EP0914287A1

EP0914287A1 - Method for winding up an advancing thread

Info

Publication number: EP0914287A1
Application number: EP98916999A
Authority: EP
Inventors: Hermann Westrich
Original assignee: Barmag AG; Barmag Barmer Maschinenfabrik AG
Current assignee: Oerlikon Textile GmbH and Co KG
Priority date: 1997-03-25
Filing date: 1998-03-18
Publication date: 1999-05-12
Anticipated expiration: 2018-03-18
Also published as: KR20000015980A; EP0914287B1; CN1102124C; US6105896A; WO1998042607A1; CN1220642A; TW483866B; DE59811457D1

Abstract

The spool (17) is formed on a spool spindle (14, 15), said spool spindle being driven, and mounted on a moving support (11) in such a way that it projects outwards. A press roll (15) is in contact with the perimeter of the spool by means of a bearing force. The press roll is also mounted on a moveable support (8). As the spool travels, the distance between the centers of the spool and the press roll is governed by an evasive movement of the press roll or a constant evasive movement of the spool spindle in accordance with the increasing spool diameter. The constant evasive movement of the spool spindle takes place at a variable speed, the speed being predetermined for controlling the device, in accordance with the increase in diameter of the spool.

Description

Process for winding up a thread

The invention relates to a method for winding a thread running into a bobbin according to the preamble of claim 1 and a winding machine for carrying out the method according to the preamble of claim 17.

When winding a continuously running thread into a bobbin, in which a pressure roller with a contact force rests on the circumference of the bobbin, the increase in the bobbin diameter is made possible by an evasive movement of the bobbin or by an evasive movement of the pressure roller. The contact pressure between the spool and the pressure roller is specified by hydraulic or pneumatic force transmitters. Since the center distance between the pressure roller resting on the circumference of the spool and the spool also has an effect on the contact force, the change in the center distance simultaneously causes a change in the contact force. The problem thus arises that on the one hand there is always a predetermined contact force between the pressure roller and the bobbin and on the other hand an unimpeded increase in the bobbin diameter is possible.

From EP 0 374 536 (Bag. 1670) a method and a dishwasher are known in which the evasive movement of the winding spindle receiving the bobbin during the winding cycle is regulated as a function of the position of the pressure roller. Here, the evasive movement of the winding spindle can take place gradually or continuously. Since the contact force between the pressure roller and the spool depends on the relative position between the pressure roller and the spool, there is a change in the contact pressure inevitable during the winding trip.

From US 5,407,143 a dishwasher is known in which the rotary movement of a turret is controlled with a cantilevered winding spindle in such a way that the contact pressure between a pressure roller and the bobbin maintains a predetermined target value. Here, an adjusting device for changing the center distance is used at the same time to regulate the contact force. This creates unwanted changes in investment power due to stick-slip effects.

From WO 96/01222 a method and an on dishwasher is known in which the rotary movement of the turret takes place as a function of the angular position of the winding spindle. From the relationship between the angular position of the winding spindle on the winding turret and the diameter of the bobbin, the corresponding angular position is inferred from the changing diameter. Since the pressure roller resting on the spool is stationary, the growth of the spool increases the contact force between the pressure roller and the spool. In addition, the method - especially in the case of soft spools - can lead to overdriving of the winding turret, so that the contact between the pressure roller and the spool is completely lost.

The method disclosed in DE 195 38 480 also has the disadvantage that the step-wise rotary movement of the winding turret, depending on the angular position of the winding spindle in the course of the winding travel, causes an inconsistent change in the contact force between the coil and the pressure roller due to the diameter increase. In the known method, a time is specified after which the angular speed of the winding turret is calculated recurring depending on the position of the winding turret. Since the temporal increase in diameter of the bobbin with a small bobbin diameter requires a substantially faster change in the angular speed of the bobbin turret compared to a large bobbin diameter, there are fluctuations in contact force at the beginning of the bobbin travel.

Accordingly, it is an object of the invention to further develop a method mentioned at the beginning for winding up a continuously starting thread and a winding machine for carrying out the method in such a way that the thread has a constant contact force with a predetermined contact force or a given contact force profile during the entire winding cycle Starting speed of the thread is wound up.

Another object of the invention is to change the center distance between the pressure roller and the spool in proportion to the increasing diameter.

The solution to the problem results from the features of claim 1 and from the features of claim 17.

When winding a thread at an essentially constant thread speed, the increase in diameter over time depends on the respective bobbin diameter. Thus, with a small bobbin diameter, the outside diameter of the bobbin will grow much faster than with a large outside diameter with the same amount of thread wound per unit of time. The increase in diameter per unit of time can therefore be viewed as a function of the outside diameter of the coil. This increase in diameter determines the change in the center distance between the coil and the pressure roller. The invention now establishes the connection between the evasive movement of the winding spindle to increase the center distance between the pressure roller and the spool and the increase in diameter of the spool depending on the spool diameter. The evasive movement of the winding spindle therefore takes place at a variable speed which results from a predetermined speed function. The speed function assigns a specific speed dependent on the temporal increase in diameter of the coil to each coil diameter in the course of the coil travel. The particular advantage of this method is that the contact force set on the pressure roller is independent of the evasive movement to increase the center distance between the spool and the pressure roller. The circumferential contact between the spool and the pressure roller remains unchanged as long as the speed of the evasive movement is adapted to the diameter increase.

In cases where the spool is guided in a linear movement path relative to the pressure roller by means of the movable carrier, the method variant according to claim 2 is particularly advantageous. Here the evasive movement of the winding spindle takes place at a speed which is proportional to the diameter increase of the winding during the winding cycle. Thus, the bobbin can grow with the position of the pressure roller unchanged and with the set contact force being maintained.

In the cases in which the bobbin is moved on the curved movement path relative to the pressure roller during the winding travel, the method variant according to claim 3 and claim 4 is particularly advantageous. Here, the evasive movement of the winding spindle is carried out at a speed that is not proportional to the diameter increase. This allows the The speed of the evasive movement also leads to a change in the contact force. In the case of a movable pressure roller, the contact force between the spool and the pressure roller is essentially determined by the weight of the pressure roller. The force effect of the pressure roller is therefore largely dependent on its position in relation to the spool. The contact force can thus be influenced and controlled in a very simple manner by the deflection movement of the bobbin during winding. In the case of bobbin construction in particular, it is advantageous if the contact force can be changed during the bobbin travel. Each set contact force can then be kept constant by a corresponding speed of the evasive movements.

Another advantage is that the wrap around the thread on the pressure roller can be influenced. The length of the looping of the thread on the pressure roller is referred to as the so-called "print length". The print length thus defines the length from the point at which the thread runs onto the pressure roller to the point at which the thread is deposited on the spool Thread on the pressure roller and has a direct influence on the bobbin build-up. For example, if the print length is too short, the risk of strikers on the bobbin increases. In these cases, the oscillated thread at the end of the bobbin falls off the edge of the bobbin therefore pretend that the pressure roller constantly assumes a position in which the print length on the pressure roller is constant.

In a particularly advantageous variant of the method, the winding spindle is moved at a speed which is proportional to the diameter increase of the bobbin in some areas of the winding travel and thus leads to an unchanged position of the pressure roller or which is not proportional to that in some areas The diameter of the coil is increasing, so that the position of the

Pressure roller changed with regard to influencing the contact force or the print length. This method variant is particularly advantageous in order to maintain certain contact pressure profiles during the winding cycle. Defined print lengths can also be set on the pressure roller during the winding cycle.

When winding a thread into a bobbin, the winding cycle is characterized by a winding time in which the bobbin is completely wound. The winding time depends on the winding speed, the thread titer and the package build. The bobbin has a specific bobbin diameter at all times during the winding cycle. This means that a specific coil diameter can be assigned to each winding time. The method variant according to claim 5 can thus be used particularly advantageously in processes in which the winding parameters and the thread type remain unchanged. The control of the evasive movement of the winding spindle can be carried out as a pure time control. The speed function on which the control system is based represents the relationship between the speed of the evasive movement and the winding time.

In a particularly advantageous method variant according to claim 6, the evasive movement of the winding spindle is controlled as a function of the winding diameter. The combination of the coil diameter and the winding time enables the parameters that change in the process to be recorded directly and thus the speed of the evasive movement to be specified precisely.

In order to continuously record the coil diameter of the coil to be wound, it is of advantage if the position of the carrier of the pressure roller relative to the machine frame or the position of the carrier of the winding spindle relative to the machine frame is determined. Since the pressure roller and the spool are in constant circumferential contact, the corresponding position of the pressure roller or the corresponding position of the spool spindle can be calculated solely from the geometric conditions for each spool diameter.

The position of the carrier of the pressure roller, for example a rocker arm, or the position of the carrier of the winding spindle, for example likewise a rocker arm, in its position relative to the machine frame is thus known at the same time. This relationship between the bobbin diameter and the position of the carrier can be specified to a control device of the winding machine as a master curve. The respective coil diameter could then be determined solely from the measurement of the position of the carrier. At the same time, the instantaneous diameter increase is known, so that the speed of the evasive movement can be controlled accordingly.

The method variant according to claim 8 has the advantage that no additional devices are required for detecting the coil diameter. In order to keep the thread tension essentially constant during winding, the winding speed is regulated with the aid of the pressure roller. The speed of the pressure roller is continuously recorded and compared with a predetermined setpoint. The setpoint specifies a constant speed of the pressure roller. If the actual speed deviates from the target speed, the drive of the winding spindle is controlled in such a way that the desired speed is set on the pressure roller. This information, which is already present in a dishwasher, can also be used in this method variant to determine the coil diameter. In a particularly advantageous method variant according to claim 9, the speed of the evasive movement is calculated in advance from a parameter which characterizes the temporal increase in diameter of the coil and the coil diameter. The relationship can be represented by the following mathematical equation: v = (K ^2/2) * (l / D). Here v denotes the speed, K the diameter increase parameter and D the coil diameter. Due to the predetermined speed of the evasive movement, the pressing force can be kept essentially constant during the winding travel. The speed function results from F _v = v (D), ie a specific speed v results for each bobbin diameter that is wound during the winding cycle.

According to the variant of the method according to claim 10, the parameter K, which characterizes the temporal increase in diameter of the bobbin, can be determined during the winding travel with the carrier of the winding spindle at a standstill.

In order to traverse a contact force profile with variable contact force during the winding cycle, the method variant according to claim 11 can be used particularly advantageously. The position of the pressure roller is included in the determination of the speed. The position of the pressure roller can be defined, for example, by the swivel angle α of the movable support of the pressure roller, which is designed as a rocker. From the position of the pressure roller and the bobbin diameter, the contact force caused by the weight can be calculated on the basis of the geometric relationship between the pressure roller and the bobbin spindle. The speed is then based on the coil diameter, the calculated contact force corresponds, and the diameter increase determined.

Since the contact force between the pressure roller and the spool is essentially determined by the relative position of the pressure roller to the spool, the method according to claim 12 is particularly suitable for determining the contact force and for using it to control the evasion speed.

The method according to claim 13 is particularly advantageous in order to wind up a continuously starting thread, in which an automatic change between a first and a second winding spindle takes place by rotating a winding turret. Here, in a winding area at the beginning of the winding cycle, the center distance between the pressure roller and the bobbin is changed by the evasive movement of the pressure roller with the carrier of the winding spindle stationary. During this time, the second winding spindle with a fully wound bobbin is in a so-called parking station. During this time, the full bobbin is pulled off the bobbin spindle by means of a clearing device and exchanged for an empty tube. Subsequently, the winding travel is continued in a transition area such that the center distance is increased by the evasive movement of the winding spindle. In the transition area, however, the evasive movement of the winding spindle is carried out at such an accelerated speed that the pressure roller moves back to its starting position in a short time. The starting position of the pressure roller represents the actual optimal working point of the dishwasher. This working point is therefore only left for the time of clearing, in order to be able to be set again as quickly as possible afterwards. Following the transition area, the winding travel in the winding area is then continued by the steady evasive movement of the winding spindle. When dividing the winding travel into a winding area, a transition area and a winding area, the speed function relevant for the evasive movement of the winding spindle in the winding area can be determined during the winding travel in the winding area. The carrier of the winding spindle (winding turret) stands still in the winding area. The increasing spool diameter causes the pressure roller to evade in this phase. The pressure roller will deflect on a guideway determined by the carrier. The weight component of the pressure roller acting on the surface of the spool will change continuously as it passes through this guideway. Each position of the pressure roller thus corresponds to a certain contact force.

According to the method variant according to claim 14, the actual values of the contact force are now determined in this phase and the control of the evasive movement of the winding spindle in the winding area is used as a basis. Weight tolerances of the pressure roller and the carrier of the pressure roller and any hysteresis forces which occur when the pressure roller is moved can thus be compensated for advantageously.

Likewise, according to claim 15 there is the possibility of determining the temporal increase in diameter in the winding area. From the known sleeve diameter and the bobbin diameter measured continuously per unit of time, the amount of thread deposited on the bobbin per unit of time can be determined, so that the diameter increase of the bobbin and the parameter K are known. The speed function with which the evasive movement of the winding spindle in the winding area must be carried out can thus be calculated in advance for the entire winding travel. The speed of the evasive movement of the winding spindle is equal to the angular speed of the Winding turret.

The evasive movements of the winding spindle are brought about by a drive which drives the respective carrier and the speed of which can be changed. The drive is advantageously designed as an electric motor, which is controlled by means of an actuator for changing the drive speed. Depending on the type of carrier of the winding spindle, the drive can also be designed as a pneumatic cylinder, pneumatic motor or servo drive.

The dishwasher according to the invention is characterized in that the signals generated for regulating the winding speed can be used simultaneously to control the evasive movement of the winding spindle. By specifying a speed function as a function of the bobbin diameter or the winding time, the drive of the bobbin turret is set to the speed determined by the currently corresponding diameter increase rate at any time during the winding cycle.

In order to receive feedback of the controlled change in position of the bobbin turret during the winding cycle, the on dishwasher according to claim 18 is particularly advantageous. Here, the position of the carrier of the pressure roller or the position of the winding turret is continuously detected by a position sensor and given to the control device. Since, due to the geometrical arrangement, only one bobbin diameter corresponds to each position of the pressure roller and each position of the winding turret, a comparison can be made between the control and the actual position.

Particularly advantageous here is the design of the winding machine according to claim 20, which continuously calculates the during the winding trip Speed function for controlling the winding turret calculated. The winding parameters such as the speed of the pressure roller and the speed of the winding spindle are continuously fed to a computing unit of the control device. The calculation can be carried out both continuously and at intervals, for example at given diameter steps.

According to a particularly advantageous development, the carrier of the pressure roller is connected to a drive. This makes it possible to wind contactlessly in certain sections during the winding trip. Since the speed function of the winding turret is known during the winding travel, a target diameter of the bobbin can be exactly predetermined in the case of contactless winding. A cyclical lifting of the pressure roller from the surface of the bobbin can also be advantageous in the case of heavily prepared threads in order to be able to break down the lubricating film which grows in front of the starting gap. The drive of the carrier is designed, for example, as a pneumatic cylinder.

Further advantageous developments of the invention are defined in the subclaims.

Further advantages of the method according to the invention are explained below using an exemplary embodiment in the following drawings.

Show it:

Figure 1 is a side view of a winding machine in operation.

FIG. 2 shows the front view of the dishwasher from FIG. 1 in operation;

Fig. 3 is a diagram with a speed curve during the

Winding trip; Fig. 4 is a diagram with an investment force curve during the

Winding trip; 5 schematically shows a dishwasher in the winding area;

6 schematically shows a dishwasher in the transition area; Fig. 7 shows schematically a winding machine in the winding area.

Fig. 8 schematically shows the force relationship between the pressure roller and the spool and Fig. 9 schematically shows the pressure roller in two different positions.

An exemplary embodiment according to FIG. 1 and FIG. 2 is described together below.

The winding machine has a winding turret 11 which is rotatably mounted in a machine frame 9 by means of the bearing 20. The winding turret 11 is driven by an electric motor 40. In the winding turret 11, two winding spindles 14 and 15 are rotatably supported so as to be offset from one another by eccentric offset. In Fig. 1 it is shown that the winding spindle 14 is in the operating position in a winding area and the winding spindle 15 in a waiting position in an exchange area of the dishwasher.

A thread 1 is supplied to the winding machine at a constant speed. The thread 1 is first passed through the head thread guide 2, which forms the tip of the traversing triangle. The thread then arrives at a traversing device. The traversing device here consists of a traversing drive 6 and the vanes 3. The vanes 3 alternately guide the thread 1 back and forth along a guide ruler 4 within the limits of a traversing stroke. The traversing device is movably mounted on the machine frame 9 of the winding machine. For this purpose, a carrier 7 is used, at the free end of which Traversing device is attached and which is pivotally mounted with the other end such that the traversing device can perform a movement perpendicular to itself and to the pressure roller 5, ie a parallel displacement.

Behind the traversing device, the thread is deflected on a pressure roller 5 by more than 90 ^° and then wound on the spool 17. The coil 17 is formed on the winding tube 16. The winding tube 16 is clamped on the freely rotatable winding spindle 14. The winding spindle 14 with the winding sleeve 16 clamped thereon and the coil 17 to be formed thereon is located in the central winding region.

The winding spindle 14 is supported in the winding turret 11 via the bearing 30. The winding spindle 14 is driven by a winding spindle drive 27, which is designed, for example, as a synchronous motor or asynchronous motor. The winding spindle drive 27 is fastened in alignment with the spindle 14 on the winding turret 11. The winding spindle drive 27 is supplied by a frequency generator 21 with three-phase current of a controllable frequency. The frequency transmitter 21 is controlled by a control unit 34 which is controlled by a speed sensor 35. The speed sensor 35 scans the speed of the pressure roller 5. The control unit 34 controls the frequency transmitter 30 of the winding spindle 14 in such a way that the speed of the pressure roller 5 and thus also the surface speed of the winding 17 remains constant despite the increasing winding diameter.

If the winding spindle drive 27 is formed by an asynchronous motor, the speed of the winding spindle is detected by a speed sensor (not shown here). The signal from the speed sensor is sent to control unit 34 given up. The control unit 34 now regulates the winding spindle speed to a constant value in an inner loop. The signal of the speed sensor 35, which detects the speed of the pressure roller, leads in an outer control loop to the fact that the winding spindle speed is changed.

The second winding spindle 15 is arranged eccentrically via a bearing 29 in the winding turret 11 and is driven by means of a winding spindle drive 28. The winding spindle drive 28 is currently deactivated because the winding spindle 15 is ready to exchange a full bobbin for an empty tube 18.

The winding turret 11 is rotatably mounted in the machine frame 9 of the winding machine and is driven in the direction of rotation 23 by the electric motor 40. The electric motor 40 is designed, for example, as an asynchronous motor. The electric motor 40 serves to rotate the winding turret 11 in the sense that the center distance between the pressure roller 5 and the winding spindle 14 is increased as the bobbin diameter increases. For this purpose, the electric motor 40 is frequency-controlled via an actuator 13, so that the winding turret 11 can execute any rotational speed in the direction of rotation 23. Here, however, in connection with a polarity reversal, a rotational movement counter to the direction of rotation 23 could also be given to the turret.

1, the pressure roller 5 is mounted on a rocker 8, so that the pressure roller can execute a movement in a radial component to the winding spindle 14. The rocker 8 is pivotally mounted on the machine frame 9 about the pivot axis 25. The pivot axis 25 is formed by a rubber block (not shown here). This rubber block is firmly clamped in the machine frame. The rocker arm 8 is attached to the rubber block, so that the rocker arm 8 can be pivoted elastically. This Rubber-elastic storage acts like a spring, which acts on the rocker 8 in the sense of increasing the contact pressure. By means of a relief device 12, which can be acted upon pneumatically and which acts from below against the weight on the rocker 8, the weight which bears on the pressure roller and thus as a contact force on the spool 17 can be compensated in whole or in part, so that a fine adjustment a basic value of the desired contact pressure between the contact roller and the coil surface is adjustable. The relief device 12 can be controlled via a control device 10. A position sensor 19 is arranged below the rocker 8. The position sensor 19 detects the stroke of the pressure roller 5 or the swivel angle of the rocker 8 relative to the machine frame 9. The sensor could therefore be designed as an angle sensor. The sensor 19 is connected to a control device 10. The control device 10 is also coupled to the control device 34 and the converter 13.

At the free end of the rocker 8, on which the pressure roller 5 is rotatably mounted, a force sensor 41 is arranged, which serves to detect the contact force between the pressure roller 5 and the spool 17. The force sensor 41 can be formed, for example, by strain gauges which detect the bearing load on the pressure roller.

The operation of the on dishwasher is described below.

The coil 17 is wound on the sleeve 16. As the bobbin diameter increases, the burr turret 11 is continuously moved in the direction of rotation 23 at a predetermined rotational speed. The rotational speed is controlled by the actuator 13 and the electric motor 40. For this purpose, the actuator 13 is connected to the control device 10. In the control device 10, the currently wound bobbin diameter is calculated on the basis of the rotational speeds of the pressure roller 5 given by the control unit 34 and the rotational speed of the winding spindle 14. From a master curve stored in the control device 10 between the bobbin diameter and the rotational speed of the bobbin turret, the associated rotational speed of the bobbin turret can be determined for the current bobbin diameter. The master curve is applied via an input 24 of the control device 10. The control device 10 outputs a corresponding control signal to the actuator 13, so that the electric motor 40 is operated at the specific rotational speed. If the speed of rotation of the winding turret is precisely adapted to the increase in diameter, the pressure roller 5 remains unchanged in its position. If the speed of rotation is too slow or the speed of rotation is too fast, the position of the pressure roller changes. This change in position is detected by the sensor 19. The sensor 19 leads its signal directly to the control device 10. The control device 10 now corrects the rotational speed so that the pressure roller is moved back into its new position. Thus, the set contact force between the pressure roller and the spool remains essentially unchanged.

With the help of the signals given by the control unit 34, the diameter increase per unit of time can also be calculated. It is therefore possible to adapt the predefined speed function to the actual diameter increase or to calculate it in advance. In this case, the control device 10 has a computing unit which carries out a continuous or step-by-step calculation of the diameter increase and determines a correction and pre-calculation of the speed function for moving the winding turret. This speed function is determined by the Control device 10 then taken as the basis for controlling the drive of the winding turret.

However, there is also the possibility of specifying a correspondingly programmed course of the winding trip to the control device in such a way that the pressure roller is deflected from its desired position in certain areas of the winding trip. For this purpose, a rotation speed is set on the winding turret that is smaller than the corresponding diameter increase. This procedure makes it possible to change the contact force between the pressure roller and the spool. By deflecting the pressure roller 5 from its position, the contact force will increase due to the geometric changes. The contact force is detected by means of the force sensor 41 and given to the control device. After a target-actual comparison, the speed of the evasive movement can thus be continuously corrected.

In particular in a winding machine according to FIGS. 1 and 2 with two winding spindles, the procedure for winding a thread shown in FIG. 3 has proven itself.

A speed function F _{v is shown} in a diagram in FIG. 3, the coil diameter D being plotted on the abscissa and the rotational speed of the turret v being plotted on the ordinate. The winding trip is essentially divided into three sections. The first section I is the winding area at the beginning of the winding trip. The second section II is the so-called transition area, and section III is the wikel area. The winding area I begins at a coil diameter D _j . D _{j ^} is the diameter of the empty tube. This means that the thread has just been caught on the empty tube and the winding travel begins. In this phase I the Revolver not turned. The speed function F _v shows zero speed. The winding spindle is thus fixed. The increase in diameter between D _j and D ₂ is absorbed by the evasive movement of the pressure roller. The pressure roller is thus pivoted evenly on the rocker 8 in this phase. After reaching the coil diameter D ₂ , the electric motor of the turret is activated. A steadily accelerated rotary movement is set on the winding turret. The speed function F _v increases linearly. It is thereby achieved that the pressure roller 5 is pivoted back very quickly into its starting position at the beginning of the winding cycle. This transition area II is thus passed through very quickly. The starting position of the pressure roller represents an optimal working point for the further course of the winding travel. At the end of the transition area, the winding diameter is D ₃ . Now the speed of rotation of the winding turret is no longer accelerated. The evasive movement of the winding spindle is now adapted to the diameter increase of the coil. The speed function F _v shows a course which is essentially proportional to the diameter increase, ie the speed of the winding turret decreases hyperbolically with increasing coil diameter. There is a uniform delay in the rotary movement of the winding turret, which is adapted to the increase in diameter. The winding cycle is finished with the maximum bobbin diameter D after reaching the full winding.

Then there is a change of thread from the wound full bobbin to an empty tube. For this purpose, the winding turret is pivoted at an increased rotational speed in such a way that the second winding spindle is pivoted into the thread path with an empty tube. The winding spindle with the empty tube was previously driven to the speed required for winding. As soon as the empty tube dips into the thread run with a catch slot, the thread is on the empty tube caught and tears between the full spool and the empty tube, so that the new winding process can begin.

A further diagram is shown in FIG. 4, the coil diameter D being plotted on the abscissa and the contact force P between the coil and the pressure roller on the ordinate. It can be seen here that the contact force in the winding area I initially increases linearly between the diameters D _j and D. Due to the evasive movement of the pressure roller, the relative position of the pressure roller to the spool changes continuously, so that the weight force of the pressure roller acting on the spool changes, in this case increases. With the simultaneous movement of the pressure roller and the winding turret, there is only a slight increase in the contact pressure in transition area II. In winding area III, an essentially constant contact force is then achieved by controlling the winding turret rotation speed. In winding area III, the speed function is determined by the specified contact force. When using a winding machine according to FIG. 1, the change in speed is not proportional to the increase in diameter, since the change in contact force must be compensated for due to the change in position of the winding spindle. This compensation can be done by step or steady change of position of the pressure roller, which is controlled by the speed of rotation of the winding turret.

The procedure - as described according to FIG. 3 - leads to the schematic positions shown in FIGS. 5 to 7 in a winding machine. The winding turret 11 is stationary in the winding area (FIG. 5). The winding spindle 14 thus remains in its position. The pressure roller 5 is therefore pivoted on the rocker 8 by an angle a until the spool diameter D is reached in the direction of movement 32, by the increasing spool diameter to dodge.

The diverter movement of the pressure roller can also be carried out, for example, by a drive (12) which engages the rocker.

After the rocker 8 has covered a maximum swivel angle o ^. ^, Which is given up by the sensor 19 of the control device 10, the rotary drive of the turret 11 is activated. Here, the control device 10 will control the rotary drive such that the winding turret is moved at a maximum accelerated speed until the pressure roller 5 has returned to its starting position (FIG. 6). In this phase, the winding turret has traveled the angle of rotation β _γ in the direction of rotation 23. After the pressure roller has reached its starting position and in the meantime the bobbin diameter has increased to D ₃ , the control device 10 controls the rotary drive of the bobbin turret 11 in such a way that a rotational speed which is dependent on the diameter increase is set on the bobbin turret. By the end of the winding cycle, the winding turret has traveled the angle of rotation β ₂ .

Due to the fact that the pressure roller and the coil are kept in constant circumferential contact, the respective position of the turret can be determined from the geometic relationships, both from the position of the pressure roller and the current coil diameter, or from the position of the turret and the current diameter of the Determine the position of the pressure roller. A position sensor can therefore also be attached to the turret, which detects the angular position of the turret and gives it to the control device. In this case, the position sensor on the rocker arm of the pressure roller can be omitted. The evasive movement can also be controlled solely by determining the position of the pressure roller and the winding spindle, since each layer defines a coil diameter. In this case, the control device is connected to a position sensor for the pressure roller and to a position sensor for the winding turret. The current coil diameter and the diameter increase are determined from the sensor signals. The increase in diameter then leads from a stored master curve to the speed of the evasive movement to be set.

The method according to the invention can not only be carried out by a winding machine described in accordance with FIGS. 1 and 2, but can also be carried out advantageously by dishwashers with only one winding spindle. The winding spindle is mounted on a movable carrier. The carrier of the winding spindle is coupled to an inverter-controlled drive. The carrier can be designed as a rocker arm, which is supported on one side on the machine frame.

Likewise, the carrier of the winding spindle or the pressure roller can be designed as a linear guide, in which a carriage is driven by a linear drive.

In particular, the method according to the invention is also suitable for changing the contact force solely by changing the rotational speeds of the carrier of the winding spindle or winding turret. The contact force acting between the pressure roller and the spool results from the weight of the pressure roller. 8 shows the force ratio between the pressure roller 5 and the spool 17. The weight of the pressure roller is designated G, which has a vertical direction of action. The investment power P, which acts between the pressure roller and the spool 17, has the connecting line between the axis center point M _{A of} the pressure roller and the axis center point M _{s of} the winding spindle as the direction of action. The coil 17 has the diameter D _j in this phase. The coil 17 now grows from the diameter D to the diameter D ₂ in the course of the winding cycle. The position of the winding spindle is not changed. Here, the axis center point M _{A of} the pressure roller will move on a circular guideway F _A , the center of which is formed by the axis center point M _{τ of} the pivot axis of the carrier or the rocker. The carrier or the rocker of the pressure roller is thus shifted by the angle. Since the weight G of the pressure roller remains unchanged, a contact force P _α acting between the pressure roller 5 and the spool 17 will result due to the changed angular position. The winding machine according to the invention thus offers the possibility of setting a contact force which is desirable for the formation of the bobbin simply by changing the position of the pressure roller. The weight G of the pressure roller could be increased or relieved by a force sensor as required by a constant value. If a contact force desired for the bobbin build-up is set by changing the position of the pressure roller, the pressure roller is then held in position by moving the winding spindle away by means of the winding turret.

For example, in order to obtain a change in the contact force caused by the speed of the winding turret in the winding area, there is the possibility of stopping or slowing down the speed of the winding turret for a short time, so that the increase in diameter leads to a change in position of the pressure roller. As soon as the position of the pressure roller required for the contact force is reached, the speed of the winding turret is increased to the value proportional to the diameter increase. It is the same possible to increase the speed of the winding turret so that it is greater than the speed required for the diameter increase. In this phase, the pressure roller is deflected in the opposite direction. As soon as the desired contact force between the pressure roller and the bobbin is reached, the speed is set again to the value proportional to the diameter increase. This results in a high flexibility in the construction of the coil.

A constant regulation of the rotational speed of the carrier or of the winding turret could also take place in that a sensor detects the speed of the evasive movement and gives it up to the control device as the actual value. A constant correction of the speed can thus be carried out in the control device on the basis of an actual-target comparison.

The inventive method can also be used advantageously to change the thread wrap on the pressure roller during a winding trip. For this purpose, the pressure roller is shown in two different positions in FIG. 9. The pressure roller can for example be guided by a rocker which is rotatably mounted in the pivot axis MT. In the lowest position of the pressure roller, a coil with the diameter O _{1 is} wound on the winding spindle. In the upper position of the pressure roller, the bobbin on the winding spindle has grown to the diameter D ₂ .

The pressure roller and the winding spindle are in relation to the thread run in such a way that a thread 1 running onto the surface line of the pressure roller is only placed on the surface of the bobbin to be wound after partial wrap on the pressure roller. The looping area of the thread 1 on the pressure roller is characterized by the angle γ. This part length the extent is also known as the so-called print length. The print length has a significant influence on the spool structure. In order to achieve an undisturbed spool build-up, a minimum print length is required on the pressure roller.

In Fig. 9 the wrap angle of the pressure roller at the lower position is marked with y ^. In contrast, the wrap angle in the upper position of the pressure roller is designated by y ₂ , the wrap angle y _{2 being} smaller than the wrap angle y _λ . The print length can thus be influenced solely by changing the position of the pressure roller. In particular in the case of a winding spindle guided on a winding turret, the print length will increase as the center distance between the winding spindle and the pressure roller increases. Such a change in the print length can be compensated for by changing the position of the pressure roller in the meantime. With this, the speed of the winding turret can also be determined as a function of a print length to be maintained on the pressure roller.

The method according to the invention can also advantageously be used with a winding machine which has a stationary pressure roller and a winding spindle mounted on a movable carrier. Here, the position of the wearer is sensed and given to a control device. The control device will then determine the current bobbin diameter and thus the increase in diameter from the rotational speeds of the pressure roller and the bobbin spindle and control the drive of the bobbin spindle carrier in such a way that the carrier carries out an evasive movement at a defined speed. LIST OF REFERENCE NUMBERS

thread

Head thread guide

wing

Guideline

Pressure roller

Traverse drive

carrier

wing

Machine frame

Control device

Winding turret

Relief device

Converter

Winding spindle

Bobbin

Kitchen sink

Bobbin

Position sensor

camp

Frequency transmitter

Sense of rotation

entrance

swivel axis axis

Winding spindle drive

Spindle bearing

Kitchen sink

Direction of movement

control unit

Speed sensor

Electric motor

Force sensor

Claims

PATENT CLAIMS

1. A method for winding a continuously running thread into a bobbin, in which the bobbin is formed on a driven bobbin spindle, which is cantilevered on a movable carrier, in which a pressure roller mounted on a second movable carrier with a by the position of the pressure roller relative to Coil changeable contact force is applied to the circumference of the coil and at which a required by the diameter increase of the coil

The axis distance between the bobbin and the pressure roller is changed by an evasive movement of the pressure roller or by an evasive movement of the winding spindle as a function of the growing bobbin diameter, characterized in that the evasive movement of the winding spindle is controlled during the winding travel according to a predetermined speed function (F _v ), which assigns a certain speed (v) to the evasive movement in the course of the winding cycle to each bobbin diameter (D).

2. The method according to claim 1, characterized in that the determined by the speed function (F _v ) speed (v) is proportional to the diameter increase of the coil during the winding trip, so that the coil grows with the position of the pressure roller substantially unchanged.

3. The method according to claim 1, characterized in that the speed ( _v ) determined by the speed function (F _v ) is not proportional to the diameter increase of the bobbin during the bobbin travel, so that the bobbin grows with a changed position of the pressure roller.

4. The method according to any one of claims 1 to 3, characterized in that the speed ( _v ) determined by the speed function (F _v ) is proportional or not proportional to the diameter increase of the bobbin during the winding travel within partial regions of the winding travel.

5. The method according to any one of the preceding claims, characterized in that the control of the evasive movement of the winding spindle takes place during the winding travel as a function of a winding time.

6. The method according to any one of claims 1 to 4, characterized in that the control of the evasive movement of the winding spindle takes place during the winding travel as a function of the bobbin diameter.

7. The method according to claim 6, characterized in that the coil diameter is detected by the position of the support of the pressure roller and / or the position of the support of the winding spindle.

8. The method according to claim 6, characterized in that the coil diameter is determined by the speed ratio of the speed of the pressure roller and the speed of the winding spindle.

9. The method according to any one of claims 1 to 8, characterized in that the speed (v) of the evasive movement from a parameter determining the temporal diameter increase of the coil (K) and the coil diameter (D) as a function of the winding time or

Coil diameter is calculated in advance.

10. The method according to claim 9, characterized in that the parameter (K) during the winding travel with the carrier stationary

Winding spindle is determined.

11. The method according to any one of claims 1 to 8, characterized in that the speed (v) of the evasive movement from a temporal

Diameter increase of the bobbin determining parameter (K), the bobbin diameter (D) and the position of the pressure roller (a) as a function of the winding time or the bobbin diameter is predetermined.

12. The method according to claim 11, characterized in that the parameter and the contact force between the pressure roller and the The bobbin is determined as a function of the position of the pressure roller relative to the bobbin during the bobbin travel with the bobbin spindle carrier stationary.

13. The method according to any one of claims 1 to 12 or the preamble of claim 1, in which the carrier of the winding spindle is formed by a winding turret with a second winding spindle, characterized in that in a winding area at the beginning of the winding trip the pressure roller from an initial position fixed carrier of the winding spindle is moved, that in a transition area the pressure roller and the winding spindle are moved together at a steadily accelerated speed until the pressure roller has reached their starting position before the start of the winding travel and that in a winding area the winding spindle moves away by the winding turret according to a predetermined speed function which assigns a certain speed of the evasive movement to each bobbin diameter in the course of the winding travel.

14. The method according to claim 13, characterized in that the actual values of the contact force are determined as a function of the position of the pressure roller during the winding travel within the application area and that the speed of the winding turret in

Dependence on a comparison between the actual value of the investment force and the target value of the investment force specified by a profile is changed.

15. The method according to claim 13 or 14, characterized in that the function of the speed of the winding turret for the winding area is calculated in advance from the winding parameters determined during the winding travel within the winding area.

16. The method according to any one of claims 1 to 15, characterized in that the evasive movement of the winding spindle is carried out with a variable-speed drive of the carrier of the winding spindle.

17. On dishwasher for carrying out the method according to one of claims 1 to 16 with a traversing device, with a pressure roller (5) mounted on a support (8) movable to the machine frame, with a winding spindle (14) cantilevered on a rotatable winding turret (11) ), with a drive (40) for the winding turret (11) and with a control device (10) for controlling an evasive movement of the winding spindle (14) as a function of the diameter increase of the coil, characterized in that

the control device (10) has an input (24) for inputting a speed function which, in the course of the winding travel, assigns a specific speed to the evasive movement of each coil diameter, and that the control device (10) with a control device (34) for determining the coil diameter or Winding time is connected, so that the variable speed drive (40) of the turret (11) through the control device (10) can be controlled in accordance with the speed function.

18. On dishwasher according to claim 17, characterized in that a position sensor (19) for detecting the position of the carrier (8) of the pressure roller (5) or the turret (11) is connected to the control device (10).

19. On dishwasher according to claim 18, characterized in that the carrier is designed as a rocker arm (8) mounted on one side on the machine frame and that the position sensor (19) is designed as an angle sensor which detects the swivel angle of the rocker arm (8).

20. Winding machine according to one of claims 17 to 19, characterized in that the control device (10) has a computing unit which from the winding parameters supplied by the control unit (34)

Speed function for controlling the winding turret speed calculated.

21. On dishwasher according to one of claims 17 to 20, characterized in that the control device (10) is connected to a force sensor (41) for detecting the contact force between the pressure roller and the spool and a storage unit for storing the actual values of the contact force in Depends on the position of the carrier of the pressure roller.

22. On dishwasher according to one of claims 17 to 22, characterized in that the carrier (8) of the pressure roller (5) has a drive (12) which can be controlled via the control device (10).