EP0374536B1 - Winding apparatus - Google Patents

Description

The invention relates to a winding machine according to the preamble of claim 1, and a method for operating a winding machine.

This winding machine is known from European patent application 0 161 618 A1. During the winding cycle, the winding turret is stationary with the exception of two short times in which the winding spindle which is in operation is first brought into contact with a first and then in contact with a second contact roller. The contact rollers, on the other hand, are mounted on a movable carrier, so that they can execute a lifting movement with radial component to the winding spindle corresponding to the increasing bobbin diameter, since the winding turret is not rotated during the actual winding travel.

Another winding machine, in which the relative movement between the contact roller and the winding spindle is carried out in accordance with the growing bobbin diameter by rotating the bobbin turret, is known from EP-B1 1359 and US Pat. Nos. 4,298,171 and EP-B1 15410.

At this Known winding machine, the contact roller is firmly mounted in the machine frame. The winding spindles are mounted in rockers which are pivotally mounted on the turret, so that the winding spindles can assume an outer and an inner radial position relative to the turret. At the beginning of the winding process (winding travel), the relative movement between the winding spindle and the contact roller is effected when the bobbin turret is stationary by swinging out the rocker. Then the rocker is determined relative to the reel turret and the relative movement between the reel spindle and the contact roller is effected by rotating the reel turret.
For this purpose, a torque is exerted on the turret by means of pneumatic or hydraulic cylinders. This torque is counteracted by the torque of the force exerted by the fixed contact roller on the spool or the spool spindle. The increase in this force as the coil diameter increases causes the turret to rotate.

In the winding machine, there are inconsistent changes in the radial force (contact pressure) between the contact roller and the bobbin to be formed. This is based on the fact that the contact pressure is applied by the same control devices which also control the relative movement between the contact roller and the operating reel spindle. Therefore, the stick-slip effects, which are inevitable when the turret is rotating slowly, act as fluctuations and, in particular, inconsistent fluctuations in the contact pressure.

A winding machine is known from US Pat. No. 4,106,710 (Bag. 943), in which the bobbin turret stands still during the bobbin travel and the bobbin spindle in operation thus remains stationary. The contact roller is mounted on a carriage which is movable essentially radially to this winding spindle. The contact roller can therefore move relative to the carriage. Depending on this movement, pneumatic cylinder-piston units are controlled, which serve to compensate for the weight of the slide. The contact roller is therefore not with the weight of all components of the carriage on the spool, but only with a reduced force. As the coil diameter increases, the coil must therefore exert the force required to move the carriage, which corresponds to the reduced force mentioned.

From DE-OS 25 44 773 (Bag. 961) a winding machine is known in which a winding spindle is mounted in a movable carriage. The contact roller is mounted in a likewise movable carrier. The carriage of the winding spindle is held by pneumatic cylinders which are pressurized depending on the movement of the carrier of the contact roller. This compensates for the weight of the slide with the winding spindle and bobbin. As the coil diameter increases, the Cylinders exerted pressure force reduced so that the carriage sinks due to its own weight. Stick-slip effects are also inevitable. This winding machine is not suitable for lossless winding on two alternating winding spindles, since for this purpose it would also have to contain a rotatable turret on which the two winding spindles are mounted.

The invention has for its object to provide a winding machine in which the radial contact force between the contact roller and the bobbin changes continuously and only slightly in the course of the winding cycle and which is simple and compact.

The solution results from the characterizing part of claim 1.

It should be emphasized that the position of the contact roller remains essentially unchanged in the course of the winding travel, even as the bobbin diameter increases. This means that the contact roller only makes slight movements radially to the operating spindle in the range of a few millimeters, preferably less than 1 mm. The required relative movement, with which the distance between the axis of the contact roller and the axis of the operating reel spindle is adapted to the growing reel diameter, is carried out by rotating the reel turret during the winding travel. The rotation is effected by a motor. The motor is controlled by a sensor which detects the movement of the contact roller, ie in particular the path which the carrier of the contact roller takes. As a result, the motor of the bobbin turret is controlled so that the turret rotates so far, even with very small movements of the contact roller, that the bobbin spindle dodges with the increasing bobbin diameter of the contact roller, while the contact roller barely leaves its starting position and immediately reaches it again.

The actuation of the motor assigned to the coil turret (rotary drive) thus takes place as a function of the output signal of the sensor, which detects the deviation between the actual value and the target value of the position of the contact roller. The rotary actuator can be actuated step by step. For this purpose, the rotary control device is given a specific maximum value of the deviation between the actual value and the setpoint value of the position of the contact roller, e.g. programmed. As long as the deviation is smaller than this predetermined maximum value of the deviation, the rotary drive is braked so that the coil turret cannot change its rotational position. If the actual deviation between the setpoint and the actual value of the position of the contact roller exceeds the specified maximum value, the brake is released and the reel turret is rotated at a specified speed until the deviation between the setpoint and actual value is again below the specified maximum value of the deviation.

In another procedure, the rotary drive is actuated by the rotary control device and the sensor in such a way that the rotary drive is constantly in operation and the turret rotates continuously in such a way that the deviation between the desired value and the actual value of the position of the contact roller is corrected to a certain, low value becomes.

The contact roller and its carrier as well as the operating reel spindle and the reel turret with the rotary drive thus form, together with the rotary control device and the sensor, a control circuit by means of which the position of the contact roller is kept essentially unchanged.

In contrast to all known winding machines in the winding machine according to this invention, the center distance between the contact roller and the operating winding spindle is not dependent on that between the contact roller and the Operating spool spindle prevailing contact pressure, but determined by a rotary drive, which drives the spool turret positively in the sense of increasing the center distance.

Stick-slip phenomena do not occur when the turret is rotated because the turret is positive, i.e. is forcibly driven. The level of the contact pressure is determined solely by the force acting on the contact roller. The winding spindles are immovably mounted on and relative to the reel turret, which, in contrast to the winding machine mentioned at the beginning, results in a much more stable structure and a constant course of the contact pressure.

The winding machine according to this invention is preferably used for winding freshly spun man-made fibers in spinning plants. In the design of the winding machine according to claim 2, the bobbin turret rotates in the same direction of rotation as the operating spindle and so-called synchronous catching is made possible. For this, reference is made to EP-A 0 286 893 (EP-1575) and US patent (still pending).

In the embodiment according to claim 3 it follows that the contact force initially increases. It is therefore wound at the beginning of the winding cycle with a low contact pressure, thereby preventing damage to the first layers of thread. Furthermore, the change in contact pressure can be kept small. For this purpose, the guidance of the contact roller as well as the pivot point of the coil turret and the turning circle of the coil turret on which the spindle axes lie (spindle turning circle), as well as the radius of the contact roller relative to each other are designed in such a way that the change in the contact pressure of the contact roller on the desired maximum diameter ratio The bobbin remains within the desired limits during the winding cycle. The quotient is here as the diameter ratio:
Understand the diameter of the winding spindle at the start of the winding cycle (empty tube) / the diameter of the winding spindle at the end of the winding cycle (full package). This operating diameter ratio is at least 1: 3 in modern winding machines. The permitted change in the radial contact pressure is in any case less than 50%, the contact pressure starting from a lower value, which means that it may initially increase. The radial force exerted by the contact roller on the bobbin will change in the solution according to claim 4 in the course of the winding cycle by no more than 10%, preferably after the winding of the first layers of thread by no more than 5%.

The winding machine according to this invention is operated in such a way that the bobbin turret is rotated in the same direction of rotation as the operating bobbin spindle as the bobbin diameter increases. The winding spindles are driven by axle drive motors, with each winding spindle being assigned an axle drive motor.

As already stated, according to the invention it is possible to keep the contact pressure between the contact roller and the winding spindle or bobbin constant in the course of the winding cycle within a small range that is not harmful to winding technology.

When winding man-made fibers for which the winding machine is primarily intended, it can be expected that the thread will generally run vertically from top to bottom. Since the contact roller is arranged between the traversing mechanism and the operating reel spindle, both the carrier and the contact roller are loaded by a gravity component. The measures according to claim 4 or 5, the radially acting bearing force between the contact roller and the coil can be adjusted to the dimension permissible in terms of winding technology. The relief device can be, for example, a force transmitter for a constant force, for example a spring or a pneumatic or hydraulic cylinder-piston unit, which is subjected to constant pressure.

In the case of difficult winding tasks, there is also the option of e.g. to control hydraulic or pneumatic relief device according to the desired course of the contact pressure during the winding cycle.

If the contact roller is mounted in such a way that it does not rest on the coil with its gravitational force, but without gravity, a loading device, e.g. a hydraulic or pneumatic cylinder-piston unit is provided, which acts on the support of the contact roller and generates the necessary contact pressure. The loading device can be designed so that it generates a constant contact pressure. However, it is also possible to design the loading device in such a way that the contact pressure is controlled in the course of the winding travel according to a certain programmed course.

The carrier on which the contact roller is mounted is preferably a rocker arm which is pivotally mounted on one side in the machine frame and at the other free end of which the contact roller is seated (claim 7). If the contact roller is to rest on the spool with its own weight, the rocker is arranged horizontally or inclined. If the contact roller is to rest on the spool without the influence of its weight, the rocker must be arranged essentially vertically.

By claim 8 results in a wear-resistant suspension, which also has the advantage that the pivoting movement of the contact roller is subject to an increasing force with the deflection. Therefore, a position that is stable in the course of the winding cycle can be set for the zero position of the contact roller without any technical difficulties.

Incidentally, the suspension in a rubber block also has the advantage that the rubber block not only the pivoting movement within the scope of the slight measuring deflections of the contact roller, but also a movement perpendicular to it, i.e. on the connecting line between the pivot axis and the axis of the contact roller. As a result, the contact roller can align not only in the swivel direction, but also perpendicular to it, parallel to the axis of the winding spindle. It is also particularly important that the rubber block dampens the movement of the contact roller.

The traversing according to this invention can be one of the traversing devices known from the prior art. In this context, particular reference should be made to wing traversing in accordance with EP-D 1114642, reversing thread traversing in accordance with US Pat. No. 3,664,596, grooved roller traversing in accordance with US Pat. No. 3,797,767 or other traversing devices. The traversing device can be fixed in place in the machine frame.

As is known, the thread that wraps around the contact roller is placed on the contact roller with the traversing law of the traversing device, the reversal of stroke depending on the distance between the traversing device and the line of the thread on the contact roller. Any change to this distance is included in the filing law.

The embodiment according to claim 9 and 10 or 11 ensures that, despite the slight movement of the contact roller, the distance between the traversing device and the contact roller does not change in the course of the winding cycle. For this purpose, the traversing device is preferably also mounted on a rocker arm, which is pivotably mounted either coaxially with the rocker arm of the contact roller or on the rocker arm of the contact roller. This makes it possible to remove the traversing device from the contact roller for maintenance to be lifted off, so that on the one hand the contact roller and on the other hand the traversing device is easily accessible. On the other hand, the measure according to claims 9 to 11 prevents the traversing also executing a movement perpendicular to the thread run when it moves relative to the contact roller. This is particularly important if, as suggested by claim 12, a drive device acts on the carrier of the traversing mechanism, by means of which the distance between the contact roller and the traversing mechanism can be changed in the course of the winding cycle. The invention thus also offers the possibility of traveling with a variable traverse stroke during the winding travel. For this purpose, the drive device is controlled according to a predetermined program. Appropriate programming can shorten the stroke in the course of the winding travel, in particular at the beginning of the winding travel (claim 14). For this purpose, reference is made to the coil structure according to US Pat. No. 4,789,112 (Bag. 1540). It is also possible to carry out breathing by appropriate programming (claim 15), as described, for example, in US Pat. No. 4,325,517 (Bag. 1157) and DE-OS 37 23 524 A1 (IP-1536). It is also possible to move the traversing device back and forth axially in a time-recurring manner relative to the contact roller in order to effect a stroke shift.

The invention also solves the problem of changing bobbins. The bobbin should be changed so that the thread is wound without interruption. For this purpose, the bobbin turret is always rotated in the same direction of rotation both during the bobbin travel and when changing the bobbin.

The process of "synchronism catching", in which at the moment of threading the surface of the empty tube and the thread have the same direction of movement, is characterized in that the thread is subject to only slight thread tension fluctuations. The operational reliability of this method is based on these small thread tension fluctuations. Spool sleeves with a thread catch slot are preferably used, as is known in DE-A 39 23 305 (Bag. 1650).

With "synchronous trapping", the bobbin turret rotates in the same direction as the operating bobbin spindle. This means that the idle spindle must move past the contact roller when it is moved into its operating position. This results in a narrowing of the geometric design options. This restriction is also avoided by the configuration according to claim 6. It should be emphasized that the contact roller only has a slight movement of e.g. 10 mm.

A deflecting thread guide is required for synchronous catching, which deflects the thread from the normal plane of the catch slot of the empty tube into a normal plane of the full bobbin (cf. PCT / DE 89/00094). According to claim 17, this deflecting thread guide, designed as a sheet metal, serves, together with a further protective sheet, the purpose of protecting the empty sleeve to be put into operation against the full bobbin, which is still rotating. In particular, it can happen that the torn or cut thread end lifts off the rotating full spool and damages the thread layers forming on the empty tube. Claim 17 creates a complete encapsulation of the full bobbin with respect to the empty tube even before the thread is cut off or torn off.

The method for changing the bobbin on the winding machine results from claim 18 with advantageous developments according to claims 19 to 21. As already mentioned, it is favorable for synchronized catching that the contact roller can carry out a slight evasive movement so as not to impede the empty tube moving into the operating position . The mobility of the contact roller is used, which is used in the context of this invention to control or regulate the rotary drive of the bobbin turret in the course of the bobbin travel as a function of the growing bobbin diameter. However, this function is overridden during the formation of the first thread layers on the empty tube. This ensures that the coil turret can temporarily remain in its position. During this time, the full bobbins can be removed from the bobbin spindle, which has meanwhile moved into their rest position, for which purpose, in particular, an automatic bobbin changer can serve.

The measuring function of the contact roller, by means of which the growing bobbin diameter is detected, can be started again after a certain programmed time has elapsed or after the full bobbins have been exchanged for empty tubes on the bobbin spindle which is at rest by lowering the contact roller and making contact is brought with the operating winding spindle. A special control is dispensed with by the measure according to claim 20. Here, the restart of the measuring function of the contact roller takes place in that, as the coil diameter increases, contact between the coil and the contact roller again results in a measurement deflection of the carrier of the contact roller.

It is preferably provided that the contact roller is driven during the non-contact time, preferably driven at a peripheral speed that essentially corresponds to the target peripheral speed of the coil. A suitable drive for this can be seen from DE-A 38 34 032.

The invention is described below using exemplary embodiments.

Fig. 1

die Seitenansicht einer Aufspulmaschine im Betrieb;

Fig. 2

die Frontansicht der Aufspulmaschine im Betrieb;

Fig. 3A,B,C

die Frontansicht der Aufspulmaschine beim Spulenwechsel;

Fig. 4

die Seitenansicht der Aufspulmaschine nach Fig. 1 beim Spulenwechsel;

Fig. 5

ein weiteres Ausführungsbeispiel einer Spulmaschine mit einer Kehrgewindewellenchangierung;

Fig. 6,7

Ausführungsbeispiele, bei welchen der Abstand zwischen Changiereinrichtung und Kontaktwalze steuerbar ist;

Fig. 8,9

Diagramme für den Verlauf der Anpreßkraft zwischen Kontaktwalze und Spule;

Fig. 10,11

Spulhülsen;

Fig. 12

Aufhängung der Führung der Kontaktwalze (Detail);

Fig. 13

eine Spule, die mit der Aufspulmaschine hergestellt ist;

Fig. 14

Programm zur Veränderung des Abstandes zwischen Changierung und Kontaktwalze;

Fig. 15

Detail der Figuren 1, 4, 5, 6, 7, bei welchen der Revolvermotor als Bremsmotor ausgeführt ist.

Show it:

Fig. 1

the side view of a winding machine in operation;

Fig. 2

the front view of the winding machine in operation;

3A, B, C

the front view of the winding machine when changing the bobbin;

Fig. 4

the side view of the winding machine of Figure 1 when changing the bobbin.

Fig. 5

a further embodiment of a winding machine with a reversible thread shaft maneuvering;

Fig. 6.7

Embodiments in which the distance between traversing device and contact roller is controllable;

Fig. 8.9

Diagrams for the course of the contact pressure between the contact roller and the coil;

Fig. 10.11

Bobbin tubes;

Fig. 12

Suspension of the guide of the contact roller (detail);

Fig. 13

a bobbin made with the winding machine;

Fig. 14

Program for changing the distance between traversing and contact roller;

Fig. 15

Detail of Figures 1, 4, 5, 6, 7, in which the revolver motor is designed as a brake motor.

The winding machines, which are shown in Figures 1 to 4, 5, 6, 7, differ only in details. The following description therefore relates to all exemplary embodiments. Attention is drawn to the different details.

The winding machine shown is the thread 3 supplied by delivery unit 17 without interruption at a constant speed. The thread is first passed through the head thread guide 1, which forms the tip of the traversing triangle. The thread with direction of movement 2 then arrives at the traversing device 4, which will be described later. Behind the traversing device, the thread on the contact roller 11 is deflected at more than 90 ° and then wound on the spool 6. The coil 6 is formed on the winding tube 10.1. The winding tube 10.1 is clamped on the freely rotatable spindle 5.1 (operating spindle). The winding spindle 5.1 with the winding sleeve 10.1 stretched thereon and the coil to be formed thereon is in the beginning of the operating position. At this time there is a second winding spindle (idle spindle) 5.2 with a winding tube (empty tube) 10.2 stretched thereon in the waiting position. Both winding spindles 5.1 and 5.2 are freely rotatably mounted in a rotatable turret 18. In all of the exemplary embodiments, the spindles 5.1 and 5.2 are driven by synchronous motors 29.1 and 29.2. The synchronous motors 29.1 and 29.2 are each fastened in alignment with the spindles on the turret 18. The synchronous motors are supplied by the frequency transmitters 30.1 and 30.2 with three-phase current of a controllable frequency. The frequency transmitters 30.1 and 30.2 are controlled by a control unit 31, which is controlled by a speed sensor 53. The speed sensor 53 senses the speed of the contact roller. The control unit 31 controls the frequency transmitters 30.1 and 30.2 of the respective operating spindle 5.1 so that the speed of the contact roller 11 and thus also the surface speed of the coil remains constant despite the increasing coil diameter.

The synchronous motors 29.1 and 29.2 can be replaced by asynchronous motors. In this case, a control signal is superimposed on the control frequencies F4 and F5, so that the The target value of the spindle speed, which is predefined by the control unit 31, is exactly maintained. A suitable controller results from DE-C 34 25 064 (IP-1348).

The bobbin turret 18 is rotatably mounted in the frame of the winding machine and is pivoted by the drive motor (turret motor 33), so that the spindles 5.1 and 5.2 can be moved alternately into the operating position or waiting position when the bobbin 6 is fully wound on one of the spindles is.

The turret motor 33 also serves to turn the coil turret in the sense that the center distance between the contact roller 11 and the operating spindle 5.1 is increased as the coil diameter increases.

The turret motor 33 can be designed as a brake motor. Such a brake motor has the property that its rotor is fixed immovably, ie can no longer be rotated if the brake motor is not connected to a power source. Such a turret motor 33, which is designed as a brake motor, is shown schematically in FIG. 15. 15 is a detailed drawing of FIGS. 1, 4, 5, 6, 7 and shows the rotary drive and the rotary control device for the turret 18. The shaft 70 of the turret motor 33 and of the turret 18 is acted upon by a brake 71. The brake 71 is actuated by an electromagnet 72. The electromagnet is connected to the rotation control device 54. The rotary control device 54 alternately closes either the rotor circuit of the turret motor 33 or the circuit of the electromagnet 72 of the brake 71 as a function of the output signal from the sensor 52, which senses the movement of the carrier 48 or 63 for the contact roller.

The turret motor 33 can also be a stepper motor which rotates continuously at a very slow speed and which is controlled by the rotary control device in dependence on the output signal of the sensor 52, which senses the movement of the carrier 48 or 63 for the contact roller, in such a way that the center distance between the contact roller 11 and the operating spindle 5.1 increases continuously with the increasing coil diameter.

The contact roller 11 is mounted on a carrier so that the contact roller can move with a radial component to the operating spindle. In the exemplary embodiment according to FIGS. 1 to 4, 6 and 7, the rocker 48 serves as the carrier for the contact roller. The rocker 48 is pivotally mounted in the machine frame about the pivot axis 50. The pivot axis 50 is - as already mentioned - so that the contact roller is movable with a radial component to the operating spindle 5.1. The pivot axis 50 is formed by a rubber block. This rubber block is firmly clamped in the machine frame. The rocker 48 is attached to the rubber block, so that the rocker 48 can be pivoted elastically. An embodiment of such a mounting of the rocker is shown in detail in Fig. 12. The rubber block 42 is a cylindrical body which is introduced into the annular space between the pivot axis 50 and the bearing eye of the rocker 49. The pivot axis 50 is rotatably mounted in the machine frame. The inner circumference of the rubber block is rotatably connected to the pivot axis 50. The outer jacket of the rubber block is rotatably connected to the inner jacket of the bushing of the rocker 49.

In the exemplary embodiment according to FIG. 5, the contact roller is mounted on a carrier 63 which can be moved in a straight line in guides 64.

With the rocker 48 or the carrier 63, the contact roller can move a very small distance, e.g., in front of the growing coil diameter of the operating spindle in the operating position. Dodge 2 mm.

As already explained above, all conceivable traversing devices can be used. In the exemplary embodiment according to FIGS. 1 to 4, the traversing device is a so-called wing traversing. It has two rotors 12 and 13, which are connected to one another by a gear 22 and driven by the motor 14. Wings 8 and 9 are fastened to the rotors 12 and 13, as can be seen in particular from FIGS. 2 and 3. The rotors rotate with different directions of rotation 27, 28 and in doing so guide the thread along a guide ruler 9, one wing taking over the guidance in one direction and then dipping under the guide ruler, while the other wing takes over the guide in the other direction and then dives under the ruler. The traversing motor 14 is driven at a constant speed, but can also be controllable as a function of the signals from a programmer.

In the exemplary embodiment according to FIG. 5, the traversing device is a so-called reverse thread shaft traversing. The reversing thread shaft 23 is rotatably mounted in a housing. In a known manner, the reverse thread shaft has an endlessly going and returning groove on its cylindrical circumference. One end of a traversing thread guide 40 engages in the groove 15. The traversing thread guide is straight in the straight guide 44 of the housing. Further details of the exemplary embodiments relate to the suspension of the traversing device.

Regardless of the type of traversing device, the housing of the traversing device can be fixed in place. This is shown in the exemplary embodiment according to FIG. 5.

When the traversing device is fixed in position, the distance between the contact roller 11 and the traversing thread guide 40 changes, even if the measuring movements of the contact roller are very small and almost negligible.

In the exemplary embodiments according to FIGS. 1 to 4, 6, 7, the traversing device 4 is movably mounted in the machine frame of the winding machine. For this purpose, a rocker 49 is used, at the free end of which the traversing device is fastened and which is pivotally mounted at the other end in such a way that the traversing device makes a movement perpendicular to itself and to the contact roller, i.e. can perform a parallel shift.

In the exemplary embodiments according to FIGS. 1 to 4, the rocker arm is pivoted freely in the machine frame. The pivot axis is arranged essentially coaxially with the pivot axis 50 of the rocker 48.

In the exemplary embodiment according to FIG. 7, the rocker 49 for the traversing device is freely pivotably mounted on the rocker 48.

In the exemplary embodiment according to FIGS. 1 to 4, the rocker 49 for the traversing device with support 51 lies on the rocker 48 for the contact roller 11. The rocker 49 therefore follows the movements of the rocker 48. On the other hand, it can be folded up independently, which is of great advantage for the maintenance of the contact roller and the traversing device. By means of a cylinder-piston unit 21 which is acted upon pneumatically and which acts on the rocker 48 or the carrier 63 from below, the weight which bears on the contact roller and thus as a pressing force on the coil can be compensated for in whole or in part . This is the weight of the traversing device and the contact roller (exemplary embodiments according to FIGS. 1 to 4, 7) or only the contact roller (exemplary embodiments according to FIGS. 5, 6).

In all exemplary embodiments, a sensor 52 is arranged in a stationary manner in the machine frame. This sensor scans the movement of the rocker 48 or in FIG. 5 of the carrier 63, the sensor measuring the distance to the rocker 48 or to the carrier 63, that is to say the path of the rocker 48 or the carrier 63. Depending on the output signal, i.e. e.g. when a predetermined distance is exceeded, the sensor 52 outputs an output signal which is given to a control device 53 for the turret drive 33. The further function will be discussed later.

The mode of operation of the winding machine is the same for all exemplary embodiments. The mode of operation is described below with reference to the exemplary embodiment according to FIGS. 1 to 4.

In Fig. 1 the operation of the winding spindle 5.1 is shown. Only a few layers are wound on the empty sleeve 10.1 and the contact roller 11 is in circumferential contact with the coil to be formed. As the bobbin diameter increases, the contact roller makes a slight radial movement. The distance of this movement is detected by the distance sensor 52. Depending on the output signal of the distance sensor 52, the turret motor 33 is controlled via the control device 54 in such a way that the turret rotates further by a small angle of rotation in the sense that the center distance between the contact roller and the operating spindle 5.1 is increased. The direction of rotation of the operating spindle is marked by arrow 55. Since the thread wraps around the contact roller in a counterclockwise direction, it will wrap around the operating spindle and bobbin in a clockwise direction. As a result, the operating spindle also rotates clockwise. Therefore, the winding turret also rotates clockwise with direction of rotation 56.

The invention provides two alternative methods for controlling the revolver motor:
If the turret motor 33 - as shown in Fig. 15 - is designed as a brake motor, the shaft of the turret motor is initially locked by the brake, so that the reel turret cannot rotate as the spool diameter increases. As a result, the contact roller 11 is pressed out of its desired position into an actual position. A certain permissible maximum value for the deviation between the actual position and the desired position of the contact roller is specified in the control device 54. As soon as it is determined by the distance sensor 52 that the deviation between the desired position and the actual position exceeds the predetermined maximum value, the brake is released by means of the magnet and at the same time the rotor of the turret motor 33 is connected to its current source. As a result, the turret motor is rotated a little further at a slow but constant speed until it is determined by the sensor 52 that the contact roller 11 has essentially returned to its desired position. The maximum permissible deviation between the target position and the actual position of the contact roller is very small and is, for example, 1 mm. Now the turret motor 33 is switched off again and the brake is activated instead. As a result, the shaft of the turret motor 33 and thus also the coil turret is again not rotatably locked.

In the other method, the turret motor 33 is constantly connected to a power source. The very low speed of the turret motor 33 is controlled by means of the distance sensor 52 and the rotary control device 54 so that the contact roller does not leave its desired position or that the deviation between the actual position and the desired position remains constant and as small as possible. In this embodiment, a turret motor 33 is required, the rotational speed of which does not depend on the torque. Therefore, in this turret motor, the contact pressure between the contact roller 11 and the operating spool spindle 5.1 or the coil formed thereon - in the former method does not lead to a rotation of the coil turret - in the latter method does not lead to an increase in the rotational speed of the coil turret.

The end position of the coil is marked with (6) and the end position of the operating spindle with (5.1). The result of this is that the center of the winding spindle has traveled over a part, the so-called operating area, of the spindle turning circle during the winding travel with the rotation of the winding turret. This operating range is marked with the reference symbol 57 in FIG. 1. The greatest change in the radial contact pressure now occurs between the starting position in which the operating spindle 5.1 is brought into contact with the contact roller 11 for the first time and the position in which the spindle axis of the operating spindle 5.1 lies on the tangent 58, which is from the center of the contact roller 11 pulls to the operating range of the spindle turning circle. The angle alpha, which the center of the winding spindle 5.1 has traversed relative to the center of the contact roller 11, should now be as small as possible. In Fig. 1, this angle was shown quite large in order to gain better graphic clarity. In reality, this angle is much smaller, and preferably less than 15 °. The particular advantage of the invention is that even with a small diameter ratio (diameter of the empty tube to diameter of the full spool) of less than 1: 3 and also if the wrap angle of the thread on the contact roller 11 is greater than 90 °, the change in contact pressure can be kept low. A further advantage can be seen in the fact that - as can also be seen in FIG. 1 - with increasing coil diameter, the wrap angle on the contact roller increases and not decreases. A reduction in the wrap angle would result in increased slippage of the thread on the contact roller. Increasing the slip leads to a change in the thread tension, in particular when the contact roller is driven or is driven for the purpose of thread tension relief with a power which is greater than the idle power; see. DE-OS 35 13 796 (= Bag. 1400).

Another advantage is that the contact pressure assumes a relatively low value in the course of the winding travel and in particular at the beginning of the winding travel and increases. This takes into account the fact that the contact pressure when winding the first layers should be relatively low and increase later.

These advantages result in particular from the fact that the position of the contact roller remains unchanged during the winding cycle - apart from changes which are insignificant in terms of winding technology - but the contact pressure is exerted by the mobility of the contact roller and the force acting on it, in contrast to the known winding machine, in which the contact pressure is applied by the torque acting on the bobbin turret and is therefore largely dependent on the relative position between the bobbin spindle and the contact roller.

FIGS. 8 and 9 illustrate once again what is particularly important according to this invention in the design of the winding machine in order to minimize the fluctuation in the contact pressure between the contact roller and the bobbin. Figures 8 and 9 show the geometry of the cross-section of the winding machine with the contact roller 11, the winding spindle 5.1 at the beginning of the winding cycle, the full bobbin 6 at the end of the winding cycle and the operating range B of the spindle turning circle which the bobbin turret describes with the axes of the bobbin spindles. During a winding cycle, the axis of the winding spindle moves between points A1 and A2 on the spindle turning circle S. The section between points A2 is referred to here as operating area B, in FIG. 1 at 57. Shown Furthermore, the pivot axis 48, on which the contact roller 11 is rotatably mounted, and the pivot axis 50, about which the rocker is pivotable, are in different geometrical positions.

The contact pressure with which the contact roller 11 rests on the bobbin has the direction of the connecting line between the center K of the contact roller and the axis A of the bobbin spindle. One extreme direction goes through points K and A1, i.e. the position of the axis of the winding spindle at the start of the winding cycle. The other extreme direction is the tangent from the axis K to the operating area B of the spindle turning circle S. It can be seen from both FIG. 8 and FIG. 9 that the line of action of the force G exerted by the contact roller is the guide direction of the contact roller, that is, the perpendicular D to the rocker 48 at point K. At the beginning of the winding cycle, this force G breaks down into the initial contact force P1, which passes through the initial position A1 of the spindle axis, and a force parallel to the rocker 48. In extreme cases, the force G in turn breaks down into the parallel force of the rocker 48 and that on the tangent T extreme contact pressure PE.

It is again evident from FIGS. 8 and 9 that the difference between the initial force P1 and the extreme force PE is relatively small because the arc which the initial force direction of the force P1 (connecting line between K and A1) cuts off from the spindle turning circle S only has a low arch height H. Decisive for this is the relative position of the center point MR of the coil turret, the radius of the spindle turning circle and the position of the contact roller 11 and the starting position A1 of the winding travel.

It can also be seen from FIG. 8, however, that the difference between the initial contact force P1 and the most extreme contact force PE is thereby further reduced can, if the guide direction of the contact roller 11, which is predetermined by the position of the pivot point 50, is set so that the guide direction or the direction of force G intersects the operating region B of the spindle turning circle S. With such a particularly favorable geometric design, the contact force initially decreases slightly in the course of the winding travel until it has exactly the value of the effective force G; then the contact pressure increases slightly up to the extreme value PE and then decreases again. This geometric design is therefore particularly preferred and is covered by claim 3.

About the traversing process:
It is shown in the embodiments 1, 4, 5, 6, 7 that the traversing 4 is movably mounted on a rocker 49 such that the distance between the traversing device and the contact roller 11 can be changed.

In the exemplary embodiment according to FIG. 1, FIG. 4, the smallest distance between the traversing device and the contact roller 11, which is maintained during the winding operation, is predetermined by the stop 51. This means that the distance is not changed during the winding cycle. However, the distance can be increased if the winding machine is to be serviced.

In the exemplary embodiments according to FIGS. 6 and 7, drive and control devices are also provided, by means of which the distance between the traversing device and the contact roller 11 can also be changed during the winding cycle. The drive device is a pneumatic cylinder-piston unit 66. The piston and the piston rod 67 of this cylinder-piston unit are supported on the rocker 49. In contrast, the cylinder is supported in the machine frame in the exemplary embodiment according to FIG. 6, on the rocker 48 in the exemplary embodiment according to FIG. 7 the contact roller. The control device 68 primarily comprises a program generator, by means of which the pressure for the drive device 66 can be controlled according to a predetermined program. 6 and 7, a breathing program is specified as such a program. With so-called breathing, the traversing stroke (see above) is periodically shortened and lengthened, for example by 5%. For this purpose, reference is made to the methods already mentioned above. Breathing serves the purpose of avoiding damage to the spool edges, in particular thickening of the spool circumference and errors in the spool end faces. Conventionally, breathing is effected in that the traversing path of the traversing device is shortened and lengthened accordingly. However, this is not possible with the traversing devices shown and described above. The invention creates a breathing method in which the traversing stroke is not changed, although the path of the traversing device remains constant.

This is done in that the distance between the traversing and the contact roller 11 is continuously increased and decreased by the drive device 66 according to the predetermined program. To do this, one must know that due to the increase in the distance between the contact roller and the traversing device, the actual traversing stroke of the thread on the contact roller and thus also on the bobbin is shortened. If, on the other hand, the distance between the traversing device and the contact roller is reduced, the actual traversing stroke of the thread on the contact roller or bobbin increases.

r

Radius der Leerhülse,

S

Schichtdicke

SB

Schichtdicke der Basisschicht.

It can be seen that other programs can also be specified. Such a program results, for example, from the aim of producing a coil, which is shown in FIG. 13 and is described in the above-cited US Pat. No. 4,789,112. According to such a program, the distance between the traversing and the contact roller - as shown in Fig. 14 - enlarged at the beginning of the winding cycle and then kept constant. In the period in which the distance is increased, a base layer with a layer thickness of no more than 10% of the total layer thickness of the coil is to be achieved. The time period in which the distance between the traversing device and the contact roller remains constant should be sufficient to build up at least 80% of the total diameter of the coil. Then the distance can be slightly reduced again. A schematic diagram of the distance over time is shown in FIG. 14. Here means

r

Radius of the empty tube,

S

Layer thickness

SB

Layer thickness of the base layer.

If this program is followed, a coil is created which has a weakly conical base layer on both ends. Otherwise, the coil is cylindrical. The change in distance can be made so small that the change in length of the base layer is barely visible and is only effective through improved, above all more stable support of the entire layers of the coil.

For the procedure of changing the bobbin:
When the end position (5.1) of the operating spindle shown in FIG. 1 is reached, the relief device 21 is pressurized in such a way that the contact roller 11 lifts off the full spool. In the illustrated examples, the relief device is a pneumatic cylinder-piston unit 21, which acts on the rocker 48 or - in FIG. 5 - on the carrier 63 of the contact roller. This is also a very small movement of, for example, 10 mm. The coil turret is now rotated further with the previous direction of rotation 56, the operating spindle 5.1 still being driven. As a result, the previous rest spindle 5.2 enters the Starting position of the operating range, that is the position in which the operating spindle 5.1 is shown in FIG. 1. It should be added that the drive motor 29.2 of the idle spindle has already been put into operation, so that the empty sleeve rotates at the desired peripheral speed. See the following Fig. 4: The empty sleeve 10.2, which is clamped on the spindle 5.2, forms a gap with the contact roller 11 through which the thread runs.

When moving into its operating position, the spindle 5.2 with the winding tube 10.2 clamped thereon is moved into the thread path stretched between the contact roller 11 and the full bobbin 6. The empty sleeve 10.2 has the same direction of movement as the thread on the contact path. For this reason, the process described here is referred to as synchronized trapping. It should be noted that the thread is still guided back and forth by the traversing device 4 and is therefore laid on the full spool 6 over at least approximately the entire traversing stroke H.

The lifting device described below is only one example.

The lifting device 25, which is shown pivoted by 90 ° in FIG. 2 and in FIG. 3A, has a pivot axis 34 which is parallel to the traversing direction, to the axis of the contact roller and to the axes of the winding spindles. The V-shaped front edge 35 intersects the pivot axis 34 with its two legs and, in the pivoted-out state (FIG. 1B), forms two leading edges lying at an angle to the traversing device, which converge in a guide notch 36. The guide notch 36 initially lies in a normal plane of the winding spindle, which lies within the traversing stroke. However, the lifting device can be moved on its pivot axis 34 in the direction of arrow 45 (FIGS. 2, 3A) until the guide notch 36 lies in a normal plane in which each Coil tube 10.1 or 10.2 has a catch slot 37.1 or 37.2. This normal level is referred to in this application as the catch level. The catch slot is a narrow notch made in the surface of the coil sleeve, which extends in a normal plane over part or all of the circumference and which can have a special design, which will be dealt with later. It should be mentioned that the catch slot 37 lies outside the traverse stroke H, in which the winding tube is normally wound.

Suitable designs of the catch slot are shown in FIGS. 10 and 11. This will be discussed later. Another suitable embodiment of the lifting device 25 will be shown later.

To change the thread, i.e. Detaching from the full spool 6, which is still rotating, and placing it on the empty tube 10.2, which is already rotating, the lifting device 25 is pivoted forward. By pivoting the lifting device 25, the thread - as shown in FIG. 4 - is brought so far out of the engagement area of the wings 7, 8 of the traversing device 4 that the contact is completely lost. Therefore, the thread slides on one of the inclined sliding edges 35 and enters the guide notch 36.

Simultaneously with the lifting device, the thread transfer device 26 is pivoted. The thread folding device has a pivot lever 41, on the free end of which there are a deflecting device. This is a plate 39. The pivot axis 38 is so and the length of the lever 41 and its shape are chosen so that the plate 39 can be retracted between the circumference of the empty spindle 5.2 operated in the operating position and the full reel 6 moved into the waiting position.

The shape of the sheet 39 results from FIGS. 3A and 3B. It should be noted that the real front view is shown in Fig. 3B. 3A differs from this only in that the thread lifting device 25 and the thread folding device 26 are shown rotated by 90 ° for a better illustration.
The sheet 39 is moved from the side on which the thread runs into the gap between the empty tube and the full spool.

As shown in Fig. 3B, the leading edge of the sheet, i.e. the edge which first comes into contact with the thread when swiveled in is designed as a sliding edge 42. A slot 43 is introduced into the sheet metal perpendicular to this sliding edge 42, the slot being essentially perpendicular to the sliding edge 42. The slot lies in a normal plane which, although the full coil 6, i.e. still cuts the traverse stroke H, but lies in an end region near the catch slot 37 located on the sleeve. This level is referred to in this application as the bead level, since in this normal level a thread bead of a few turns is formed on the full bobbin as the end.

Let us now consider the situation when the lifting device 25 is pivoted out and when the thread folding device 26 is pivoted into the position shown in FIG. 2 and in FIG. 3B:
The thread first slides on the V-shaped sliding edge 35. Therefore, the thread also slides on the sliding edge 42 of the sheet 39. The thread enters the guide notch 36 of the lifting device 25 and into the holding slot 43 of the thread folding device 26. It should be emphasized that the guide notch 36 and the holding slot 43 initially lie essentially in the same normal plane. Therefore, the thread first runs without traversing in the winding area of the empty tube 10.2 and in the winding area of the full bobbin 6 and forms a bead thereon. Now the lifting device 25 in the direction of the end of the spool on which the catch notch is located, ie in the direction of arrow 45, until the guide notch 36 lies essentially in the normal plane in which the catch slot is also on the empty tube 10.2 (catch level). During this movement of the lifting device 25 in the direction of arrow 45, the thread is held in the holding slot 43. On the other hand, it is conveyed into the area of the catch slot of the empty tube 10.2 by the catch notch 36, supported by the contact roller 11, which is preferably driven during the catch of the thread and therefore exerts a tensile force on the thread. It is noteworthy that the holding slot in sheet 39 is so designed and that sheet 39 moves so deep into the gap between the full bobbin and the empty tube that the thread is also deflected in the sense of a larger wrap around the empty tube 10.2.

The thread runs essentially in the normal plane of the catch slot to the catch slot 37. However, it runs out of the catch slot at an acute angle, since it is deflected through the holding slot 43 in the plate 39 in the direction of the center of the traversing stroke. 3A, 3B show that the thread leaves the catch slot at an acute angle. 3A, 3B, however, show the schematic connection in series of the traversing device, the contact roller, the winding spindles and the thread transfer device and therefore cannot reproduce the spatial looping conditions. In this respect, reference is made to FIG. 4. As a result of the special design of the catch slot and the large wrap, the thread initially falls deep into the catch slot. On the other hand, the thread is firmly clamped in the catch slot due to the lateral leading out of the catch slot, so that the thread cannot leave the catch slot again and tears off if it is a thread with a correspondingly low titer. Otherwise, a thread cutter, which is fastened on the sheet 39, can also be actuated at this moment, specifically in the region of the end of the holding slot 43.

After cutting the thread, the thread end caught in the catch notch is now wound on the empty tube 10.2 of the winding spindle 5.2. The lifting device 25 is then moved back into its neutral position. Therefore, the thread is caught again by the traversing device 4 and guided back and forth. As a result, the first thread layers of the bobbin are formed on the empty tube. The gap between the coil forming and the contact roller 11 is initially maintained. This means that the winding spindle 5.2 now in operation must be driven without regulating the peripheral speed of the forming coil. Therefore, the winding spindle 5.2 is driven at a constant speed or a speed decreasing according to a predetermined program, the speed being calculated in advance so that the peripheral speed of the empty tube and the first thread layers has the value necessary to achieve the thread speed. During the time in which the contact roller 11 does not rest on the coil being formed, the rotary control drive of the coil turret 18 is also out of operation. The coil turret 18 is therefore fixed. The bobbin change is now carried out on the bobbin spindle 5.1 by replacing the full bobbin there with an empty tube.

3C, a coil transport device 65 is partially shown as a doffer. This bobbin transport device 65 can be moved along the machine front of the winding machine. The bobbin transport device has a bobbin mandrel 66 at the height at which the bobbin spindle 5.1 with the full bobbin 6 formed thereon is during the time phase in which the contact roller is lifted off the bobbin spindle 5.1 and the new bobbin formed thereon Position with the winding spindle 5.2 is aligned. A push-out device 67 is now started. The push-out device is described for example in DE-PS 24 38 363 = US-PS 3,974,973 (Bag. 906). It can are then a fork which can be moved parallel to the winding spindle 5.1 and thereby engages behind the winding tube 10.1 on the end face of the machine and pushes it from the winding spindle 5.1 onto the winding mandrel 66. Correspondingly, empty tubes can now also be pushed onto the winding spindle 5.2.
Other suitable doffer are shown for example in DE-PS 24 49 415 (Bag. 917) and DE-OS 24 55 739 (Bag. 923). As already said, this bobbin changing process takes place while the contact roller is lifted from the bobbin spindle 5.2 and the bobbin forming on it.

There are two ways to start the revolver revolver. According to the first method, the time which is necessary for the bobbin changing process is programmed into a timer and specified by this timer. However, this time is not only specified according to the requirement of the bobbin changing process, but also according to winding-up aspects. This will be discussed later. After the specified time has elapsed, the timer restarts the rotary drive of the coil turret by reducing the pressure in the relief device 21 to the level desired for normal operation. This lowers the contact roller again until it lies on the spool. The sensor 21 is now in operation again and controls the rotary drive of the coil turret 18 as a function of the measuring movements of the contact roller.

According to the other possible method, as many thread layers are formed on the empty tube 10.1 of the winding spindle 5.2 that has started operating until the resulting bobbin grows against the contact roller. This causes a deflection on the rocker 48, which is detected by the sensor 52. The output signal is now also used to reduce the pressure in the relief device 21 back to the level desired for normal operation.

As mentioned above, the lifting of the contact roller from the empty tube 10.2 that has started up and the winding spindle 5.2 has the reason, on the one hand, of carrying out the bobbin change on the winding spindle 5.1 that is now in the waiting position. But there is also a winding-up reason. This is that the first layers of thread are wound without contact with the contact roller. When winding the first layers of thread, the bobbin is still very hard. Therefore, when the contact roller comes into contact with the first thread layers, there is a risk that the thread layers will be damaged. This risk is avoided according to the invention. This winding-up aspect is taken into account when specifying the time in which the contact roller remains inoperative.

Otherwise, the invention also offers the possibility of specifying the force with which the contact roller rests on the bobbin and to program it during the bobbin travel in such a way as is desirable or necessary in terms of winding technology. If a constant contact force is desired, the pressure-relieving device is subjected to a slight pressure during the winding-up process after the contact between the contact roller and the forming coil has been made, but this remains constant and serves to provide part of the total weight of the rocker 48 and the contact roller and traversing device to compensate for adjusting the contact pressure exerted by the contact roller on the coil to the correct level. However, as already mentioned, it is also possible to control the pressure in such a way that a predetermined course of the contact pressure is achieved via the winding travel.

During the winding of the first layers of thread there is a risk that the cut or torn end of the thread will be flung around on the full spool 6, which is still rotating and has to be braked. On the one hand, the sheet 39 already provides effective protection. In addition however, a mudguard 60 is provided, which is shown in both FIG. 1 and FIG. 4. The fender 60 is pivotally mounted. The swivel axis is parallel to the axes of the winding spindles. During operation, it is folded out of the possible range of movement of the coil turret and the spools or winding spindles clamped thereon and held in its rest position by a magnet 61. For the purpose of changing the spool, the mudguard 60 - as shown in FIG. 4 - is pivoted in the direction of the spool turret, simultaneously with the pivot lever 41 of the folding device 26. The free end of the mudguard 60 is supported on the free end of the plate 39 . Since the mudguard 60 on the side facing away from the thread run and the plate 39 from the thread run side is pivoted into the gap between the full bobbin 6 and the empty tube 10.2, at a time when the thread has not yet been torn or cut off, the plate 39 and the protective plate 60 form a complete protection, both locally and in terms of time, of the new bobbin to be wound on the empty tube 10.2 against the twisting end of the full bobbin. Of course, the holding slot 43 is made very narrow, so that the twisting thread end of the full spool cannot penetrate the holding slot.

FIGS. 10 and 11 show developments of the left end of a winding tube as well as a partial section A-A through the catch slot.

The sleeve 10 has a catch slot 37 at the end shown at a certain distance from its end face. The catch slot extends in the circumferential direction over an angle of, for example, 120 °. If one assumes that both the surface of the sleeve 10 and the thread move in the direction of arrow 55, the catch slot begins with an insertion piece 74. This insertion piece 74 is distinguished characterized in that it has a relatively large width compared to the thread diameter. The sinker 74 can extend, for example, over 45 ° of the coil circumference. The catch piece 75 then follows. The catch piece 75 looks different in the two examples given. 10, the catch piece 75 is formed in that the catch slot narrows conically in the circumferential direction, namely on a relatively short piece of its circumference, for example 20 °.

In the embodiment according to Fig. 11, the catch piece is designed so that each wall has sawtooth-like projecting, radial edges which are arranged one behind the other in the circumferential direction, e.g. are arranged at a distance of 2 mm. The edges of the opposite walls are offset from each other and - as I said - sawtooth sharp. The axial distance between the normal planes in which the edges lie is smaller than the thread thickness. The distance can be zero or negative. The edges preferably point in the direction of movement 55 of the winding tube.

In the secondary figures, a partial section A-A is shown through the catch slot.

About the function:
When catching the thread, the thread is guided in the normal plane of the catch slot 37. Since the thread and the sleeve surface have the same direction of movement 55, the insertion piece 74 comes into contact with the thread first. The thread essentially falls to the bottom of the catch slot. This means that the thread speed is slightly - in the order of 1% - greater than the translational speed of the catch slot or the sleeve. The resulting relative speeds, however, do not have any effect in the form of frictional forces acting on the thread, since the insertion piece 74 is so wide that it does not affect the thread significantly hindered. Therefore, the thread pulling forces are sufficient to pull the thread as deep as possible into the catch slot or the insertion piece. The catch piece 75 is now designed so that clamping forces are suddenly exerted on the thread. This happens because the catch piece very suddenly narrows so far that practically positive locking occurs between the thread and the side walls of the catch slot. It must be taken into account here that multifilament chemical threads are involved, which offer multiple possibilities of engagement for a positive connection compared to the bobbin tubes made of cardboard.

The very sudden, cutting-like narrowing of the catch piece 75 according to FIG. 1 is sufficient for this practical form fit.
2, the thread is deflected very suddenly in a zigzag shape, which practically leads to a positive connection.

It has been shown that the thread which has fallen deeply into the catch slot and is then clamped in is securely clamped and torn off when the thread leaves the catch slot laterally, as is provided in the device according to the invention.

REFERENCE SIGN LISTING

1

Head thread guide

2nd

Thread running direction

3rd

thread

4th

Traversing device

5

Winding spindle

5.1

Operating spindle

5.2

Resting spindle

6

Kitchen sink

7

wing

8th

wing

9

Guideline

10th

Bobbin

10.1

Bobbin

10.2

Empty pod

11

Contact roller

12th

Shaft, rotor

13

Shaft, rotor

14

Traversing motor

15

Reverse thread shaft - groove

16

Reverse thread shaft

17th

18th

Coil turret, turret

19th

20th

21

Cylinder-piston unit, relief device

22

Gear, traverse gear

23

24th

25th

Lifting device

26

Thread transfer device

27

Direction of rotation

28

Direction of rotation

29

Motor, spindle motor, synchronous motor, asynchronous motor

30th

Frequency transmitter

31

Control unit

32

33

Revolver motor

34

Swivel axis

35

Leading edge, sliding edge

36

Leadership notch

37

Slot

38

Swivel axis

39

sheet

40

Traversing thread guide

41

Swivel lever

42

Sliding edge

43

Slot, holding slot

44

Straight guidance

45

Arrow direction

46

47

Rubber block

48

Swingarm

49

Swing arm, bearing eye

50

Swivel axis

51

attack

52

Sensor, distance sensor

53

Rotary control device

54

Rotary control device

55

Direction of rotation, arrow

56

Direction of rotation, arrow

57

Operating area

58

tangent

59

60

Fender

61

magnet

62

63

carrier

64

guide

65

Coil transport device

66

Cylinder-piston unit, drive device, coil mandrel

67

Piston rod, push-out device

68

Control device

69

70

wave

71

brake

74

Invasion piece

75

Catch piece, catch brake

Claims (23)

1. Bobbin winding machine
   for a continuously fed fibre,
   having a rotatable bobbin revolver (18) on which two winding spindles (operating spindle 5.1, non-operating spindle 5.2) are supported, having a cross-winding device and a contact cylinder which are disposed upstream of the bobbin revolver (18) in the fibre run, the contact cylinder being in peripheral contact with the bobbin being formed on the one winding spindle (operating spindle) and the distance between the axis of the contact cylinder and the axis of the operating winding spindle being variable in the direction of an increase and in accordance with the growing bobbin diameter,
   the contact cylinder (11) being supported on a carrier which is movable in such a way that the contact cylinder may execute a lifting movement with a radial component relative to the operating spindle (5.1), and a preselected force in the direction of movement of the carrier acting upon the contact cylinder (11),
   characterized in that
   the revolver is connected to a rotary operating mechanism by means of which the revolver (18) may be driven during winding travel in the direction of an increase in the distance between the axis of the contact cylinder (11) and the axis of the operating spindle (5.1),
   that the rotary operating mechanism (33) is incorporated with a sensor (52) and a rotation control device (54) in a control loop,
   that the sensor (52) during winding travel detects the lifting movement of the contact cylinder (11),
   that the rotary operating mechanism (33) is controllable by the sensor in dependence upon the variation between the setpoint position and the actual position of the contact cylinder in the control loop in such a way that the position of the contact cylinder remains substantially constant in the course of winding travel.
2. Bobbin winding machine according to claim 1,
   characterized in that
   the bobbin revolver (18) is rotatable by the rotation control device (54) in the same direction of rotation as the winding spindle,
   that the fibre is wrapped in a first direction around the contact cylinder with an angle of wrap of more than 60°, that the fibre is wrapped in the opposite direction around the bobbin resting against the contact cylinder, that - in relation to the connecting plane between the axis of the bobbin revolver and the axis of the contact cylinder -
   the operating spindle (5.1) is situated at the side towards which the fibre running off from the contact cylinder is directed,
   and that the contact cylinder and the bobbin revolver with the spindles mounted thereon are so disposed relative to one another that the line of initial force is a secant of the spindle turning circle,
   the line of initial force being the connecting line between the axis of the contact cylinder and the axis of the operating spindle (5.1) when situated in its starting position.
3. Bobbin winding machine according to claim 2,
   characterized in that
   the carrier with the contact cylinder supported thereon and the bobbin revolver with the spindles supported thereon are so disposed relative to one another that the angle alpha between the line of initial force and the line of extreme force is smaller than 20°, preferably smaller than 15°,
   the line of extreme force being the tangent extending through the axis of the contact cylinder to the spindle turning circle.
4. Bobbin winding machine according to one of the preceding claims,
   characterized in that
   the contact cylinder rests with a gravity component on the winding spindle,
   and that the carrier of the contact cylinder is connected to a relief device (59), preferably a controllable relief device, which for at least partial compensation of the force of gravity acts upon the carrier.
5. Bobbin winding machine according to claim 4,
   characterized in that
   the relief device is program-controllable in such a way that the resulting contact pressure of the contact cylinder on the bobbin has a preselected characteristic, e.g. remains substantially constant, in the course of winding travel.
6. Bobbin winding machine according to claim 4,
   characterized in that
   the relief device of the carrier is controllable in such a way that the contact cylinder lifts by a small gap from the operating winding spindle.
7. Bobbin winding machine according to one of the preceding claims,
   characterized in that
   the carrier of the contact cylinder (11) is a rocker (48) which is suspended in the machine frame so as to be capable of swivelling and on whose free end the contact cylinder is supported.
8. Bobbin winding machine according to claim 7,
   characterized in that
   the rocker (48) is supported so as to be capable of swivelling resiliently in a rubber block clamped in the machine frame.
9. Bobbin winding machine according to one of the preceding claims,
   characterized in that
   the cross-winding device is supported on its own carrier (49), which in the direction of the force acting upon the contact cylinder is connected in a form-fit manner to the carrier of the contact cylinder (11) but which in the opposite direction is movable independently of the carrier of the contact cylinder.
10. Bobbin winding machine according to claim 9,
    characterized in that
    the carrier (49) of the cross-winding device is a rocker which is supported so as to be capable of swivelling on the carrier (48) of the contact cylinder.
11. Bobbin winding machine according to claim 9,
    characterized in that
    the carrier (49) of the cross-winding device is a rocker which is supported so as to be capable of swivelling in the machine frame substantially coaxially to the rocker (48) of the contact cylinder.
12. Bobbin winding machine having a cross-winding device and a contact cylinder according to one of the preceding claims,
    characterized in that
    the carrier of the cross-winding device is movable independently of the contact cylinder,
    and that acting upon the carrier of the cross-winding device is a drive device by means of which the distance between the cross-winding device and the contact cylinder is variable.
13. Bobbin winding machine according to claim 12,
    characterized in that
    the drive device is controllable according to a preselected program in the course of winding travel.
14. Bobbin winding machine according to claim 12,
    characterized in that
    the drive device is controllable in such a way that the distance between the cross-winding device and the contact cylinder increases during winding travel, particularly at the start of winding travel.
15. Bobbin winding machine according to claim 12,
    characterized in that
    the drive device is controllable in such a way that the distance between the cross-winding device and the contact cylinder may be increased and decreased at recurrent intervals in the course of winding travel.
16. Bobbin winding machine according to claim 12,
    characterized in that
    by means of the drive device the position of the cross-winding device relative to the winding spindle is controllable in such a way that the cross-winding device is axially displaced in both directions at recurrent intervals.
17. Bobbin winding machine according to one of the preceding claims,
    characterized in that
    as a deflecting fibre guide, a plate (39) may be moved, in particular swivelled, from the fibre run side into the gap between the non-operating spindle (5.2) with empty tube (10.2), which has been moved into operating position, and the operating spindle (5.1) with full bobbin (6) which is still being driven,
    that the plate has a retaining slot (43) emanating from its front edge (42), which slot at its base lies in a normal plane of the full bobbin (6),
    and that a guard plate (60) at the side of the non-operating spindle and operating spindle, which is remote from the fibre run, may be introduced, in particular hinged, into the region between the non-operating spindle moved into operating position and the operating spindle moved into non-operating position in such a way that the guard plate (60) together with the plate (39) of the deflecting fibre guide (26) already screens off the empty tube (10.2) from the full bobbin prior to interception of the fibre at the empty tube.
18. Method of operating a bobbin winding machine having two winding spindles (operating spindle (5.1); non-operating spindle (5.2) mounted on a bobbin revolver, the bobbin revolver on completion of winding travel being rotated in such a way that the winding spindle with a full bobbin (operating spindle (5.1)) passes out of the operating range and the winding spindle with an empty tube (non-operating spindle (5.2)) passes into the operating range, a peripheral contact being effected in the operating range between the bobbin to be formed and a contact cylinder,
    characterized in that
    the bobbin revolver (18) during winding travel is set in rotation by a rotary operating mechanism, which is controlled by a control loop, in accordance with the growing bobbin diameter and with the position of the contact cylinder being substantially unchanged,
    that the rotation (56) on completion of winding travel is continued at an increased speed until the non-operating spindle (5.2) with the empty tube (10.2) passes into the region of the contact cylinder (11) and the contact cylinder (11) is no longer in contact with the full bobbin of the operating spindle (5.1),
    that the carrier with the contact cylinder (11) is displaced in such a way that, when the non-operating spindle (5.2) moves into the region of the contact cylinder (11), a small gap remains between the contact cylinder and the empty tube (10.2) and the control loop having a sensor (52) for detecting the lifting movement of the contact cylinder (11) and having the rotary operating mechanism (33) is interrupted,
    that the rotary operating mechanism (33) of the bobbin revolver (18) is de-activated,
    that the fibre is removed from the cross-winding device and held fast by an interception fibre guide (25) associated with the cross-winding device (4),
    that a deflecting fibre guide (26) is introduced into the fibre run between the non-operating spindle (5.2) with the empty tube and the still driven operating spindle (5.1) with the full bobbin,
    which deflecting fibre guide (26) axially secures the fibre in such a way that the fibre running off from the deflecting fibre guide continues to run in a normal plane onto the full bobbin (6) and is wound there into a bead, while at the same time the fibre is wrapped with an increased angle of wrap around the empty tube (10.2), and that the interception fibre guide (25) is then axially displaced in such a way that the fibre upstream of the empty tube (10.2) passes into the region of the interception slot (37) and runs into and is caught by the interception slot,
    that the carrier with the contact cylinder (11) is lowered,
    so that the empty tube (10.2) with the fibre deposited thereon comes into contact with the contact cylinder and that as a result the control loop with the sensor and the rotary operating mechanism is closed again.
19. Bobbin winding machine according to claim 1,
    characterized in that
    the contact cylinder (11) is connected to an auxiliary operating mechanism which is activated when contact with the winding spindle is interrupted.
20. Bobbin winding machine according to claim 1 or 19,
    characterized in that
    the rotation control device for the rotary operating mechanism of the bobbin revolver is re-activated when the fibre layers on the winding spindle grow against the contact cylinder and the carrier of the contact cylinder has reached its setpoint position.
21. Bobbin winding machine according to claim 1 or according to one of claims 19-20,
    characterized in that
    removal of the full bobbin is effected, in particular an automatic bobbin changer for removing the full bobbin and for pushing on an empty tube may be set in operation, while the rotation control device is de-activated on lifting of the contact cylinder.
22. Bobbin winding machine according to claim 1,
    characterized in that
    the rotary operating mechanism is controllable by means of a sensor in such a way that, upon an unacceptable variation between the setpoint value and the actual value of the position of the contact cylinder, the rotary operating mechanism is driven and, upon correspondence as well as upon a permitted variation between the setpoint value and the actual value of the position of the contact cylinder, the rotary operating mechanism is braked.
23. Bobbin winding machine according to claim 1,
    characterized in that
    the rotary operating mechanism may be continuously driven by the sensor in such a way that the variation between the setpoint value and the actual value of the position of the contact cylinder is adjusted to a permitted low value.

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