EP1446346A1 - Spooling device - Google Patents

Abstract

A system for winding a cross-wound bobbin has a rotatably supported tube holder that is intended to receive a tube. The yarn guide element that serves the purpose of shogging the yarn moves in the direction parallel to the axis of rotation of the tube and is made to execute the oscillating reciprocating motion with the aid of a work cylinder. The work cylinder has the advantage that for braking the kinetic energy at the turning point of the yarn guide element, no additional external energy must be applied. It suffices for the applicable cylindrical chamber to be blocked off. Moreover, the gas compressed in the process can be used to accelerate the piston in the opposite direction. The stored braking energy also can be used simultaneously as acceleration energy. Since in the creation of a cross-wound bobbin many thousand such changes of direction occur, the energy savings are substantial.

Description

Spulvorrichtuncr

In the production of yarn, the thread that is created during ring spinning is first wound up as a bobbin. These are small bobbins with a relatively small amount of thread. The cops are not suitable for delivering the thread directly to a thread-consuming machine, for example a weaving machine. To do this, the thread must first be rewound into a cross-wound bobbin from which the thread can be pulled off overhead. Overhead take-off is necessary because only it guarantees a high thread take-off speed with short start-stop times.

From DE 121 963 a winding device is known which is suitable for producing cross-wound bobbins. For this purpose, the device has a rotatably mounted sleeve carrier, on which the sleeves are placed, on which the cross wrap is produced. A roller is used to drive the sleeve or the cross wrap formed on it or roller is provided, which is aligned axially parallel to the axis of rotation of the sleeve carrier. It becomes frictional: • held against the outside of the cross wrap formed. In order to be able to change the incoming thread, a thread guide element is provided which can be moved parallel to the axis of rotation of the sleeve. It sits on a rope that runs around three rollers. One of the rollers is driven while the thread guide element is moved back and forth between the other two rollers. The drive motor is controlled so that the desired cross wrap is generated by means of a microprocessor control, which detects the speed of the tube carrier with a sensor.

Appropriate control of the motor and thus the traversing stroke is intended to avoid a high edge build-up at the front ends. The arrangement is also intended to prevent image windings. In the case of image windings, the threads in the next but one winding would lie directly one above the other with the same winding direction.

However, it has been shown that the known arrangement shows a considerable energy requirement. At the end of the traverse stroke, the motor has to be braked and accelerated in the opposite direction of rotation, which causes an increased power requirement.

Proceeding from this, it is an object of the invention to provide a winding device which, with at least the same flexibility, has a lower energy requirement for the reversal process.

In the winding device according to the invention is a provided sleeve carrier rotatably about an axis of rotation. A thread guide element, which is driven with the aid of a working cylinder, moves parallel to the axis of rotation of the core carrier. A fluid supply device is assigned to the working cylinder and is controlled via a control device. With the help of the fluid supply device, the two cylinder chambers of the working cylinder are optionally supplied with pressurized fluid, so that the piston moves in the corresponding direction and takes the thread guiding element with it. The speed at which the piston moves essentially depends on the inflow speed of the fluid.

The piston is braked practically without energy by closing the ventilation opening of the cylinder chamber, the volume of which decreases during the traversing stroke.

With the help of the new arrangement, high traversing speeds can be achieved. In particular, it is possible to achieve a reversal of the movement of the thread guide element at the ends of the cross wrap very quickly, that is to say on a very short path.

In addition, the arrangement is very flexible, in the sense that different traversing speeds can easily be set for the back and forth during the traversing stroke. The required image disturbances in the cross wrap can also be generated, as can the axial displacement (jitter) of the reversal point, in order to avoid the edge build-up. With the help of at least one sensor, which works at least as a digital position sensor, the control unit learns ^"" that the thread guide element is at the position of the sensor. From the successive position measurements and the knowledge available in the control system about the oscillating stroke components in between, the control system is able to control the fluid flow to the respective cylinder chamber in the above sense.

The current traversing stroke is ended at the correct point and the next traversing stroke is started in the opposite direction by appropriately switching the fluid supply to the respective cylinder chamber.

In order to set the sleeve or the cross wrap formed in each case in rotation, two types of drive devices are possible. In the one drive device, a roller-shaped drive roller is provided, which is held in the system in a frictionally locking manner by appropriate measures on the outer and outer surface of the cross wrap formed in each case. This drive roller is driven by a motor. The motor expediently works at a constant speed. However, a variable speed is also conceivable.

The other possibility for driving provides a motor that is directly coupled to the sleeve carrier in a rotationally fixed manner. In this case, the motor must have a variable speed if a constant peripheral speed and thus a constant winding speed are to be achieved.

Frequency-controlled AC motors come as the motor or stepper motors with which a desired speed can be set very precisely without - additional control loops for speed stabilization.

If the sleeve carrier is driven directly, that is to say even without a drive roller resting against the winding, it is readily possible to produce both cylindrical and frustoconical cross-wound bobbins. To do this, it is sufficient to carry out a more or less shortened traverse stroke in layers.

Both working cylinders with piston rods and piston rodless working cylinders are suitable as working cylinders. The arrangement with piston rods shows the fundamentally somewhat simpler structure and also the disadvantage that the piston has different effective surfaces depending on the direction of movement. The effective piston area is smaller on the side with the piston rod than on the opposite side, so that different forces occur with the same fluid pressure. In addition, the mass to be accelerated and braked is larger in accordance with the mass of the piston rod. But the sealing is much easier.

With the rodless working cylinder, on the other hand, the effective piston areas are the same on both sides, which means that the braking and acceleration behavior of the piston is the same regardless of the direction of movement at a given fluid pressure. But sealing is a little more problematic. In particular, if compressed air is used as the fluid, a certain leakage can be accepted if the friction on seals can thereby be avoided. The fluid supply device comprises a multi-way valve for each cylinder chamber, which has a connection for connection to the respective cylinder chamber, a connection serving for ventilation and a connection which can be connected to a fluid pressure source. The valve has moved as close as possible to the respective cylinder chamber in order to avoid dead spaces. The avoidance of dead spaces leads to better control and regulating behavior and also significantly reduces air consumption.

The multi-way valves are magnetically controlled multi-way valves which are acted upon directly by the control device.

Instead of using only one position sensor, it is also possible to set a speed sensor which additionally allows the speed to be measured. Because of its position, the controller thus receives information about the current position of the piston or the thread guide element as well as about its speed.

It is also possible to use two or more sensors for the position and / or the speed. Of course, the sensors are arranged within the stroke that the thread guide element performs in the smallest constructively provided stroke.

For the rest, further training is the subject of subclaims. Such combinations of features to which no express exemplary embodiment is directed are also to be regarded as protected. Exemplary embodiments of the subject matter of the invention are shown in the drawing. Show it:

1 shows a first embodiment of the device according to the invention with direct drive of the coil carrier, in a simplified perspective schematic representation,

2 shows an exemplary embodiment of the device according to the invention with a drive via a friction roller, in a simplified perspective illustration,

Fig. 3 shows an embodiment of the device according to the invention with a working cylinder with piston rod, in a simplified perspective view, and

Fig. 4 shows an embodiment of the invention

Device with a working cylinder with rope, in a simplified perspective view.

Fig. 1 shows in schematic form the essential components of a new device for winding a cross winding bobbin 1; Components that are usually present but are not essential for understanding the invention are omitted. The device includes a sleeve carrier 2, which is rotatably mounted with respect to an axis of rotation 3, a drive device 4 for the sleeve carrier 2, a thread guiding element 5, a working cylinder 6 for moving the thread guiding element 5, a fluid supply device 7 for the working cylinder 6 and one Control device 8, which cooperates with sensors 9 and 10.

The sleeve carrier 2 consists essentially of a shaft which is rotatably mounted between two bearing flanges 11 and 12. At least at one end, the sleeve carrier 2 can be detached from one of the bearing flanges 11, 12 in order to be able to axially attach a cylindrical coil sleeve 13. By means of devices, not shown, which are located on / inside the sleeve carrier 2, the coil sleeve 13 can be fixed in a frictionally locking manner on the outer circumferential surface of the sleeve carrier 2. The sleeve 13 serves as a carrier for a cross winding 14 of the cross winding spool 1 with two end faces 15 to be built thereon.

For example, at the end rotatable in the flange 12, but otherwise rigidly connected, sits on the sleeve carrier 2 in a rotationally fixed manner a pulley 16, over which an endless belt 17 runs, by means of which the sleeve carrier 2 is coupled in terms of drive to a pulley 18. The pulley 18 is seated in a rotationally fixed manner on a motor shaft 19 of the drive motor 4. The drive motor 4 is a motor which can be controlled in terms of speed, for example a stepper motor or a frequency-controlled AC motor. For reasons of service life, it is preferably a motor that is brushless.

The drive motor 4 is regulated in such a way that the sleeve carrier 2 rotates at an angular speed which leads to an essentially constant circumferential speed of the cross winding 14 formed in each case. Accordingly, the angular velocity is higher when the outer diameter of the cross wrap 14 is small, and decreases as the diameter increases. eater of the cross wrap 14 to a minimum value with the cross wrap 14 full.

The thread guide element 5, shown in this case as a simple fork, can be moved back and forth essentially parallel to the axis of rotation 3 in front of the cross wrap 14 or the sleeve 13. The working cylinder 6 is used for this purpose. The working cylinder 6 is designed as a rodless working cylinder. Its structure is generally known, so a simplified explanation suffices.

It has an elongated cuboid housing 21 in which a cylinder bore 22 is contained. A piston 23 moves within the cylinder bore 22 and divides the cylinder bore 22 into two cylinder chambers 24 and 25.

As is customary in the case of rodless working cylinders 6, the cylinder bore 22 opens to one side in an outside slot 26 which is closed on the inside by a sealing tape 27 and on the outside by a protective tape 28.

The piston 23 is composed of a center piece 29 and two end-side disk-shaped end pieces 31 and 32, which are circular-cylindrical and have a diameter corresponding to the diameter of the cylinder bore 22. The end pieces 31, 32 seal with little leakage against the wall of the cylinder bore 22 or the sealing strip 27 in the region of the slot 26. Smaller leaks are harmless. In the interest of the lowest possible energy consumption, the piston 23 should move as smoothly as possible in the cylinder bore 22 be, which is why it is advisable to dispense with seals on the end pieces.

The end pieces 31, 32 are spaced apart from one another in such a way that the sealing tape 27 can be pulled downward from the slot 26 in the region of the middle piece 29. In this area, it runs through a slot-like opening in an extension 33 which projects through the slot 26 to the outside.

On the extension 33 sits on the top of the working cylinder 6, a slider 34, on which the thread guide element 5 is fastened. There is a similar groove in the slider 34 in order to lift off the protective tape 28 so that the extension 33 can be guided to the outside through the gap between the raised sealing tape 27 and the raised protective tape 28. In this way, the piston 23 and the slider 32 are mechanically connected to one another.

Instead of the mechanical connection shown between the thread guide element 5 and the piston 23 via the extension 33, a magnetic coupling can also be used. In this case, the cylinder does not require a lateral slot 26 and the seals required for this.

At each end of the cylinder housing 21, a multi-way valve 35 or 36 is flanged, which belongs to the fluid supply device 7. The two multi-way valves 35, 36 are provided with a schematically indicated electric drive 37 or 38, via which an associated valve spindle 38 can be moved in a valve chamber. With the help of the directional control valve 35, the cylinder chamber 25 optionally connected to a vent opening 41 or a fluid supply opening 42. In a central position of the valve spindle 39, the cylinder chamber 25 is hermetically sealed, so that no fluid can escape from the cylinder chamber 25.

The construction of such multi-way valves with a spindle is known and therefore need not be explained in more detail here.

The directional control valve 36 has a corresponding structure. It is provided with an outlet opening 43 and an inlet opening 44. The inlet openings 42 and 44 are connected via lines 45 and 46 to a source 47 for pressurized fluid, for example compressed air.

Furthermore, the two sensors 9 and 10, which serve to detect the position of the piston 23 or the passage of the end pieces 31 and / or 32, are seated in the cylinder housing 21 in corresponding bores 48 and 49 leading from the underside.

The entire device is controlled by the electronic control device 8, which is based, for example, on a microcontroller.

It receives signals from an input keyboard 51, as well as the signals from the sensors 9 and 10 connected via lines 52 and 53. Via lines 54 and 55, the central control device 8 is connected to the electric drives 37 and 38 of the directional control valves 35 and 36, and it is also connected to the drive motor 4 via a line 56 in order to control its speed. The device described so far works as follows:

After the flange 12 has been pivoted away, the previously wound full cross-wound bobbin 1 is withdrawn from the sleeve carrier 2. Then a new empty sleeve 13 is pushed onto the sleeve carrier 2 and fastened there in a frictional manner by means of securing devices (not shown). Now a thread 57 coming from a thread supply (not shown further) is passed through the thread guide element 5 and fastened to the sleeve 13 in a suitable manner. The thread 57 comes from a known, not shown spinning station or a package.

After the device has been prepared so far, the user gives the start command via the control panel 51, whereupon the central control 8 initiates two things at the same time: it switches on the motor 4 at a speed which produces the required peripheral speed with the smallest winding diameter. In addition, it begins to alternately control the directional control valves 35 and 36 so that the piston 23 performs an oscillating movement in front of the sleeve 14 side. The control by the control device 8 takes place in such a way that the speed of the piston 23 and thus of the thread guiding element 5 between the two end faces 15 of the cross-winding 14 is essentially constant.

The ratio between the circumferential speed of the cross winder 14 and the linear speed of the thread guide element 5 defines the pitch angle which the thread winding forms on the outer circumferential surface of the cross winder 14. If it is assumed that the thread 57 is to be continuously deposited from the left end face 15 to the right end face 15, the control 8 brings the directional control valve 36 into a position in which the right cylinder chamber 24 is connected in terms of flow to the vent opening 43. At the same time, the control device 8 holds the directional control valve 35 in a position in which there is a flow connection between the cylinder chamber 25 and the fluid source 47. As a result, the fluid or the compressed air can flow under pressure into the cylinder chamber 25 and move the piston 23 to the right.

Just before the thread guide 5 reaches a position at which the yarn arrives at the right end face 15 57, the controller 8 switches the directional control valve 35 in a position in which the cylinder comber fluidly communicates with ^• the vent opening 41 in connection 25th As a result, the driving force for the piston 23 is switched off immediately. The kinetic kinetic energy still present and the residual pressure in the cylinder chamber 25 would cause the piston 23 to move a considerable distance, based on the figure, to the right.

In order to make the braking distance as short as possible, the control device 8 simultaneously ensures that the directional valve 36 moves from the ventilation position into the shut-off position, in which the cylinder chamber 22 is not connected in terms of flow neither to the ventilation opening 43 nor to the ventilation opening 44. Since this situation occurs shortly before the right end piece 32 reaches the right end of the cylinder chamber 24 and the directional valves are flanged on, the gas cushion trapped therein is very small. A short movement of the piston 23 becomes too lead to a considerable increase in pressure, which in connection with the vented cylinder chamber 25 brakes the piston 23 relatively abruptly. The air compressed in the right cylinder chamber 24 will, after the piston 23 has stopped, start to move the piston 23 in the opposite direction. As soon as the pressure in the cylinder chamber 24 has fallen below the pressure of the fluid source 47, the control device 8 controls the directional control valve 36 into the ventilation position. In this position, the fluid source 47 is connected to the right cylinder chamber 24 via the line 45 and the inlet opening 44. The piston 23 will now move from the right to the left and correspondingly lay the thread 57 in a helix which runs from the right end 15 to the left end 15.

This valve position is maintained until the piston 25 has moved the thread guide element 5 in the immediate vicinity of the left end face 15. The control device 8 will transfer the directional valve 36 from the ventilation position to the ventilation position, at the same time the directional valve 35 into the shut-off position. This repeats at the left end for the Zylinderka mer 25 the process as described above in connection with the cylinder chamber 24 when the piston 23 reaches the right end.

As can be seen from the illustration, the new device for braking the kinetic energy of the piston 23, which is required to drive the thread guide element 5, does not require any additional energy. Braking is done simply by compressing the air in the cylinder chamber concerned. The compressed air can also be used as an energy store to accelerate the piston in the opposite direction. In any case, the braking energy used for gas compression during braking can be recovered during acceleration.

The least energy-efficient braking of the kinetic energy is considerable when producing cross-wound bobbins, since a braking and acceleration process occurs per layer of the cross-wound bobbin and a cross-wound bobbin has several tens of thousands of layers.

The speed at which the piston 23 moves in the constant speed range can be adjusted by regulating the pressure source 47 or the inflow speed of the fluid into the cylinder chambers 24 and 25, for example by additional flow valves (not shown) or proportionally adjusting the directional valves on the inlet side. This makes it possible to determine within wide limits the angle that the turns on the cross wrap 15 have. It is readily possible to produce different angles, for example by making the angle at which the thread 57 is deposited smaller when the thread is wound from the left end face 15 to the right end face 15 compared to the opposite winding direction.

Instead of regulation on the inlet side, regulation on the outlet side by way of the directional valves or additional proportional valves can also be used.

Slight variations in the stroke that the thread guiding element 5 performs can cause so-called image disturbances and also a scattering of the reversal points (edge displacement) on the two end faces 15. The image disturbances prevent the thread from being placed exactly congruent to the next but one turn below in each turn after the next. Such congruent winding would reduce the amount of thread to be applied with the same winding diameter. The jitter in the area of the ends 58 and 59 prevents the reversal points from being congruent with one another, which would lead to a high edge build-up.

The pitch angle can also be influenced by adjusting the speed of the motor 4.

The "approaching" of the thread guide element 5 to the relevant end face 15 is detected with the aid of the two sensors 9 and 10, which measure the passage of the adjacent end piece 31 or 32. The distance between the two sensors 9 and 10 is expediently chosen such that it is smaller than the smallest path traveled by the thread guide element 5 during operation parallel to the axis of rotation 3.

Due to the geometric relationships between the sensors 9 and 10 and the two end pieces 31 and 32, the control device 8 can measure the speed at which the piston 23 has passed since the last passage, for example, past the sensor 9 until the sensor 10 first passes through the end piece 32 moved from left to right. From this speed of movement in conjunction with the position of the sensor 10, the controller 8 can estimate how long it will take until the piston 23 has transported the thread 57 to the right front end 15 and the above-described reversal of the valves 35 and 36 must take place , For the opposite direction according to the same.

Incidentally, the controller 8 knows, due to the running time of the arrangement in connection with the thread thickness entered, for example, via the keyboard 51 and the pitch angles entered via the keyboard, the diameter of the cross winder 14 that has arisen since the beginning of the winding and can accordingly drive the motor 4 without sensors for the winding diameter readjust and / or influence the speed of movement of the piston 23.

Figure 2 shows an embodiment which differs from the embodiment of Figure 1 in the manner in which the sleeve 13 is rotated. While in the embodiment according to FIG. 1 the sleeve carrier 2 is driven directly by the motor 4, according to the embodiment according to FIG. 2 a friction roller 65 is provided, which is rotatably mounted axially parallel to the axis of rotation 3. The elements for storing the friction roller 35 are not shown in detail and are sufficiently known from the prior art.

The friction roller 65 is driven directly by the motor 4. With the help of the bearing device, not shown, it is ensured that the friction roller 65, the length of which corresponds to the greatest axial length of the cross wrap 14, is held in a frictionally engaged manner on the outer peripheral surface formed in each case. In this way, a constant peripheral speed is inevitably generated when the motor 4 drives the friction roller 65 at a constant speed.

Figure 3 finally shows an embodiment of the Invention in which, instead of the rodless working cylinder 6 shown in FIGS. 1 and 2, a working cylinder 6 with a piston rod 66 is used. Otherwise, the mode of operation is as explained above with reference to FIG. 1, only the different effective diameters of the piston having to be taken into account.

FIG. 4 shows an embodiment of the device according to the invention, in which the working cylinder 6 does not require a piston rod. The connection between the piston 23 and the slider 34 is made by a flexible link in the form of a rope 68. The slider 34 runs freely displaceably on the smooth upper side of the working cylinder 6.

The cable 68 is fastened to the end face of the slider 34 facing the viewer and runs from there in the direction of the left end face of the working cylinder 6. On the outside of the working cylinder 6, a deflection roller 71 is rotatably mounted on the end face by a bearing block 69. The rope 68 runs around this deflection roller 71. Below the deflection roller 71, the cable leads through a bore 72 into the cylinder chamber 25, within which it is connected to the end piece 31. The rope 68 extends coaxially within the cylinder chamber 25 and runs parallel at the top to the flat top of the working cylinder 6.

Another section of the cable 68 leads from the end face of the slider 34 facing away from the viewer in the direction of the right end end of the working cylinder 6. Here, with the aid of a further bearing block 73, a deflecting roller 74 is also rotatably mounted loosely. To the

-lϊ Deflection pulley 74 guides the relevant section of the cable 68 around and on the underside of the deflection pulley 74 through an unrecognizable bore into the cylinder chamber 24.

The rope 68 is held taut by spring members, not shown.

When the piston 23 moves to the left, the slider 34 moves with the thread guide 5 on the upper side of the working cylinder 6 into the right end position, and vice versa. The movement of the slider 34 is forcibly coupled to the movement of the piston 23 but in opposite phase.

The arrangement shown works dynamically in the sense that the piston 23 itself is constantly in motion during the winding process. There is therefore no imperative to hermetically seal the cylinder chambers 24 and 25 from the outside atmosphere. Accordingly, it is sufficient if the cable 68, which consists, for example, of a monofilament, passes through the bore 72 without a special seal, or the corresponding bore at the other end of the working cylinder 6. A leak-free seal is not necessary. It is sufficient if the rope 68, together with the bore, produces a throttling with a sufficient throttling effect.

In the interest of the lowest possible energy consumption of the arrangement, on the other hand, it is important to keep the friction of the overall system as small as possible and, in addition, there would be the risk that a seal due to enormous number of movements would soon be damaged by the rope 68 anyway.

The advantage of the arrangement according to FIG. 5 is the same as that of the arrangement according to FIGS. 1 and 2. The mass of the moving parts is kept very small, which reduces the energy expenditure for braking and accelerating. Another advantage of the arrangement according to FIG. 4 is the avoidance of complicated sealing tapes on the working cylinder 6. The structural design is significantly simpler.

Measures as to how the rope 68 can be kept taut are sufficiently known to the person skilled in the art and need not be explained in more detail here.

Instead of a cable for coupling the slider 34 to the piston 23, a thin band, for example a steel band, can also be used, as is illustrated in broken lines at 75. The advantage of the tape compared to the rope is the reduced thickness with the same area, so that the bending forces are kept small when deflected via the rollers 71 and 74. Under certain circumstances, the service life increases significantly.

A device for winding a cross-wound bobbin has a rotatably mounted sleeve carrier which is provided for receiving a sleeve. The thread guide element, which is used for traversing, moves in the direction parallel to the axis of rotation of the sleeve and is brought into the oscillating reciprocating motion with the aid of a working cylinder. The working cylinder has the advantage that to brake the kinetic energy at the reversal point of the no additional external energy has to be applied. It is sufficient if the relevant cylinder chamber is shut off. In addition, the compressed gas can be used to accelerate the piston in the opposite direction. The stored braking energy can also be used as acceleration energy. Since many thousands of such changes of direction occur when a cross-wound bobbin is produced, the energy saving is significant.

Claims

Claims: 1. Device for winding cross-wound bobbins (1), the cross-wound bobbins (14) of which have two end faces (15), it with a sleeve carrier (2) rotatably mounted about an axis of rotation (3), onto which a sleeve (13) for a cross winding bobbin (1) can be detachably attached, with a drive device (4) which is set up to hold the sleeve (13) in To make revolutions in order to wind a thread (57) onto the sleeve (13), with a thread guide element (5) which is guided to move back and forth essentially in the longitudinal direction of the cross-winding (14), around the thread (57) to oscillate during winding in the sense of producing a cross wrap (14) with a working cylinder (6), the cylinder space (22) of which is divided by a piston (23) into a first and a second cylinder chamber (24, 25), wherein the piston (23) is coupled to the thread guide element (5) in order to move the thread guide element (5) back and forth in the sense of traversing, with a controlled fluid supply device (7) which is connected to the cylinder chambers (24, 25) to at least one of the cylinder chamber n (24, 25) alternately supplying or venting with pressurized fluid in such a way that the piston (23) executes the required longitudinal movement, and with a control device (8) for controlling the fluid supply device (7) such that it brings the piston (23) into the required movement coordinated with the rotation of the sleeve (13) or of the cross wrap (14). 2. Device according to claim 1, characterized in that the sleeve (13) is formed by a cylindrical or conical sleeve. 3. Device according to claim 1, characterized in that the drive device (4) has a rotatably mounted drive roller (65) which is frictionally held in contact on the outer circumference of the cross winding bobbin formed in each case and which is driven by a motor (4) is. 4. The device according to claim 3, characterized in that the motor (4) runs at constant speed. 5. The device according to claim 1, characterized in that the drive device (4) comprises an adjustable in speed electric motor (4) which is coupled directly to the sleeve carrier (13). 6. The device according to claim 5, characterized in that the motor (4) is controlled via the control device (8) such that the peripheral speed of the cross winder (14) formed in each case is essentially independent of the winding diameter. 7. The device according to claim 1, characterized in that the drive motor (4) is a frequency-controlled AC motor or a stepper motor. 8. The device according to claim 1, characterized in that the working cylinder (6) has a piston rod (66) and that the thread guide element (5) is fixed to the free end of the piston rod (66). 9. The device according to claim 1, characterized in that the working cylinder (6) is rodless. 10. The device according to claim 9, characterized in that the thread guide element (5) is mechanically coupled directly to the piston (23). 11. The device according to claim 9, characterized in that the thread guide element (5) is magnetically coupled directly to the piston (23). 12. The apparatus according to claim 9, characterized in that the thread guide element (5) with the piston (23) via a rope (68) or a band (75) is coupled. 13. The device according to claims 8 or 9, characterized in that the fluid supply device (7) per cylinder chamber (24, 25) includes at least one multi-way valve (36, 37) which has a connection connected to the cylinder chamber (24, 25), has a connection (43, 44) connected to a fluid pressure source and a vent connection (41, 42). 14. The apparatus according to claim 13, characterized in that the multi-way valve (35,36) is an electrically controlled multi-way valve. 15. The apparatus according to claim 13, characterized in that at least one sensor (9, 10) is provided which is set up to at least indirectly detect at least one position of the thread guide element (5) and which is connected to the control device (8). 16. The apparatus according to claim 13, characterized in that the sensor (9,10) is a speed sensor. 17. The apparatus according to claim 13, characterized in that at least two sensors (9,10) are provided, which are located within a distance, the ends of which are defined by the front ends (15) of the cross wrap (14) formed. 18. The apparatus according to claim 13, characterized in that the sensor (9,10) cooperates with the piston (23) of the working cylinder (6). 19. The apparatus according to claim 1, characterized in that a sensor is provided to detect the diameter of the cross wrap (14) at at least one point. 20. The apparatus according to claim 13, characterized in that the control device (8) controls the working cylinder (6) in such a way that image windings and / or a high edge build-up at the front ends (15) of the cheese (1) are avoided.