EP0165511A2 - Dispositif pour bobiner un fil livré à vitesse constante sur une bobine conique - Google Patents

Dispositif pour bobiner un fil livré à vitesse constante sur une bobine conique Download PDF

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Publication number
EP0165511A2
EP0165511A2 EP85106573A EP85106573A EP0165511A2 EP 0165511 A2 EP0165511 A2 EP 0165511A2 EP 85106573 A EP85106573 A EP 85106573A EP 85106573 A EP85106573 A EP 85106573A EP 0165511 A2 EP0165511 A2 EP 0165511A2
Authority
EP
European Patent Office
Prior art keywords
winding
drive
thread tension
roller
thread
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.)
Granted
Application number
EP85106573A
Other languages
German (de)
English (en)
Other versions
EP0165511B1 (fr
EP0165511A3 (en
Inventor
Hans Dipl. Ing. Landwehrkamp
Walter Slavik
Hans Heinrich Hauser
Arthur Dipl.-Ing. Eth Rebsamen
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.)
Rieter Ingolstadt Spinnereimaschinenbau AG
Original Assignee
Schubert und Salzer Maschinenfabrik 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
Application filed by Schubert und Salzer Maschinenfabrik AG filed Critical Schubert und Salzer Maschinenfabrik AG
Publication of EP0165511A2 publication Critical patent/EP0165511A2/fr
Publication of EP0165511A3 publication Critical patent/EP0165511A3/de
Application granted granted Critical
Publication of EP0165511B1 publication Critical patent/EP0165511B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • B65H54/42—Arrangements for rotating packages in which the package, core, or former is rotated by frictional contact of its periphery with a driving surface
    • 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
    • B65H59/382—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 mechanical 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 method for winding a thread fed at a constant speed onto a cross-wound bobbin and a device for carrying out this method.
  • Such packages are driven over their circumference so that a constant circumferential speed is achieved in the drive area.
  • constant thread delivery as is the case with open-end spinning machines and also with some winding machines, only the different path of the thread needs to be compensated for over the width of the bobbin, which is usually done with relatively simple means, for example a curved thread guide rail to achieve.
  • relatively simple means for example a curved thread guide rail to achieve.
  • the drive point is shifted relative to the conical cross-wound bobbin by the conical bobbin resting on a plurality of support rollers, each of which can optionally take over the drive.
  • an axially displaceable drive roller is required, whose stroke range extends from the first support roller at one end of the coil to last support roller at the other end of the package is sufficient. Due to the large stroke of this drive roller, it is also subject to relatively large wear.
  • the drive speed for the cheese can only be changed gradually in accordance with the number of support rollers. If only a few support rollers are provided, this gradation is very large. If many support rollers are provided, the support area which transmits the drive becomes very small, so that this also results in poor drive transmission. In both cases, the thread tension is not taken into account at all, so that the conical cross-wound bobbins generated are not wound evenly.
  • the winding roller consists of two or more partial rollers, which can be brought into controllable connections with the drive shaft carrying them, optionally via controllable couplings.
  • the couplings are controlled by a pendulum arm, over which the thread to be wound is placed in the form of a loop, so that the conical cheese is driven depending on the size of the thread loop and thus at different peripheral speeds.
  • the adaptation to thread tension changes achieved by this device is quite rough, since for structural reasons only a limited number of couplings between the drive shaft and the winding roller can be accommodated.
  • the object of the invention is therefore to avoid the disadvantages mentioned and to provide a method and a device for producing uniformly wound, in particular conical, cross-wound bobbins, which enable a winding under uniform thread tension at each winding point, the device being simple and compact in its construction is.
  • This object is achieved according to the invention in that thread tension fluctuations are compensated for and, in addition, changing the winding speed prevents predetermined thread tension limit values from being exceeded.
  • the thread tension fluctuations that occur when the thread winds up are compensated for by the deflection of the thread during the formation of the first turns on a newly inserted sleeve. If an elastic layer layer has subsequently formed from the wound thread turns when the bobbin has become larger, the shift in the region of the thread tension fluctuations caused thereby is compensated for by the change in the winding speed.
  • the cheese is driven with a maximum peripheral speed determined by the desired tensioning delay which is reduced to avoid area shifts in the thread tension fluctuations. In this way, trouble-free running with even tension delay over the entire duration of the bobbin build-up is guaranteed, even with conical cross-wound bobbins.
  • a first regulating system for compensating for periodic thread tension fluctuations and a second regulating system for compensating for area displacements of thread tensions are provided for carrying out the described method. This ensures in a simple manner that a constant tension delay is maintained during the winding of the thread.
  • the first regulating system consists of a thread tension sensor which can be brought into effect on the second regulating system when a predetermined range of thread tensions is shifted.
  • the first regulating system thus simultaneously serves as a monitoring system which monitors a break out of the predetermined range of thread tensions. A separate monitoring system for controlling the second regulating system is therefore unnecessary.
  • the second regulating system is designed as an adjustable transmission gear, the drive part of which is connected to a drive shaft extending over a plurality of winding positions and the driven part of which is connected to the winding roller, the drive part being connected to the driven part by means of the translation in each case determining transmission link is connected, which is connected to the first regulating system. Because both the drive part and the driven part are axially immovable and the transmission element determining the translation is located between this drive part and the driven part, there are no elements which are moved along the cross-wound bobbin or the winding drum, so that the risk of faults due to deposits due to abrasion of an element which can be displaced along the winding drum is not occurs.
  • the speed of rotation of the drive is not simply transferred to the winding drum. Rather, the winding roller is generally driven at a speed which differs from the rotational speed of the drive, the winding speed of the winding roller being able to be varied within a wide range with the aid of the controllable transmission gear.
  • a “winding roller” should be understood to mean any element by means of which the package is driven over its circumference, regardless of whether this element extends over the entire length of the package or only over a more or less large partial area thereof .
  • the transmission gear can be set to a maximum transmission ratio that cannot be exceeded. In this way, a feedback of the winding speed to the thread tension compensation is excluded in a simple manner.
  • the transmission link is infinitely adjustable, so that a very fine adaptation to changing conditions is possible and a conical cross-wound bobbin is always formed in the desired manner from start to finish, which can thus also be optimally processed in later processing phases.
  • controllable transmission gear can be designed differently and also have differently designed transmission elements, for example in the form of eddy current of an eddy current clutch or magnetic powder of a magnetic powder clutch, which transmits a rotational speed supplied to it to the desired extent.
  • torque clutches react differently with every response. In order to achieve defined conditions, it is therefore expedient to scan the rotational speed of the winding roller and regulate the clutch as a function of the desired conditions and the actual rotational speed of the winding roller in a transmission member designed in this way.
  • both the drive part and the driven part are designed as a cone wheel, between which the transmission member is axially adjustable .
  • designing this transmission element as an adjusting ring has proven to be particularly advantageous. This ensures that regardless of the respective position of the transmission member, the winding roller always assumes the same radial position, so that the respective coil diameter can be monitored in a simple manner by a stationary light barrier.
  • the transfer element is assigned an adjustable basic position and a feedback device for returning the transfer element to it, the maximum - Basic position determining the transmission ratio. If the transmission member is part of a cone gear, this basic position can advantageously be determined by a stop assigned to the transmission member.
  • the adjustable stop is advantageously associated with an actuating fork for the transmission element which is acted upon by the feedback device, it having proven expedient to arrange the adjustable stop on the actuating fork.
  • the return device can be designed as a return spring, but the return device is preferably designed as converging outer surfaces of the cone wheels.
  • the converging lateral surfaces of the drive and driven wheels exert a force on the transmission element, which returns it to its basic position.
  • the cone wheel forming the driven part is mounted on an axis which is inclined with respect to the drive shaft which carries the cone wheel forming the drive part.
  • the inclination of this axis can be adjustable.
  • the adjustable axis is advantageously mounted on a lever to which an adjusting eccentric is assigned.
  • the cone wheels have different conicity.
  • the lateral surfaces of the transmission member also have different conicity, adapted to the conicity of the cone wheels.
  • the feedback device has the additional advantage that, due to the displacement of the transmission element, the transmission between the cone wheels takes place at different points, so that excessive wear on a single circumferential line of the cone wheels is avoided.
  • the transmission gear has a one-stage transmission ratio, the winding roller being eccentrically mounted to a drive shaft by a bearing accommodating the drive shaft, and the driven part being designed as a conical inner contour. This ensures that regardless of the respective position of the transmission member, the winding roller always assumes the same radial position, so that the respective coil diameter can be monitored in a simple manner by a stationary light barrier.
  • the drive shaft is arranged outside the winding roller.
  • the transmission gear is connected to the winding roller and / or the drive shaft via a further gear.
  • the rotation is thus passed from the drive shaft to an intermediate shaft, to the transmission member or the like, from which the rotation is then directed to the winding roller mounted concentrically to the drive shaft.
  • the further transmission it has proven to be expedient for the further transmission to be arranged between the driven part and the winding roller.
  • the translation can be done in different ways, e.g. with the help of toothed or friction wheels or chains. It is particularly simple and quite sufficient if the further gear is designed as a cord overdrive.
  • the control connection between the thread tension sensor forming the first regulating system and the transmission gear forming the second regulating system can take place in any customary and known manner, e.g. electric.
  • mechanical solutions have proven to be particularly inexpensive.
  • the thread tension sensor has a bracket which senses the tension of the thread fed to the winding device and which is connected with the aid of a linkage to the transmission element of the transmission gear.
  • the thread tension sensor has a nose extending parallel to the winding roller for cooperation with an adjusting lever of this maintenance device, which can be optionally delivered to a plurality of winding positions.
  • the thread tension sensor is advantageously made of plastic.
  • bracket and linkage Elongated hole provided, the size of which is expediently adjustable. In this way, the sensitivity of the device according to the invention and / or the position of the thread tension range can be set.
  • the thread tension sensor can have a guide for a push rod forming part of the linkage with an adjustable stop which can be brought into contact with the thread tension sensor and via which the transmission element can be moved out of its basic position.
  • an elastic coupling member that transmits the relative movements can be provided.
  • the transmission gear is advantageously arranged at the end of the smaller diameter of the conical package inserted into the winding device.
  • the winding roller has at least two idler rollers and one between this idler rollers arranged, the cheese driving drive roller.
  • the idler rollers serve only as a spool support element, while the spool is driven solely by the drive roller. It has been found to be advantageous that the drive roller is not located in the center of the inserted bobbin, but is offset between the idler rollers in the axial direction to the larger diameter of the conical bobbin inserted in the bobbin device, with different numbers of idler rollers being provided on both sides of this bobbin can.
  • the drive roller can be driven over its outer circumference.
  • the drive roller of a multi-stage winding roller is not to be driven over its circumference, it is provided in an expedient embodiment of the device according to the invention that the drive roller is connected via a sleeve-like connecting piece to a drive element provided at one end of the winding roller and driven by the transmission gear, the between Drive roller and drive element arranged idler roller is mounted on this sleeve-shaped connecting piece.
  • the drive roller advantageously has on its end facing away from the sleeve-like connecting piece a sleeve-like extension for mounting at least one further loose roller.
  • the winding roller Regardless of whether the winding roller is driven over its outer circumference or over its end, it advantageously has a surface specially designed as a driving surface for better entrainment of the package, which can be done by appropriate choice of material for this surface or by profiling the same.
  • the subject matter of the invention is simple in structure, safe in function, space-saving and easily adaptable to fluctuating thread tensions and winding conditions.
  • the device allows precise controls despite the high winding speed, so that both precise cylindrical and precise conical packages are produced.
  • the winding device 1 initially described and shown in FIG. 1 is part of an open-end spinning machine for the production of conical cross-wound bobbins 11, but the invention can also be implemented in other textile machines that use winding units or winding devices 1 to form cylindrical or conical cross-wound bobbins 11 have.
  • each winding device 1 essentially consists of a bobbin holder 2, an individual, axially immovable winding roller 3 and an axially immovable drive shaft 4 which drives the winding roller 3 via a controllable transmission gear 5.
  • the bobbin holder 2 has two bobbin arms 20 and 21 for receiving a conical sleeve 22, on which the conical cross-wound bobbin 11 is formed by winding the thread 10 and is driven by the winding roller 3 by friction.
  • the winding roller 3 is freely rotatably supported on the drive shaft 4 with the aid of two roller bearings 30 and 31.
  • a gear 71 is connected in a rotationally fixed manner, which gear is part of a spur gear 7 arranged between the above-mentioned transmission gear 5 and the winding roller 3.
  • the drive shaft 4 is jointly assigned to a large number of winding devices 1 arranged next to one another and extends accordingly over this large number of winding devices.
  • the winding roller 3 is not driven directly by the drive shaft 4, but by interposing the controllable transmission gear 5.
  • the transmission gear 5 shown in Figure 1 has a controllable cone gear 6 and a non-controllable spur gear 7.
  • the transmission gear 5 has a rigidly connected to the drive shaft 4, designed as a cone gear 60, with which, with the interposition of a transmission member 61, an output gear designed as a cone gear 62 works together.
  • the transmission element 61 which in the embodiment shown is designed as an adjusting ring, can be adjusted parallel to the surface lines of the two cone wheels 60 and 62, as will be described later.
  • the cone wheel 62 is supported by means of roller bearings 63 and 64 on an axis 65, which in turn is carried by a bearing 66.
  • a spur gear 70 is non-rotatably connected to the cone gear 62, which meshes with a spur gear 71 connected to the winding roller 3.
  • the transmission element 61 is guided by an actuating fork 80, to which a suitable drive 8 is assigned.
  • the drive 8 can be designed as a stepper motor which can be rotated back and forth and which engages via a pinion in a toothed rack which is connected to the actuating fork 80.
  • Such a stepper motor is inexpensive and requires no control device for its control, so that the control effort is low.
  • such a drive enables a very fine gradation, which is practically equivalent to a stepless adjustment of the transmission member 61.
  • the drive 8 is connected to a control device 9, which in turn is connected in terms of control to a thread tension sensor 90.
  • the thread tension sensor 90 forms a first regulating system 96, while the transmission gear 5 forms a second regulating system 51.
  • the thread 10 to be wound is produced continuously in a spinning device 12 and drawn off from it with the aid of take-off rollers 13 and 14.
  • the thread 10 then passes through a stationary thread guide 15 and a thread tension compensation bracket 16.
  • the thread 10 is placed in the sleeve 22 to form a cross-wound bobbin 11 with the help of a traversing thread guide 17 (indicated by dashed lines).
  • the thread 10 fed to the spool device 1 is scanned by the thread tension sensor 90. Any change in the thread tension l ird to the control device 9 reported that according to this thread tension change the drive uri 8 controls the transmission member 61 of the cone parallel to de transmission 6 Cone wheels 60 and 62 moves. As a result, the transmission ratio of the transmission gear 5 changes.
  • the speed of the winding roller 3, driven by the drive shaft 4 via the transmission gear 5, for the conical cross-wound bobbin 11 changes in accordance with the thread tension change, so that the thread winding speed generated always takes into account the constant thread delivery speed, taking into account the thread running change which the thread 10 is drawn off from the spinning device 12 by the take-off rollers 13, 14.
  • the first regulating system 96 formed by the thread tension sensor 90 thus, together with the second regulating system 51 formed by the transmission gear 5, winds up the thread 10 with constant tension.
  • the conical gear 62 of the conical gear 6, its transmission member 61 and the adjusting fork 80 are shown in a perspective view in FIG.
  • the transmission member 61 is designed as an adjusting ring which can be displaced axially parallel to the surface line of the two cone wheels 60, 62.
  • the adjusting ring is dimensioned such that it always surrounds the cone 62 enclosed by it with play, regardless of the current position. This is the case if the inner diameter of the adjusting ring is larger than the largest outer diameter of the cone wheel 62 enclosed by it.
  • the transmission element 61 which is designed as an adjusting ring, is guided between two pairs of driving pins 800 and 801, of which only one driving pin can be seen in FIG. 5.
  • An embodiment of the transmission member 61 as a collar is particularly wear-resistant and therefore long-lasting in comparison to other designs in which, for example, a cord, a belt or the like is used as the transmission member finds.
  • a collar reacts particularly quickly to the actuating movements given to it, so that with the aid of a collar a very rapid adaptation to changing conditions is made possible.
  • a further transmission 7 with a non-controllable transmission ratio is provided.
  • the drive shaft 4 is arranged inside the winding roller 3, since then a concentric arrangement of the winding roller 3 and the drive shaft 4 is made possible.
  • the controllable transmission gear 5 is arranged between the drive shaft 4 and the non-controllable spur gear 7. The reason for this is that for the attachment of the drive wheel carried by the drive shaft 4 (cone wheel 60), a certain amount of space must be present next to the winding roller 3, while the attachment of the spur gear 71 to the winding roller 3 takes place within the same.
  • a two-stage gear ratio is provided, but instead a single gear stage or auct more than two gear stages can be used.
  • a one-step translation is shown for example in Figure 2.
  • the drive shaft 4 is in this case mounted on each winding device 1 with the aid of a roller bearing 41 in a stationary bearing 40, on which, on the other hand, one end of the winding roller 3 is also supported with the aid of a roller bearing 30.
  • the winding roller 3 has a cone-shaped inner contour 32.
  • This inner contour 32 which is designed as a hollow cone, forms the output part of the transmission gear 5, which is rigidly connected to the winding roller 3.
  • This inner contour 32 works via the transmission member 61 with the one on the drive shaft 4 axially immovable drive part designed as a conical wheel 60.
  • the transmission member 61 is controlled, as described with reference to FIG. 1, to change the transmission ratio with the aid of the adjusting fork 80.
  • this transmission gear 5 can be arranged between the drive shaft 4 and the winding roller 3, the winding roller 3 is arranged eccentrically to the drive shaft 4 in order to enable an actuating movement of the transmission member 61.
  • the conical cross-wound bobbin 11 Due to its conicity, the conical cross-wound bobbin 11 is driven in its different length ranges with the same angular speed, but with different peripheral speeds, which is why the thread 10 located on the cross-wound bobbin 11 in the length ranges in which the peripheral speed of the cross-wound bobbin 11 differs from that of the winding roller 3. is subjected to greater friction, which has a disadvantageous effect on the thread 10.
  • the winding roller 3 shown in FIG. 2 has in its central length region a surface designed as a driving surface 33, while the remaining length regions of the winding roller 3 have a small surface compared to the thread 10 Have friction coefficients and only serve as a support element.
  • the driving surface 33 can have a good driving property in relation to the package 11 by a suitable choice of material or by a corresponding profiling or by a combination of both measures. Since the driving surface 33 and the remaining length regions of the winding roller 3 serving as supporting elements do not have to be selected as a function of a desired speed change, their dimensions can be chosen such that a good transmission of the rotary movement to the conical cheese 11 is always guaranteed.
  • the winding roller 3 mounted on the drive shaft with the aid of roller bearings 30 and 31 has a drive roller 34, from which a sleeve-like connecting piece 340 extends to a line roller 721 and is connected to the latter in a rotationally fixed manner.
  • a loose roller 35 is mounted on this sleeve-like connecting piece with the aid of roller bearings 350 and 351.
  • the drive roller 34 continues on its side facing away from the line roller 721 to the end of the winding roller 3, likewise in the form of a sleeve-like extension 341, and carries a further idler roller 36 by means of roller bearings 360 and 361.
  • the drive roller 34 in turn has a surface designed as a driving surface 33.
  • the two idler rollers 35 and 36 are not driven by the drive shaft 4, but by the cross-wound bobbin 11, so that the friction due to slippage between the cross-wound bobbin 11 and the idler rollers 35 and 36 of the divided winding roller 3 is very strong are reduced.
  • FIG. 4 shows, more than just two idler rollers 35 and 36 can also be provided.
  • the drive roller 34 of the roller 3 does not have to be arranged centrally between the idler rollers. Because of the greater friction caused by the larger mass on the larger diameter of the package 11, it is expedient if - as shown in FIG. 4 - the drive roller 34 is arranged offset in the direction of the larger diameter of the package 11 in the winding roller 3. This is achieved according to FIG.
  • the transmission gear 5 can be arranged and designed differently from the embodiment shown in FIG. 1. Since with conical cross-wound bobbins 11 a possibly desired thread reserve is always formed at the end of the sleeve 22 (FIG. 1), at which the larger diameter of the cross-wound bobbin 11 is located, it can happen that the thread end gets into the transmission gear 5 and thus both leads to a withdrawal of the thread reserve from the sleeve 22 and also to a malfunction of the transmission 5. As a remedy, the transmission mechanism 5 is therefore arranged according to FIG. 3 at the end of the smaller diameter of the cross-wound bobbin 11 inserted into the bobbin holder 2.
  • a torque clutch arranged between two cord exaggerations 72 and 73 and simultaneously forming the transmission element is used as the controllable transmission gear 5 50 application.
  • the first line exaggeration 73 has a line roller 730 which is arranged on the drive shaft 4 in a rotationally fixed manner and which drives a line roller 731 via a line 732.
  • This line roller 731 sits together with another line roller 720 on a common axis 65 carried by the bearing 66.
  • the two line rollers 731 and 720 are connected to one another via the torque clutch 50, for example an eddy current or magnetic particle clutch, from the control device 9 is controlled.
  • the aforementioned line roller 721 receives its drive from the line roller 720 via a line 722.
  • the torque clutch 50 can be controlled by the control device 9 in a plurality of stages or preferably continuously. But even with stepped control of the torque clutch 50, this control is much more precise than in the known prior art, where different clutches are used alternately.
  • spur gear 7 is not controllable in Figure 1, it can also be replaced by a cord overdrive 72.
  • the winding roller 3 can also be driven via its outer circumference, the winding roller 3 having a driving surface 33 which is designed both for its own drive through the transmission gear 5 and for driving the cheese 11.
  • the driving surface 33 which is designed both for its own drive through the transmission gear 5 and for driving the cheese 11.
  • the spur gear 70 it is possible in FIG. 1 to provide a friction wheel which bears against this driving surface 33 and drives the winding roller 3 or a drive roller 34 thereof.
  • the drive shaft 4 is arranged outside the winding roller 3 and drives it from the outside via a transmission gear 5.
  • this transmission gear 5 has a cone gear 6, as was described with reference to FIG. 1.
  • the cone wheel 62 is connected to a friction wheel 74 and drives the winding roller 3 as a whole or only the drive roller 34 thereof, which, like the friction wheel 74 and the cone wheel 62, is carried by the bearing 66.
  • the winding roller 3 is supported on an axis 39 which is supported by two bearings 390 and 391.
  • the conical cheese 11 is again controlled in the manner described.
  • the driven part, rigidly connected to the winding roller 3, of a friction wheel transmission connected downstream of the transmission gear 5 is formed here by the driving surface 33, while the drive part of this friction wheel transmission is formed by a friction wheel 74 connected to the cone wheel 62.
  • the transmission element 61 of the conical gear 6 and thus the second regulating system 51 are controlled by a control device 9, which in turn is controlled electrically by the thread tension sensor 90, ie the first regulating system 96.
  • the formation of the thread tension sensor 90 also plays a role here basically no role. For example, it can work without contact and determine the thread tension as a function of a measured loop size or in some other suitable way.
  • FIG. 5 shows an embodiment in which this control of the transmission element 61 takes place mechanically from the thread tension sensor 90.
  • the thread tension sensor 90 which is made of plastic for reasons of ease of movement, in this case has a bracket 91 which is pivotably mounted on an axis 93 with the aid of a holder 92.
  • the axis 93 is supported by a bearing 94.
  • the bracket 91 is elastically loaded by a torsion spring 95 and is always held by the action of this torsion spring 95 in contact with the thread 10 and thus pivoted depending on its tension.
  • one end of the torsion spring 95 is anchored in the bearing 94 and the other end of the torsion spring 95 in the holder 92.
  • the holder 92 bears on its circular end face 920 an entraining pin 921 which engages in an elongated hole 820 of a entraining block 82 which is part of a linkage 81 which connects the bracket 91 to the adjusting fork 80.
  • the driving block 82 is arranged on a push rod 83, which carries a further driving block 84 at its other end.
  • This further driving block 84 is connected via an angle lever 85, which is mounted on the machine frame 18, to a further drive rod 86, which by means of a guide 87 is guided parallel to the drive shaft 4.
  • This drive rod 86 carries the adjusting fork 80 which, with its driving pin pairs 800 and 801 (only one pin visible in each case), engages around the transmission element 61 of the conical gear 6 (see also FIG. 1).
  • an elongated hole 820 oriented in the direction of movement of the push rod 83 is provided in the driving block 82, so that small fluctuations in the thread tensions do not immediately lead to an adjustment of the transmission member 61.
  • the thread tension sensor 90 is able to compensate for smaller thread tension fluctuations without causing an adjustment of the transmission element 61.
  • this thread tension sensor 90 thus forms a first regulating system 96 for compensating for periodic thread tension fluctuations, such as occur due to the traversing of the thread 10 by the traversing thread guide 17 (see FIG. 1).
  • this first regulating system 96 is completely sufficient to absorb the thread tension fluctuations.
  • the thread Shortly after the start of the winding, the thread begins to fill the gaps between the winding roller 3 and the cross-wound bobbin 11 outside the driving surface 33 (see areas 110 and 111 in FIG. 6). In these areas 110 and 111, the bobbin circumference is thus larger than in the driven area 112, so that in the larger areas 110 and 111 more thread 10 is wound than the driving speed of the cheese 11 in its driven area 112 corresponds. This leads to a tension increase in the thread 10, so that the thread tension sensor 90 is pivoted out of the original area I-II (see FIG. 7) into the area II-III.
  • the driving pin 921 comes to rest against the driving block 82 and effects an adjustment of the transmission member 61 via the linkage 81, so that the transmission ratio of the transmission gear 5 is changed.
  • the winding speed of the thread 10 is thus reduced when certain thread tension limit values are exceeded, which is determined by the installation of the thread tension sensor 90 on the driving block 82, so that the thread tension fluctuations again in the original area.
  • the thread tension sensor 90 now moves again into the area I-II, where it compensates for the periodic thread fluctuations by swinging, while the shifted transmission element 61 ensures the higher winding speed.
  • the transmission gear 5 thus forms the aforementioned second regulating system 51 to compensate for area shifts from thread tension fluctuations.
  • the second regulating system 51 can also operate independently of the first regulating system 96, in deviation from the described embodiment, in that the second regulating system 51 is controlled as a function of an increase in the coil diameter.
  • the second regulating system 51 can be brought into effect by the first regulating system 96 when the predetermined range of thread tension fluctuations is shifted.
  • the range of thread tension fluctuations which are to remain without effects on the second regulating system 51 can be adjusted according to FIG. 5.
  • an adjusting screw 821 is provided in the driving block 82 parallel to the push rod 83 to adapt the response accuracy to the respectively required requirements.
  • Elongated opening 820 protrudes.
  • the adjusting screw 821 is to be adjusted accordingly or instead of the elongated hole 820 a cylindrical opening is to be provided for receiving the driving pin 921.
  • the two driving blocks 82 and 83 are not rigidly connected to the push rod 83.
  • an elastic coupling member 830 and 833 designed as a compression spring, is provided in front of each driving block 82 and 84, which is supported on the push rod 83 via an adjusting ring 831 and 834, respectively (seen from the viewer).
  • a stop 832 or driving ring 835 is arranged on the side of each of the two driving blocks 82 and 84 facing away from the elastic coupling member 830 or 833.
  • each movement of the thread scanning bracket 91 is transmitted to the drive rod 86 via the elastic coupling members 830 and 833, respectively.
  • the thread scanning bar 91 is in contact with the stop pin 940. If this thread scanning bar 91 is now pivoted away from the stop pin 940, the driving pin 921 executes a circular movement, whereby a movement component of the driving pin 921 located in the elongated hole 820 is always oriented in the direction of the coupling member 830 is. If the drive rod 86 is blocked because the winding position is stopped and the transmission element 61 cannot be adjusted, the drive block 82 carried by the drive pin 921 can only carry the push rod 83 via the elastic coupling element 830 until the drive ring 835 comes to rest the drive block 84 arrives. The further movement of the driving block 82 is absorbed by the elastic coupling member 830.
  • FIG. 6 shows a modification of the device described, with the aid of which periodic thread tension fluctuations are also compensated for and, in addition, a change in the wind-up speed prevents predetermined thread tension limit values from being exceeded.
  • the first regulating system 96 like the embodiment shown in FIG. 5, has a thread tension sensor 90, which is rotatably mounted about an axis 93 and is biased by a torsion spring 94 (see Figure 5). Below the bracket 91, the thread 10 is guided through the draw-off rollers 13, 14, while it is guided above the bracket 91 through a thread guide 150 held by the machine frame 18.
  • the thread tension sensor 90 is designed as a guide for the push rod 83, which carries a stop 832.
  • This stop 832 is adjustable and occupies such a position on the push rod 83 that the thread tension sensor 90 can move freely within the range I-II (see FIG. 7) to compensate for periodically occurring thread tension fluctuations without running onto the stop 832.
  • the setting of the stop 832 on the push rod 83 thus defines the limit of the area I-II to the area II-III and thus the thread tension limit values.
  • the push rod 83 is guided in a guide 880 at the end of an angle lever 88 and is supported elastically on this by means of an adjusting ring 834 and an elastic coupling member 833.
  • the angle lever 88 is supported on the machine frame 18 and engages with its free end, a driving pin 802 of the actuating fork 80, supported by means of second long holes 803 and 804 and two from the machine frame 1 8 guide pins 180 and is passed 181 parallel to the drive shaft 4 of the winding roller.
  • the actuating fork 80 carries a stop 805 which cooperates with a fixed stop 182 of the machine frame 18.
  • one of the stops namely the stop 805 of the adjusting fork 80, is adjustable, which is why it is designed as an adjusting screw.
  • a feedback device 89 is also provided. According to the embodiment shown in FIG. 6, this is designed as a return spring 890, one end of which is anchored to the machine frame 18 and the other end of which is anchored to the adjusting fork 80.
  • the adjusting fork 80 and thus also the transmission 61 are in a basic position, which is defined by the stops 182 and 805, when no forces transmitted from the first regulating system 96 act on the second regulating system 51.
  • the determination of the basic position results in a determination of the transmission ratio of the transmission gear 5.
  • the tensioning delay of the winding unit therefore depends on the arrangement or setting of the stops 182/805.
  • the adjustable stop 805 the maximum transmission ratio that cannot be exceeded, i.e. the maximum peripheral speed of the cheese 11 is set.
  • the thread tension sensor 90 reacts to this by deflections up to the area II-III.
  • the thread tension sensor 90 thus abuts the stop 832 and lifts the adjusting fork 80 from the stop 182 via the push rod 83 and the angle lever 88.
  • the actuating fork 80 moves the transmission member 61 - e.g. an adjusting ring - out of its basic position so that it reaches the larger diameter range of the cone wheel 60 and the smaller diameter range of the cone wheel 62.
  • the winding roller 3 is now driven at a lower rotational speed in order to avoid area shifts in the thread tension fluctuations, so that the peripheral speed of the cross-wound bobbin 11 driven by the winding roller 3 is also reduced. In this way, the winding speed is reduced, the thread tension decreases and the thread tension sensor 90 returns to the area I-II.
  • the actuating fork 80 When the actuating fork 80 is acted upon by the return spring 890, the actuating fork 80 has a tendency to return the transmission member 61 to the starting position.
  • the resulting increase in the peripheral speed of the package 11 leads again to an increase in the thread tension and thus to a shift in the thread tension fluctuations in the area II-III.
  • This game repeats itself until there is a balance at the transition between areas I-II and II-III.
  • the percentage differences in diameter between the areas 110, 111 and 112 of the package 11 become smaller and smaller as the package grows, so that the deflections of the thread tension sensor 90 also become smaller and smaller.
  • the feedback device 89 can also be used in the exemplary embodiments shown in FIGS. 1 to 5. It prevents the thread tension sensor 90 from moving too far when leaving the area I-II, so that the thread tension drop 90 caused by this causes the thread tension sensor 90 to immediately counter-regulate, for example with the aid of a coupling element 830 and an adjusting ring 831 (FIG 5). This can give rise to the risk that the thread tension fluctuations can no longer be compensated for, but will continue to build up. However, this is definitely avoided by the feedback device.
  • the thread tension sensor 90 has a nose 900 which extends essentially parallel to the drive shaft 4 and the winding roller 3.
  • An arm (not shown) of a maintenance device which can be moved along the machine, can cooperate with this nose 900, for example in order to pivot the thread tension sensor 90 out of the thread path into position IV for spinning. Since the actuating fork 80 abutting the stop 182 cannot follow this movement, this takes place between the push rod 83 and the transmission member 61, i. the adjusting fork 80, arranged coupling member 833 when pivoting the thread tension sensor 90 in the position IV on the additional path.
  • FIG. 8 shows another embodiment of a feedback device 89.
  • the cone wheel 62 is mounted on an axis 65 which has an inclination with respect to the drive shaft 4 with the cone wheel 60.
  • both cone wheels 60 and 62 have the same taper, they converge Tilt the lateral surfaces of the cone wheels 60 and 62, so that a force component P acts on the transmission member 61, which the transmission member 61 wants to return to the basic position.
  • this convergence can be set by the conical wheel 62 being mounted on an angle lever 68 via an intermediate lever 67.
  • This angle lever 68 can be pivoted about an axis 680, the free end having an elongated hole 681 in which an adjusting cam 682 engages.
  • the intermediate lever 67 is acted upon by a compression spring 670, which is supported in a suitable manner on a stationary part of the machine frame 18.
  • the convergence (angle ⁇ ) is achieved in that the two cone wheels 60 and 62 have a different conicity (see angles ⁇ 1 and ⁇ 2 ), which in turn acts on a force component P on the transmission member 61, which in the basic position wants to lead back.
  • its inner and outer peripheral surfaces have the same conicity as the two cone wheels 60 and 62, so that the conicity of the transmission member 61 and cone wheels 60 and 62 are matched to one another.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Winding Filamentary Materials (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
EP85106573A 1984-06-19 1985-05-29 Dispositif pour bobiner un fil livré à vitesse constante sur une bobine conique Expired EP0165511B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843422637 DE3422637A1 (de) 1984-06-19 1984-06-19 Textilmaschine mit mehreren spulstellen zum aufwinden eines mit konstanter geschwindigkeit zugefuehrten fadens auf eine konische kreuzspule
DE3422637 1984-06-19

Publications (3)

Publication Number Publication Date
EP0165511A2 true EP0165511A2 (fr) 1985-12-27
EP0165511A3 EP0165511A3 (en) 1986-08-13
EP0165511B1 EP0165511B1 (fr) 1989-05-24

Family

ID=6238663

Family Applications (2)

Application Number Title Priority Date Filing Date
EP85105557A Withdrawn EP0165428A3 (fr) 1984-06-19 1985-05-07 Machine textile avec plusieurs unités de bobinage de fil à vitesse constante sur bobine conique
EP85106573A Expired EP0165511B1 (fr) 1984-06-19 1985-05-29 Dispositif pour bobiner un fil livré à vitesse constante sur une bobine conique

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP85105557A Withdrawn EP0165428A3 (fr) 1984-06-19 1985-05-07 Machine textile avec plusieurs unités de bobinage de fil à vitesse constante sur bobine conique

Country Status (7)

Country Link
US (1) US4789107A (fr)
EP (2) EP0165428A3 (fr)
JP (1) JPS6175775A (fr)
CS (1) CS448485A3 (fr)
DE (2) DE3422637A1 (fr)
HK (1) HK31493A (fr)
SG (1) SG86891G (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0230943A1 (fr) * 1986-01-29 1987-08-05 Maschinenfabrik Rieter Ag Dispositif pour le bobinage d'un fil
EP0311815A2 (fr) * 1987-10-05 1989-04-19 W. SCHLAFHORST AG & CO. Méthode et dispositif pour égaliser la tension du fil pendant le rebobinage d'une cannette sur une bobine croisée
US5035369A (en) * 1988-05-25 1991-07-30 Elitex Koncern Textilniho Strojirenstvi System for winding a cone of yarn or the like
EP1795477A1 (fr) * 2005-12-08 2007-06-13 Murata Kikai Kabushiki Kaisha Bobinoir

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DE3802629A1 (de) * 1988-01-29 1989-08-03 Schlafhorst & Co W Einrichtung zur stufenlosen drehzahlaenderung einer friktionswalze
DE3805656A1 (de) * 1988-02-24 1989-09-07 Schubert & Salzer Maschinen Verfahren und vorrichtung zum wickeln konischer kreuzspulen
IT1226928B (it) * 1988-07-15 1991-02-22 Savio Spa Dispositivo regolatore della velocita' di avvolgimento del filato nella confezione di rocche coniche in un filatoio a rotore
DE9317052U1 (de) * 1993-11-08 1994-01-13 W. Schlafhorst AG & Co, 41061 Mönchengladbach Antriebsrolle für den rotatorischen Friktionsantrieb einer Textilspule
AU6270698A (en) 1997-02-05 1998-08-25 Plant Engineering Consultants, Inc. Precision winding method and apparatus
DE59809204D1 (de) * 1998-02-14 2003-09-11 Volkmann Gmbh Verfahren und Vorrichtung zur Garnaufwicklung auf einen konischen Spulenkörper
EP1319622A1 (fr) * 2001-12-05 2003-06-18 Schärer Schweiter Mettler AG Procédé et dispositif pour la régulation de la tension du fil dans une machine textile et l'utilisation du procédé
US6691569B1 (en) * 2002-07-31 2004-02-17 The Goodyear Tire & Rubber Company Dual windup drum extensional rheometer
US20070277843A1 (en) * 2006-06-06 2007-12-06 Whitman Michael J Hair curling system
JP5089751B2 (ja) * 2010-10-28 2012-12-05 花王株式会社 伸縮性シートの製造方法
CN103401505B (zh) * 2013-07-17 2016-05-25 苏州汇川技术有限公司 一种偏心机构减振方法及装置
CN103538965A (zh) * 2013-09-26 2014-01-29 吴江伊莱纺织科技有限公司 一种适用锥形筒纱管的摩擦辊
DE102015014429A1 (de) * 2015-11-10 2017-05-11 Saurer Germany Gmbh & Co. Kg Verfahren zum Betreiben einer Kreuzspulen herstellenden Textilmaschine
CN107910995A (zh) * 2017-12-25 2018-04-13 天津市源泉机电设备制造有限公司 一种绕线流水机组
CN111531053B (zh) * 2019-05-22 2022-04-26 湛江市顺泽实业有限公司 一种智能冲压装置的工作方法
CN112047197B (zh) * 2020-08-05 2022-03-22 深圳供电局有限公司 放线张力自调控放线架
CN115938683B (zh) * 2023-02-28 2023-07-04 滁州润翰微波科技有限公司 一种恒张力绕包设备

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GB1249247A (en) * 1968-12-09 1971-10-13 Rieter Ag Maschf Method of and apparatus for winding a yarn in which the yarn tension is controlled
DE1912374C3 (de) * 1968-07-19 1974-08-08 Veb Spinnereimaschinenbau Karlmarx-Stadt, X 9010 Karl-Marx-Stadt Spulmaschine, insbesondere Kreuzspulmaschine
DE2419422A1 (de) * 1973-05-15 1974-12-05 Elitex Zavody Textilniho Spulenaufwickelvorrichtung an textilmaschinen, insbesondere spinn-zwirn-texturier- und anderen aehnlichen maschinen
DE2328993C2 (de) * 1973-06-07 1975-04-17 Barmag Barmer Maschinenfabrik Ag, 5600 Wuppertal Aufspuleinrichtung
US3894439A (en) * 1974-07-26 1975-07-15 Domenic Borello Infinite speed drive
DE2458853A1 (de) * 1974-12-12 1976-06-16 Schlafhorst & Co W Wickeleinrichtung fuer konische, durch friktion angetriebene kreuzspulen
FR2386469A1 (fr) * 1977-04-08 1978-11-03 Starlinger & Co Gmbh Ensemble d'entrainement equipe d'un dispositif de reglage de la tension d'un fil textile
DE2730847B1 (de) * 1977-07-08 1979-01-04 Rombach Gmbh Johann B Stufenloses Reibringgetriebe
GB1587377A (en) * 1977-05-10 1981-04-01 Reiners Verwaltungs Gmbh Winding units of textile machines
GB2074204A (en) * 1980-04-19 1981-10-28 Reiners Verwaltungs Gmbh Friction-drive roller for rotating a textile bobbin

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DE1118073B (de) * 1956-08-08 1961-11-23 Barmag Barmer Maschf Regelvorrichtung an Spulmaschinen, insbesondere zur Herstellung kegelfoermiger Spulen
DE1923847A1 (de) * 1968-05-14 1969-11-27 Lodge Lane Engineering Ltd Verfahren und Garnwickelmaschine zum Herstellen von Garnwickeln
US3860186A (en) * 1968-12-09 1975-01-14 Rieter Ag Maschf Method and apparatus for winding yarn from open end spinning devices
FR2427989A1 (fr) * 1978-06-07 1980-01-04 Rhone Poulenc Textile Dispositif pour la regulation de la vitesse d'un organe delivreur ou renvideur de fil, en fonction de la vitesse d'appel de delivrage du fil
EP0094725A1 (fr) * 1982-05-17 1983-11-23 TEXTIELMACHINEFABRIEK GILBOS Naamloze Vennootschap Dispositif destiné à régler la vitesse de bobinage de fils à bobiner dans des bobineuses en fonction de la longueur disponible et/ou de la tension des fils
FR2836469B1 (fr) * 2002-02-22 2004-08-20 Dubourg Yann Frederic Etrier d'equitation a fixation automatique

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DE1912374C3 (de) * 1968-07-19 1974-08-08 Veb Spinnereimaschinenbau Karlmarx-Stadt, X 9010 Karl-Marx-Stadt Spulmaschine, insbesondere Kreuzspulmaschine
GB1249247A (en) * 1968-12-09 1971-10-13 Rieter Ag Maschf Method of and apparatus for winding a yarn in which the yarn tension is controlled
DE2419422A1 (de) * 1973-05-15 1974-12-05 Elitex Zavody Textilniho Spulenaufwickelvorrichtung an textilmaschinen, insbesondere spinn-zwirn-texturier- und anderen aehnlichen maschinen
DE2328993C2 (de) * 1973-06-07 1975-04-17 Barmag Barmer Maschinenfabrik Ag, 5600 Wuppertal Aufspuleinrichtung
US3894439A (en) * 1974-07-26 1975-07-15 Domenic Borello Infinite speed drive
DE2458853A1 (de) * 1974-12-12 1976-06-16 Schlafhorst & Co W Wickeleinrichtung fuer konische, durch friktion angetriebene kreuzspulen
FR2386469A1 (fr) * 1977-04-08 1978-11-03 Starlinger & Co Gmbh Ensemble d'entrainement equipe d'un dispositif de reglage de la tension d'un fil textile
GB1587377A (en) * 1977-05-10 1981-04-01 Reiners Verwaltungs Gmbh Winding units of textile machines
DE2730847B1 (de) * 1977-07-08 1979-01-04 Rombach Gmbh Johann B Stufenloses Reibringgetriebe
GB2074204A (en) * 1980-04-19 1981-10-28 Reiners Verwaltungs Gmbh Friction-drive roller for rotating a textile bobbin

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0230943A1 (fr) * 1986-01-29 1987-08-05 Maschinenfabrik Rieter Ag Dispositif pour le bobinage d'un fil
EP0311815A2 (fr) * 1987-10-05 1989-04-19 W. SCHLAFHORST AG & CO. Méthode et dispositif pour égaliser la tension du fil pendant le rebobinage d'une cannette sur une bobine croisée
EP0311815A3 (en) * 1987-10-05 1989-05-10 W. Schlafhorst & Co. Method and device to even out the yarn tension when rewinding from cops to cross bobbins
US5035369A (en) * 1988-05-25 1991-07-30 Elitex Koncern Textilniho Strojirenstvi System for winding a cone of yarn or the like
EP1795477A1 (fr) * 2005-12-08 2007-06-13 Murata Kikai Kabushiki Kaisha Bobinoir

Also Published As

Publication number Publication date
CS448485A3 (en) 1992-05-13
SG86891G (en) 1992-02-14
DE3422637A1 (de) 1985-12-19
EP0165511B1 (fr) 1989-05-24
EP0165511A3 (en) 1986-08-13
HK31493A (en) 1993-04-08
US4789107A (en) 1988-12-06
EP0165428A3 (fr) 1986-08-20
EP0165428A2 (fr) 1985-12-27
DE3570423D1 (en) 1989-06-29
JPS6175775A (ja) 1986-04-18

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