EP0200234B1 - Spulendorn-Antrieb - Google Patents

Spulendorn-Antrieb Download PDF

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Publication number
EP0200234B1
EP0200234B1 EP86106332A EP86106332A EP0200234B1 EP 0200234 B1 EP0200234 B1 EP 0200234B1 EP 86106332 A EP86106332 A EP 86106332A EP 86106332 A EP86106332 A EP 86106332A EP 0200234 B1 EP0200234 B1 EP 0200234B1
Authority
EP
European Patent Office
Prior art keywords
package
speed
thread
setting
friction roll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86106332A
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German (de)
English (en)
French (fr)
Other versions
EP0200234A2 (de
EP0200234A3 (en
Inventor
Werner Nabulon
Armin Wirz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Maschinenfabrik Rieter AG
Original Assignee
Maschinenfabrik Rieter AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Maschinenfabrik Rieter AG filed Critical Maschinenfabrik Rieter AG
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Publication of EP0200234A3 publication Critical patent/EP0200234A3/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/40—Arrangements for rotating packages
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/40—Arrangements for rotating packages
    • B65H54/52—Drive contact pressure control, e.g. pressing arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
    • B65H59/38—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators by regulating speed of driving mechanism of unwinding, paying-out, forwarding, winding, or depositing devices, e.g. automatically in response to variations in tension
    • B65H59/384—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators by regulating speed of driving mechanism of unwinding, paying-out, forwarding, winding, or depositing devices, e.g. automatically in response to variations in tension using electronic means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments

Definitions

  • the present invention relates to a machine for winding film material in coil packages.
  • the film material can be a synthetic plastic material, such as e.g. Polyester, polyamide or polypropylene.
  • the film material can be monofilament or multifilament, both types being referred to below as "thread".
  • FR-1 195 598 describes a winding machine in which a synchronous motor drives the delivery rollers at a speed proportional to the frequency.
  • a second synchronous motor drives the friction roller on the take-up spool.
  • the coil itself is driven by a load-dependent asynchronous motor in such a way that the forces arising from its own torque at the point of contact with the friction roller are smaller than the frictional forces at the point of contact. The only thing left to do is to transfer and compensate for a small differential friction torque.
  • the present invention relates to a winder for winding thread onto a bobbin package according to claim 1, which is delimited with respect to US-A 4,307,848.
  • coil package includes the coil sleeve if one is used.
  • the regulating means can be used to regulate the circumferential force that occurs between the friction roller and a coil pack in contact therewith.
  • the regulating means are preferably adjustable in such a way that such a circumferential force can be selectively adjusted.
  • this motor can be regulated in such a way that it delivers a regulated drive torque (with certain restrictions depending on the motor design used), regardless of the speed of the distributor roller, which is separated separately by means of feedback with inclusion the contact between the distributor roller and the bobbin pack is regulated when the regulating means are set for normal winding operation.
  • the regulating system can regulate the drive means for the bobbin mandrel in such a way that the rotational speed is adapted to the rotational speed of the friction roller when the first contact between the bobbin pack and the roller occurs.
  • the regulating system can also be set up to regulate the rotation speed of the spool mandrel in a predetermined manner during assembly of the spool pack before the spool pack comes into contact with the rubbing roller. Normally, the speed of rotation of the bobbin mandrel is regulated in such a way that the tangential speed at the circumference of the bobbin pack is equal to or slightly higher than the thread running speed.
  • the feedback signal from the friction roller for regulating the drive means for the coil mandrel is preferably a signal that corresponds to the peripheral speed of the roller. Since the diameter of the roller remains constant over the entire winding process, the rotational speed of the roller corresponds to its peripheral speed multiplied by a constant factor.
  • the signal can be taken from a tachometer generator assigned to the friction roller. Since the drive for the bobbin pack is derived both from the drive means for the bobbin mandrel and from the drive means for the friction roller, the slip between the roller and the bobbin package can be eliminated so that the feedback signal, which corresponds to the peripheral speed of the friction roller, simultaneously corresponds to the peripheral speed of the package.
  • the winding machine can include a substantially conventional traverse device for reciprocating the thread along the axis of the bobbin mandrel to enable the package to be built up.
  • the machine can also be equipped with a conventional threading device, which allows the thread to be placed on a rotating spool at the start of the process.
  • the bobbin mandrel can be constructed in a generally customary manner and can be provided with thread catching means which catch a thread placed thereon and separate it from the retracting means.
  • FIG. 1 shows the machine during a winding process
  • Figure 2 shows the parked machine.
  • the machine comprises a frame and housing part ("frame") 10 on and in which the other parts are mounted.
  • a side wall of the housing is omitted in Fig. 2 to make the inside of the housing visible.
  • a spool mandrel 12 is mounted on a carriage 14 so that it projects in front of the front of the machine.
  • the spool mandrel 12 is mounted on the carriage 14 in such a way that it can rotate about its longitudinal mandrel axis 16, the rotation being driven by an electric motor 18 which is also mounted on the carriage 14.
  • the motor 18 is designed as an asynchronous motor.
  • the carriage is movably mounted on guides 15 on the frame 10 and follows the expansion and retraction of movement means which are actuated by means of a fluid, such as e.g. a piston and cylinder unit (not shown).
  • a fluid such as e.g. a piston and cylinder unit (not shown).
  • the carriage thus moves the mandrel 12 towards and away from a friction roller 20.
  • the latter is attached to the frame 10 so that it can rotate about its longitudinal axis 22, the roller axis 22 being fixed relative to the frame 10.
  • the roller 20 is driven by an electric asynchronous motor 24 for rotation, which is fixed to the frame and drives the roller via a drive shaft 23.
  • the roller 20 can be designed as an external rotor motor with a stator fixedly attached to the frame, the rotor surrounding the stator. Motors of this type are known in winding machines.
  • the spool mandrel 12 moves towards and away from the roller 20, the axis 16 moves along the movement path 26 according to FIG. 1.
  • the spool mandrel is located in a rest position (also shown in Fig. 2).
  • a sleeve clamping device (not shown) of conventional design can be incorporated into the spool mandrel construction 12, for clamping / releasing a bobbin tube 28, on which bobbin tube thread turns 30 are formed and during the bobbin winding process are built up into a package.
  • the winding machine corresponds to the "print friction” type, in which the thread 32 runs over part of the circumference of the friction roller 20 before it passes from the roller into the thread turns 30.
  • the operator passes the thread 32 around the roller 20.
  • the operator places the thread on the spool mandrel 12 where the thread is captured by a conventional thread catching and separating mechanism 34 (FIG. 2) and placed on the bobbin tube 28, whereupon thread turns begin to form on the bobbin tube.
  • the thread is moved back and forth along the bobbin mandrel axis 16 by means of a conventional traversing mechanism 36 (FIG. 1), which is provided in front of the friction roller 20.
  • a conventional traversing mechanism 36 FIG. 1
  • the machine can also be equipped with a conventional threading device for automatically threading the thread onto the spool mandrel 12, e.g. in U.S. Patent 4,136,834.
  • Conventional devices can also be provided for applying reserve turns on the bobbin tube 28 before the winding of the main thread turns begins, these reserve turns serving to enable one package to be tied to another during further processing of the thread.
  • the bobbin mandrel 12 Immediately after completion of the pulling-in process, the bobbin mandrel 12 remains in its position at the end of the movement path 26 closest to the friction roller 20. This state is shown in solid lines in FIG. 3 and shows that there is still a distance S between the circumference of the thread turns 30, which are already built on the coil sleeve 28 and the circumference of the friction roller 20 remains. The radial thickness of the thread turns created at this stage is exaggerated in Figure 3 for clarity. The distance S is determined by the position of a stop 40 (FIG. 2) against which the carriage 14 bears at the end of the guide 15. Because of the distance S, a piece of thread L extends freely between the rubbing roller 20 and the thread turns 30 applied during this phase of the winding process. At this time, the friction roller 20 is driven by the motor 24 so that the peripheral speed of the roller is the same as the thread running speed required for the production of the thread.
  • the rotating coil mandrel 12 remains at the upper end position of its movement path 26 without moving, as shown in FIG. 3, until the coil package has built up sufficiently and bridges the distance S, so that the coil package comes into contact with the circumference of the friction roller 20 (as shown in FIG. 3 with dashed lines). From this phase onwards, the further coil pack construction is accompanied by a backward movement of the coil mandrel along its path of movement 26 against its rest position shown in FIG. This movement takes place under the influence of the carriage moving means in such a way that a controlled contact pressure is maintained between the surface of the coil package and the surface of the roller, as is known in the prior art.
  • FIG. 4 A control system for regulating the wind-up speed during a normal wind-up process is shown in FIG. 4, while FIG. 5 shows the system in the start-up phase.
  • the setting for the initial phase is maintained from the moment in which the thread is placed on the spool to the moment in which the thread turns 30 and the rubbing roller 20 are in contact.
  • the regulating system is switched to the setting for normal wind-up operation, as shown in FIG. 4. This setting is maintained until the thread turns have reached the desired diameter, at which point the winding process is stopped, either by responding to automatic thread length measuring means which measure the length of the wound thread, e.g. by comparing the coil package diameter, or by responding to manual actuation of a stop button.
  • the carriage 14 then quickly moves the spool mandrel 12 to the rest position, where the rotation of the spool mandrel is brought to a standstill and the clamping means are released, so that the full spool package can be removed and replaced by an empty spool sleeve.
  • the winding cycle can then be repeated.
  • the regulating system comprises a tacho generator 42, which is coupled to the rotor or the drive shaft 23 (FIG. 2) of the roller 20, a tacho generator 44, which is coupled to the drive shaft of the spool mandrel 13, an inverter 46 for feeding of the friction roller motor 24, an inverter 48 for feeding the mandrel motor 18, a regulator 50 for regulating the output of the inverter 46, a regulator 52 for regulating the output of the inverter 48, a setting device 54 for setting the output of the inverter 46, a setting device for setting a setting value for the regulator 52, an auxiliary setting device 58 and a timer 60 for a purpose to be described later.
  • the regulator 52 receives the output of its setting device 56 and also the output of the tachometer generator 42.
  • the regulator 52 compares the inputs coming from the setting device 56 and from the generator 42 and supplies an output signal to the inverter 48, which depends on this comparison.
  • the inverter 48 provides appropriate input to the motor 18 to regulate the rotational speed of the latter. Assuming that there is no slippage in the contact zone between the thread layers 30 and the roller 20, the tangential speed of the thread windings in the contact zone is the same as the tangential speed of the roller 20. Since the diameter of the roller is constant during the entire winding process remains, this speed is given directly by the output signal of the tachometer generator 42.
  • the regulator 52 intervenes via the inverter 48 in order to keep the output signal of the generator 42 constant at a setpoint value set on the setting device 56, i.e. the regulator 52 keeps the rotational speed of the friction roller 20 constant over this part of the winding process, above which the switching state of the circuit shown in FIG. 4 applies.
  • the regulator 52 keeps the rotational speed of the friction roller 20 constant over this part of the winding process, above which the switching state of the circuit shown in FIG. 4 applies.
  • the tacho generator 44, the device 58 and the timer 60 do not yet play a role in the control process.
  • the motor 24 meanwhile receives an input from its own inverter 46.
  • This input is determined directly by the adjusting device 54, which for this purpose is directly connected to the inverter 46, bypassing the regulator 50.
  • the influence of the adjustment of the setting of the device 54 can be seen from the diagram of FIG. 6, which is only shown for explanation and does not necessarily represent the preferred arrangement which will be described below.
  • the curve shown in solid lines in FIG. 6 represents the typical output speed N (ordinate) versus the output torque M (abscissa) for the motor 24.
  • the setting device 54 determines the synchronous speed at which the characteristic intersects the vertical axis. In the "no load" state, ie if the motor 24 were driven by the inverter 46, as shown in FIG.
  • the motor 24 would drive the roller at the speed N A and that Drive output torque M A.
  • N B the speed through the feedback pelungsschleife via the tachometer generator 42, regulator 52, inverter 48, motor 18 and the coil pack being built up on the spool mandrel 12 is determined.
  • the drive torque M B - M A acts on the reel pack from the roller and depends on the adjusting device 54.
  • the motor characteristic is shifted upward, for example to the dashed curve in FIG. 6.
  • the drive torque M A "without load” remains the same, but assuming it If there is no change in the required rotational speed N B , the drive torque of the motor increases under load to the value M B1 , so that the motor 24 transmits an additional tangential force to the circumference of the coil pack.
  • the electrical slip in the motor changes accordingly.
  • the adjustment device 54 can be designed such that any tangential force required can be exerted on the circumference of the coil package within certain physical limits. These limits result in part from the conditions in the contact zone where, for example, a very large circumferential force exerted by the roller on the package of coils simply leads to slippage between these elements, thereby failing to achieve the purpose of the feedback loop. The limits also result from the design of the motor 24, which is chosen for a particular machine. The permissible electrical slip in a given motor depends on the motor design and limits the drive torque range that can be achieved with this motor. Within the given limits, the setting of the device 54 can be adjusted according to practical requirements. The adjustment device 54 can be adjusted so that the motor 24 does not transmit any tangential force to the coil package.
  • the adjuster 54 could also be adjusted so that the roller 20 brakes the package of coils or transmits a tangential or circumferential force that changes in a predetermined manner during the normal winding process.
  • the control system is in this setting from the beginning of a winding cycle (ie from the moment the bobbin mandrel leaves its rest position) over the entire phase, during which there is a distance S (FIG. 3) between the thread turns 30 and the roller Contact between the thread turns 30 and the roller takes place.
  • the step of changing the setting according to FIG. 5 to that according to FIG. 4 will be described in more detail later. 5, the inverter 46 receives its drive input from the regulator 50, and the setting device does not perform any control function.
  • the output signal of the tachometer generator 42 now goes to the regulator 50, which also receives a setting input from the setting device 56.
  • the roller 20 is therefore driven by the motor 24 according to the speed set on the adjusting device 56.
  • the speed of rotation of the motor 18 can of course not be regulated in accordance with the output signal from the generator 42 since there is no contact between the coil package and the roller 20.
  • the regulator 52 therefore receives a signal from the tachometer generator 44, which measures the rotational speed of the motor 18 directly.
  • the setting signal for the regulator 52 is not derived directly from the setting device 56; the reasons for this are explained below using the diagram in FIG. 7.
  • the tangential speed at the circumference of the coil pack (vertical axis) and the coil pack diameter d (horizontal axis) are related.
  • the vertical axis is set at the coil diameter d, which essentially corresponds to the outside diameter of the coil sleeve 28.
  • a vertical line appears in the diagram at the bobbin pack diameter D, at which contact occurs between the bobbin pack and the roll circumference of the roll 20.
  • the following consideration applies to the circumferential speed of the coil pack during the coil build-up from diameter d to D.
  • the design could be chosen so that this speed follows the line SP 1, which can be achieved if a suitable constant setting value from the setting device 56 to the regulator 52 is given. If this design is chosen, the peripheral speeds of the package and the roller are the same when they touch each other (intersection of lines SP 1 and SR at package diameter D). However, the circumferential speed of the coil pack at diameter d is below the value SR by an amount X, which depends on the difference D-d and the angular speed to be set for motor 18 in order to reach the circumferential speed SR at coil pack diameter D.
  • the speed SR of the distribution roller should be equal to the linear thread running speed.
  • the lower peripheral speed of the package at diameter d is associated with a drop in the thread tension in the thread piece of length L between the friction roller 20 and the thread turns 30 (FIG. 3). If this drop in thread tension is too great, poor thread turns result in this initial area of the package. This in turn leads to difficulties in pulling the thread off the package during further processing.
  • the peripheral speed could be guided in such a way that it follows line SP 2, likewise by inputting a constant setting value to the control circuit of the motor 18 during this start-up phase.
  • the peripheral speed of the package would already correspond to the thread travel speed at the package diameter d .
  • the circumferential speed of the package would, however, exceed the thread running speed by an amount Y with the package diameter D. If the amount Y is too large, the system will be hit at the moment the thread turns touch the roller 20.
  • the change in the output signal of the generator 42 due to the impact together with the switching of the system to the setting for the normal winding process according to FIG. 4, result in vibrations in one or both feedback loops according to FIGS. 4 and 5. These vibrations cause a build-up in the control loops and can even lead to their instability.
  • the bobbin pack speed at the bobbin pack diameter d is somewhat higher than the thread running speed, but it decreases and when the bobbin pack diameter D is reached it becomes essentially the same size as the thread running speed and the peripheral speed of the roller 20.
  • the characteristic 3 cannot be achieved by specifying a constant setting value at the regulator 52; this value must be changed continuously over the phase during which the package diameter increases from d to D, and the auxiliary adjuster 58 is used for this purpose.
  • the device 58 responds to a timer 60 which is started upon receipt of a signal at the input 62 and counts “downwards". This start signal is provided at the point in time at which the thread begins to wind onto the bobbin tube 28, i.e. at the bobbin pack diameter d, and e.g. come from the thread pulling system that the transfer of the thread signals from the system to the spool.
  • the timer 60 is set to count down at a predetermined rate over a period of time corresponding to the time required for the package build from diameter d to diameter D; this period of time must be determined depending on the operating conditions, including the thread speed, the initial distance between the package and the roll 20, the thread count (titer) and the package length (stroke).
  • the timer 60 outputs an output signal to the setting device 58 which contains stored data which represent a sequence of setting values for the regulator 52.
  • the device 58 outputs successive values of the sequence depending on the count signals received from the timer 60.
  • the setting values provided to the regulator 52 regulate the speed of rotation of the motor 18, which speed gradually decreases as the package diameter increases.
  • the final setting value of the sequence stored in the device 58 must bring about a rotational speed of the motor 18, which results in a circumferential speed of the coil package when the coil diameter D is reached which is equal to or, if possible, equal to SR; this value is therefore related to the value output by the setting device 56, which can be coupled to the device 58, as shown in FIG. 5.
  • Device 58 may include a range of data, only a portion of which is required under given conditions, the range of the selected data sequence depending on the setting entered on device 56.
  • the data stored in the device 58 should also allow different initial diameters "d" to be taken into account, since the coil sleeve and coil mandrel diameters can differ depending on the respective boundary conditions.
  • the starting point in the sequence should therefore also be adjustable independently of the regulator 56 and the timer 60.
  • the characteristics recorded in FIG. 7 represent "idealized" operations. Since there is no feedback from the scope of the coil pack, it must be assumed that the coil pack really builds up as expected during this start-up phase - direct control only affects the speed of rotation of the motor 18. Accordingly, the startup phase is preferably kept short, i.e. the distance S is kept small, so that the feedback loop is effective as soon as possible from the circumference of the coil package.
  • a circumferential speed of the package that is lower than the thread running speed may be permissible under certain circumstances, and the characteristic SP 4 shown in broken lines may be permissible in this case.
  • can adjust the speed during the start-up phase can also be carried out discontinuously, i.e. not continuously, as shown in the diagram.
  • peripheral speed of the distribution roller is kept constant (on the required thread running speed) from the beginning to the end of the entire winding process, ie in both settings of the control system according to FIGS. 4 and 5.
  • This presupposes that the Motor 24 must run at the same speed both under load (FIG. 4) and "without load” (FIG. 5), as was discussed above with reference to the illustration in FIG. 6, ie N A N B.
  • the motor design must allow adequate settings, ie adequate supply from inverter 46. In terms of electrical properties, the motor must be able to operate over a sufficiently large range of electrical slip to be able to cover the intended load and non-load cases.
  • the device 54 can be designed to add only a predetermined correction factor to a setting input on the setting device. This design is shown schematically with the dashed connecting line in Fig. 4. On the other hand, it is not critical that the adjuster 56 be coupled to the device 58, as shown in FIG. 5. The two devices can be set independently.
  • the timer 60 is preferably adjustable so that different counting speeds and different counting times can be set.
  • the device 58 can be programmable to enable adaptations of the changeable sequence depending on various operating factors.
  • the control system can be designed so that it is automatically switched to the setting for the start-up phase as soon as the spool mandrel 12 arrives in its rest position, e.g. in response to a signal from a position sensor 62 (FIG. 2).
  • the control system is then in the start phase setting while the spool is moving along its path of travel 26 and while the motor 18 is accelerating to its "approach" speed before the thread is put on.
  • the circuits shown can be coupled to conventional start-up circuits (not shown) which cause the regulator 52 to drive the motor 18 to the required "start-up" speed, i.e. the speed chosen for the package diameter d.
  • the control system remains in the setting for the start-up phase (circuit state according to FIG.
  • the sensor 64 is, for example, an electrical switch that responds to very small movements of the carriage 14 in the return direction and actuates a relay, which in turn effects the switching of the switching state. This inevitably creates a slight delay between the contact between the coil pack and the roller and the switching of the switching state of the regulating circuit. This delay is preferably kept as short as possible.
  • the initial distance S (FIG. 3) is preferably kept as small as possible, the risk of contact between the coil pack and the roller due to actuation of the cylinder means 17 actuated by means of pressurized fluid being avoided.
  • a distance of 1 mm is usually sufficient in practical operation; the distance shown in Fig. 3 is shown exaggerated for clarity.
  • the spool mandrel axis 16 is preferably held at the end of its path of movement 26 while the spool pack builds up over this initial distance S.
  • the present invention is not restricted to a feedback signal generated by means of a tachometer generator.
  • Other systems with a feedback signal are known which represent the peripheral speed of a roller contacting a driven package.
  • a tachometer generator is a convenient and economical means of generating the required signal.
  • the timer 60 and the device 58 it was assumed that the timer was a digital counter and that the values stored in the device 58 were in the form of a sequence of discrete setting values.
  • the device can be adjusted so that it functions as an analog device, for example by gradually adjusting a potentiometer whose output voltage represents the input value for the regulator 52.
  • the start signal for the timer which reaches input 62 (FIG. 5), is best taken from the thread pulling system.
  • Such systems usually include one or more thread guides, which are set up in such a way that they carry out a predeterminable movement around the circumference of the spool in order to place the thread on the spool.
  • the movement force for this movement can be controlled manually or automatically.
  • the start signal can be generated automatically during a predetermined phase of the movement sequence of the thread guide, for example when such a movement is completed.
  • the system according to the invention has been described for a "print-friction" winding machine. It can also be used on winding machines in which the thread comes directly onto the package, i.e. without, or without substantial wrap angle of the thread on the distribution roller. In this case, the speed of the friction roller has no direct influence on the thread running speed as in the "print friction" winding. However, the requirements for speed adjustment to avoid the creation of instabilities in the control system remain.
  • the system has also been described for winding machines which have only one spool 12 and in which the winding process is temporarily stopped while the spool returns to its rest position, full bobbin packs are removed and new bobbin sleeves are fitted.
  • the present invention is not limited to application to machines of this type. Machines with multiple mandrels which are brought into a winding position one after the other and which allow winding to be wound up essentially without waste are already known, and the present invention is also applicable to such machines.
  • the present invention can be applied to the winding machine described in European Patent Application No. 73 930 (No. 82107022.4 filed on Aug. 04, 1982).
  • a winding machine is shown in a highly schematic representation, in which the friction roller is moved relative to a fixed spool.
  • the reference numerals of Fig. 8 correspond as far as possible to those used in Fig. 1.
  • the roller 20A and a traversing device 36A are mounted on a carriage 62 which can be moved vertically up and down on a spool mandrel 12A.
  • the axis 16A of the latter is fixed with respect to the frame 10A.
  • a stop (not shown), which corresponds to the stop 40 of FIG. 2, holds the carriage 62 in such a position that a distance remains between the roller 20A and a bobbin tube fitted on the bobbin mandrel of 12A. No differences are required in the electrical circuit diagram, so that no further explanation is necessary.
  • Regulators 42 through and 62 shown in Figures 4 and 5, have been treated collectively as “regulators” which can be switched in response to a switch that occurs when contact occurs between the bobbin pack and the friction roller, wherein control elements 42, 46, 48, 52 and at most 56 can be used together for both regulation settings.
  • control elements 42, 46, 48, 52 and at most 56 can be used together for both regulation settings.

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  • Winding Filamentary Materials (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
EP86106332A 1982-05-17 1983-03-14 Spulendorn-Antrieb Expired EP0200234B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/379,134 US4548366A (en) 1982-05-17 1982-05-17 Chuck drive system
US379134 1982-05-17

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP83102495.5 Division 1983-03-14

Publications (3)

Publication Number Publication Date
EP0200234A2 EP0200234A2 (de) 1986-11-05
EP0200234A3 EP0200234A3 (en) 1987-09-30
EP0200234B1 true EP0200234B1 (de) 1989-10-11

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EP86106332A Expired EP0200234B1 (de) 1982-05-17 1983-03-14 Spulendorn-Antrieb
EP85115378A Expired - Lifetime EP0182389B1 (de) 1982-05-17 1983-03-14 Spulendorn-Antrieb
EP83102495A Expired EP0094483B1 (de) 1982-05-17 1983-03-14 Spulendorn-Antrieb

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EP85115378A Expired - Lifetime EP0182389B1 (de) 1982-05-17 1983-03-14 Spulendorn-Antrieb
EP83102495A Expired EP0094483B1 (de) 1982-05-17 1983-03-14 Spulendorn-Antrieb

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IT1198061B (it) * 1986-10-22 1988-12-21 Savio Spa Apparecchiatura e procedimento per la regolazione dei comandi di azionamento nell'avvolgitura di fili in macchine tessili
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US5100072A (en) * 1990-06-06 1992-03-31 Barmag Ag Yarn winding apparatus and method
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EP0580548A1 (de) * 1992-07-23 1994-01-26 Maschinenfabrik Rieter Ag Verfahren und Vorrichtung zum Aufspulen eines Fadens
US5605294A (en) * 1993-03-15 1997-02-25 Toray Engineering Co., Ltd. Method for controlling the drive of a yarn winder, and the yarn winder thereof
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Publication number Publication date
JPH05319691A (ja) 1993-12-03
EP0094483B1 (de) 1987-09-02
EP0200234A2 (de) 1986-11-05
EP0182389B1 (de) 1990-09-19
JP2694167B2 (ja) 1997-12-24
JP2514493B2 (ja) 1996-07-10
EP0094483A1 (de) 1983-11-23
DE3373298D1 (en) 1987-10-08
EP0200234A3 (en) 1987-09-30
JPH07106828B2 (ja) 1995-11-15
JPH05278938A (ja) 1993-10-26
JPS58202261A (ja) 1983-11-25
EP0182389A2 (de) 1986-05-28
JPH0534268B2 (enrdf_load_html_response) 1993-05-21
DE3381895D1 (de) 1990-10-25
US4548366A (en) 1985-10-22
JPH0826596A (ja) 1996-01-30
EP0182389A3 (en) 1987-10-07

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