AND gate 136 to cause the carriage 32 to stop. 
The above described operational cycle can then start again. The dotted 
lines in FIG. 7 designate electrical circuits which connect discs 95, 96 
(or 95, 97) with solenoids 150 of valves W1, W2 and W3. 
Symbols in the flow diagram designating conventional parts include one way 
or check valves 145, constant pressure regulating units 146, and 
compressed air pumps or reservoirs 147. The broken lines in FIGS. 7 and 8 
symbolize electric and electropneumatic circuits which operatively connect 
the spacer discs 95, and 96, valve solenoids 150, throttle-like valves 
Db1, Db2 and a sensor unit 148 which monitors the relative positions of 
the contact roller support device 41, 42. 
The spacer disc 95 is mounted coaxially with the spirally grooved 
traversing roller 38, and the additional spacer discs 96, 97 are mounted 
coaxially with each respective chuck 86, 87. The spacer discs lie in a 
common vertical plane whereby, during the bobbin changing step by 
revolving the bobbin revolver through the cycle illustrated in FIGS. 9-12, 
the distance between the empty tube surface and said spirally grooved 
traversing roller surface is kept constant by edge-to-edge contact of disc 
95 with a respective disc 96 or 97. 
The full bobbin W is removed from the chuck shaft 87 and a new empty tube 
is substituted. 
FIG. 8 shows a different control device for the controlling movement of the 
carriage. In contrast to the device shown in FIG. 7 it comprises two 
nozzles 101 and 102 which coact with the nozzle-impingement plate 103 on 
the yoke 104. The complexity of switching is substantially simplified. 
During the winding process the control system works in a similar manner to 
that described in FIG. 1, as the valve W4 is switched into the illustrated 
blocking position. 
During the bobbin-changeover, the switching sequence is as follows. As a 
result of the rotation of the bobbin revolver 85, the distance between the 
nozzle 101 and the plate 103 increases. Thus the air can escape from the 
undersides of the pistons in the cylinders 34 and 35, allowing the 
carriage 32 to move downwards. With the continued rotation of the bobbin 
revolver, the spacing discs 95 and 96 come into contact with one another. 
As a result the valve W4 is switched via circuit 105 to its on position. 
Thus compressed air then flows via the pipe 106 into the pipe 107. As a 
result, the pistons in the pneumatic cylinders 34 and 35 move upwardly. 
The gap between the nozzle 101 and the yoke plate is not of any 
significance, since air is admitted into the system both via the throttle 
D2 and the pipe 108 and also through the valve W4, the pipe 106 and the 
pipe 107. As the carriage moves upwards air expelled from above the 
pistons in the cylinders 34 and 35 escapes via the pipe 109 and the valve 
W4. 
If the spacing discs 95 and 96 move out of contact, the valve W4 is 
switched back into the blocking position. This prevents any more air from 
being introduced via the pipe 106 into the operating system and the air 
flowing in through the throttle D2 and the pipe 108 can flow away at the 
nozzle 101. At the same time air flows out of the chambers below the 
pistons in the cylinders 34 and 35 via the pipes 107 and 108 and thence 
out of the nozzle 101. The carriage 32 therefrom moves downwards again. 
As has been confirmed by exhaustive tests, this very simply but reliably 
constructed pneumatic circuit is quite adequate to carry out safely all 
operational sequences occurring during winding and bobbin change. 
Instead of using two nozzles 101 and 102 it is possible instead to use only 
one nozzle 101. During winding this control device then operates like that 
described with reference to FIGS. 2 and 3. During bobbin changing the 
device then works as described above. However, in this case the carriage 
32, which moves downwards under its own weight, may move downwards too 
slowly in relation to the rotational speed of the bobbin revolver 85. In 
this case the circuit shown in FIG. 7 or 8 is preferable. 
FIG. 13 shows a machine similar to that illustrated in FIG. 3 but has a 
hydraulic cylinder 151 mounted on the frame 31 with its extensible piston 
rod 152 connected to the carriage 32. Otherwise the same reference 
numerals have been used as in FIG. 3. The operation of the hydraulic 
cylinder 151 and its control will now be described with reference to FIG. 
13 and the schematic circuit diagram of FIG. 14. 
The thread T is guided vertically downwards to the traversing device 36. 
The thread T is traversed by the grooved roller 38 as it is wound on 
winding W. The bobbin tube 44, as is true also in FIGS. 1 to 3, may be 
driven by a drive applied to chuck 43 so that the contact roller 39 has 
basically only a control function. However it is alternatively possible, 
as explained above, to drive the bobbin tube and its winding via the 
contact roller 39. The force storage units 27 are identical with those 
shown in FIGS. 3 and 4. 
In contrast to the previously described embodiments, the weight of the 
carriage 32 is over compensated by the pneumatic cylinders 34 and 35, so 
that is no extra downward force were applied the carriage 32 would move 
into its uppermost position. To prevent such upward movement a downward 
force is generated in the hydraulic cylinder 151 in such a way that this 
downward force together with the force resulting from the weight of the 
carriage is equal in value to the force generated by the pneumatic 
cylinders 34 and 35. The contact roller 39 therefore contacts the bobbin 
surface with a pressure which is predetermined by the force storage unit 
27. As a result there is an equilibrium of forces which enable the 
carriage 32 to be maintained in any position. The pressure in the 
pneumatic cylinders 34 and 35 is kept constant during the whole winding 
process. 
To illustrate the operation of this embodiment, when a fully wound bobbin 
has just been replaced on the chuck shaft 43 by an empty bobbin tube 44, 
the carriage 32 is in its uppermost position. The valve W5 (FIG. 14) is 
switched into position "2". This can, for example, be effected by hand or 
in the case of automatic bobbin changing by sensing devices (not shown) or 
by a time relay which is triggered off by the carriage or by a full bobbin 
at any predetermined time. Movement of the valve W5 into position "2" 
causes the carriage to move downwards. Simultaneously with the movement of 
the valve W5 into position "2" a valve Db4 is opened. The valve Db4 is 
controlled by the pressure in the pipe 155 which is originated when the 
valve W5 is switched into position "2". As a result the hydraulic cylinder 
151 is placed in communication with an oil reservoir 153. As a result of 
the downwards movement of the piston 154 in the hydraulic cylinder, it 
sucks oil from the storage container via the valve D b4 into its cylinder 
chamber. In its lowest position the carriage 32 operates a sensing element 
(not shown) which switches the valve W5 into position "1". As a result the 
valve Db4 is simultaneously blocked and the outflow out of the hydraulic 
cylinder 151 is regulated by a valve 155 which is activated mechanically 
by the support device for the contact roller 39. With the valve W5 in 
position "1", the two cylinders 34 and 35 are supplied with compressed 
air. However the carriage 32 remains stationary because the return from 
the hydraulic cylinder 151 through the valve 155 is closed by the support 
device 41, 42. The lowest position of the carriage is defined so that the 
contact roller 39 can apply the required pressure to the package or the 
bobbin tube, the support device being in the initial working position. The 
bobbin diameter increases during the winding process and as a result the 
support device is deflected upwards out of its initial working position by 
the contact roller 39. In this process the pressure does not change 
because the force generated by the force storage units 27 is independent 
of distance. The valve 155 is opened by the upward deflection of the 
support device whereby the return flow path from the hydraulic cylinder 
151 is opened and the carriage 32 moves upwards. The support device is 
brought back into its working position, the valve 155 closes and the 
carriage 32 comes to a standstill. This sequence takes place according to 
the control distance adjusted for the support device and the bobbin 
diameter present at each moment, in a more or less continuous fashion. 
When the bobbin is fully wound, the valve Db3 is opened by the bobbin or by 
the carriage position (broken line) as a result of which the return flow 
path of the oil from the hydraulic cylinder 151 to the reservoir 153 is 
opened. Since the full pump pressure is always present at the pneumatic 
cylinders 34 and 35, the carriage 2 moves into its uppermost position. In 
the uppermost position, the valve W5 is switched into the "0" position and 
for example the time relay for the control of the downward movement is 
tripped. At the same time as the valve W5 is switched, the valve Db3 is 
closed. The full bobbin can be removed from the chuck shaft and exchanged 
for an empty bobbin tube. The above described work operation cycle then 
begins again.