EP0165428A2 - Machine textile avec plusieurs unités de bobinage de fil à vitesse constante sur bobine conique - Google Patents

Machine textile avec plusieurs unités de bobinage de fil à vitesse constante sur bobine conique Download PDF

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Publication number
EP0165428A2
EP0165428A2 EP85105557A EP85105557A EP0165428A2 EP 0165428 A2 EP0165428 A2 EP 0165428A2 EP 85105557 A EP85105557 A EP 85105557A EP 85105557 A EP85105557 A EP 85105557A EP 0165428 A2 EP0165428 A2 EP 0165428A2
Authority
EP
European Patent Office
Prior art keywords
textile machine
machine according
roller
winding
drive
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.)
Withdrawn
Application number
EP85105557A
Other languages
German (de)
English (en)
Other versions
EP0165428A3 (fr
Inventor
Hans Heinrich Hauser
Arthur Dipl.-Ing. Eth Rebsamen
Walter Slavik
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 EP0165428A2 publication Critical patent/EP0165428A2/fr
Publication of EP0165428A3 publication Critical patent/EP0165428A3/fr
Withdrawn legal-status Critical Current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 textile machine with a plurality of winding units for winding a thread fed at a constant speed onto a conical cross-wound bobbin, a winding roller carrying the cross-wound bobbin and driving over its circumference being provided for each winding unit.
  • 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.
  • This requires an axially displaceable drive roller, the stroke range of which extends from the first support roller at one end of the spool to the last support roller at the other end of the package. Due to the large stroke of this drive roller, it is also subject to relatively large wear. It can also change the drive speed for the package according to the number of support rollers only gradually.
  • the winding roller consists of two or more sub-rollers, which can be brought into controllable connections with the drive shaft carrying them 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.
  • 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 a transmission element which in each case determines the transmission ratio and which is dependent on the Thread tension is adjustable. Since 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 occur along the cross-wound bobbin or the winding roller due to deposits due to abrasion of an element which can be displaced along the winding roller.
  • 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 drum being able to be varied within a wide range with the aid of the controllable transmission gear.
  • the transmission element By controlling the transmission element as a function of the sensed thread tension, uniformly well-wound conical cross-wound bobbins are always produced. This is additionally promoted by the fact that the width of the surface which transmits the winding roller rotation to the bobbin does not have to be selected as a function of the desired winding speed, but is freely selectable.
  • a “winding roller” is to 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 portion thereof.
  • 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 cones, between which the transmission member is axially adjustable .
  • designing this transmission element as an adjusting ring has proven to be particularly advantageous. This will achieved 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 screw.
  • Such a design of the subject matter of the invention enables the transmission gear to be adapted particularly quickly to changing conditions.
  • 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 various ways, for example 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 transmission gear is expediently connected to a thread tension sensor for control purposes in order to be able to control the transmission gear in a simple manner as a function of the thread tension.
  • the control connection between thread tension sensor and transmission gear can be done in any common and known way, 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.
  • an elongated hole is advantageously provided in the connection between the bracket and the linkage, the size of which is expediently adjustable. In this way, the sensitivity of the device according to the invention can be set.
  • the linkage has an elastic coupling member for each adjustment direction.
  • the transmission gear is advantageously arranged at the end of the smaller diameter of the conical bobbin inserted into the winding device.
  • the winding roller has at least two idler rollers and a drive roller arranged between these idler rollers and driving the cheese.
  • 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 object of the invention is simple in structure, safe in function, space-saving and easily adaptable to fluctuating thread tensions.
  • the device allows precise controls despite the high winding speed, so that precise conical packages are produced.
  • the textile machine initially described and shown in FIG. 1 is an open-end spinning machine, but the invention can also be implemented in other textile machines which have winding devices 1 for forming conical cross-wound bobbins 11.
  • each winding unit 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, while the spur gear 7 is not controllable.
  • the transmission gear 5 has a drive part rigidly connected to the drive shaft 4 and designed as a cone 60, with which an output part designed as a cone 62 interacts with the interposition of a transmission element 61.
  • the transmission member 61 which is designed as an adjusting ring in the embodiment shown, can be adjusted parallel to the surface lines of the two cones 60 and 62, as will be described later.
  • the cone 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 connected in a rotationally fixed manner to the cone 62 and is in engagement with the spur gear 71 connected to the winding roller 3.
  • the transmission member 61 is guided by a fork 80, which is assigned a suitable drive 8.
  • 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 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 actuating element 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 11 to be wound is continuously produced in a spinning device 12 and drawn off from it with the aid of take-off rollers 13 and 14.
  • the thread 11 then passes through a stationary thread guide 15 and a thread tension compensation bracket 16.
  • the thread 11 is the sleeve 22 to form a cross-wound le 11 with the help of a (indicated by dashed lines) traversing thread guide 17 submitted.
  • the thread 10 fed to the winding device 1 is scanned by the thread tension sensor 90. Every change in the thread tension is reported to the control device 9, which controls the drive 8 in accordance with this thread tension change and shifts the actuating element 61 of the cone gear 6 parallel to the cones 60 and 62. 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 thread tension sensor 90 thus forms, together with the step-up gear 5, a continuously operating control device which causes the thread 10 to be wound with a constant tension.
  • the cone 62 of the cone gear 6, its transmission member 61 and the 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 cones 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 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 element 61 as an adjusting ring is particularly wear-resistant and therefore long-lasting in comparison to other configurations in which, for example, a cord, a belt or the like is used as an adjusting element.
  • 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 within 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 part (cone 60) carried by the drive shaft 4 - a certain Space requirement must be present next to the winding roller 3, while the spur gear 71 is attached to the winding roller 3 within the same.
  • a two-stage gear ratio is provided, but instead a single gear stage or more than two gear stages can also be used instead.
  • 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 conical 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 arranged as a cone 60 drive part together.
  • the transmission member 61 is controlled by means of the fork 80 in order to change the transmission ratio.
  • 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 taper, 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 a surface formed as a driving surface 33 in its central length region, while the remaining length regions of the winding roller 3 have a low coefficient of friction compared to the thread 10 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, then their dimensions are chosen so 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 also sits on its side facing away from the line roller 721 up to the end of the winding roller 3 Form a sleeve-like extension 341 and carries a further loose 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 12, 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.
  • 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 to withdraw the thread reserve from the sleeve 22 and to disrupt the translation gear 5 leads. 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 coupling 50 which is arranged between two cord exaggerations 72 and 73 and simultaneously forms the transmission element, is used as the controllable transmission gear 5.
  • the first cord overdrive has a cord roller 730 which is arranged on the drive shaft 4 in a rotationally fixed manner and which drives a cord roller 731 via a cord 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 above the torque coupling 50, e.g. an eddy current or magnetic powder clutch, which is controlled by the control device 9.
  • 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 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 by the driving surface 33, while the drive part of this friction wheel transmission is formed by a friction wheel 74 with the cone 62.
  • the transmission element 61 of the conical gear 6 is controlled by a control device 9, which in turn is controlled electrically by the thread tension sensor 90.
  • the design of the thread tension sensor 90 also plays no role in principle. 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 adjusting element 61 takes place mechanically from the thread tension sensor 90.
  • the thread tension sensor 90 here 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 carries on its circular end face 920 a driving pin 921 which engages in an elongated hole 820 of a driving block 82 which is part of a linkage 81 which connects the bracket 91 to the fork 80.
  • the driving block 82 is arranged on a 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 is guided parallel to the drive shaft 4 with the aid of a guide 87.
  • This drive rod 86 carries the 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 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 adjusting element 61.
  • an adjusting screw 821 is provided in the driving block 82 parallel to the rod 83 and protrudes into the opening 820 designed as an elongated hole. By adjusting this adjusting screw 821, the size of the opening 821 and thus the sensitivity of the device can be changed.
  • the two driving blocks 82 and 83 are not rigidly connected to the rod 83.
  • an elastic coupling element 830 and 833 designed as a compression spring, is provided in front of each driving block 82 and 84, which is supported on the rod 83 via an adjusting ring 831 and 834.
  • a driving ring 832 and 835 is arranged on the side of each of the two driving blocks 82 and 84 facing away from the elastic coupling member 830 and 833, respectively.
  • 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.
  • the drive block 82 carried by the drive pin 921 can only drive the rod 83 via the elastic coupling member 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Winding Filamentary Materials (AREA)
EP85105557A 1984-06-19 1985-05-07 Machine textile avec plusieurs unités de bobinage de fil à vitesse constante sur bobine conique Withdrawn EP0165428A3 (fr)

Applications Claiming Priority (1)

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

Publications (2)

Publication Number Publication Date
EP0165428A2 true EP0165428A2 (fr) 1985-12-27
EP0165428A3 EP0165428A3 (fr) 1986-08-20

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 After (1)

Application Number Title Priority Date Filing Date
EP85106573A Expired EP0165511B1 (fr) 1984-06-19 1985-05-29 Dispositif pour bobiner un fil livré à vitesse constante sur une 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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

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IN167890B (fr) * 1986-01-29 1991-01-05 Rieter Ag Maschf
EP0311815B1 (fr) * 1987-10-05 1992-06-03 W. SCHLAFHORST AG & CO. Méthode et dispositif pour égaliser la tension du fil pendant le rebobinage d'une cannette sur une bobine croisée
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
EP0343540B1 (fr) * 1988-05-25 1993-08-11 ELITEX koncern textilniho strojirenstvi Méthode et dispositif pour bobiner des fils en une bobine conique, particulièrement pour une machine textile avec un arrivage de fils constant
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 Schlafhorst & Co W Antriebsrolle für den rotatorischen Friktionsantrieb einer Textilspule
AU6270698A (en) 1997-02-05 1998-08-25 Plant Engineering Consultants, Inc. Precision winding method and apparatus
EP0950631B1 (fr) * 1998-02-14 2003-08-06 Volkmann GmbH Dispositif et procédé pour le bobinage de bobines coniques
US6691569B1 (en) * 2002-07-31 2004-02-17 The Goodyear Tire & Rubber Company Dual windup drum extensional rheometer
JP4712549B2 (ja) * 2005-12-08 2011-06-29 村田機械株式会社 ワインダー
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
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DE1912374C3 (de) * 1968-07-19 1974-08-08 Veb Spinnereimaschinenbau Karlmarx-Stadt, X 9010 Karl-Marx-Stadt Spulmaschine, insbesondere Kreuzspulmaschine
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DE2328993C2 (de) * 1973-06-07 1975-04-17 Barmag Barmer Maschinenfabrik Ag, 5600 Wuppertal Aufspuleinrichtung
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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
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
DE2458853A1 (de) * 1974-12-12 1976-06-16 Schlafhorst & Co W Wickeleinrichtung fuer konische, durch friktion angetriebene kreuzspulen
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
FR2836469A1 (fr) * 2002-02-22 2003-08-29 Dubourg Yann Frederic Etrier d'equitation a fixation automatique

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EP0165511A3 (en) 1986-08-13
SG86891G (en) 1992-02-14
EP0165511B1 (fr) 1989-05-24
US4789107A (en) 1988-12-06
EP0165428A3 (fr) 1986-08-20
EP0165511A2 (fr) 1985-12-27
DE3570423D1 (en) 1989-06-29
CS448485A3 (en) 1992-05-13
JPS6175775A (ja) 1986-04-18
HK31493A (en) 1993-04-08
DE3422637A1 (de) 1985-12-19

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