EP0886688B1 - Systeme d'alimentation en fil - Google Patents

Systeme d'alimentation en fil Download PDF

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Publication number
EP0886688B1
EP0886688B1 EP97915362A EP97915362A EP0886688B1 EP 0886688 B1 EP0886688 B1 EP 0886688B1 EP 97915362 A EP97915362 A EP 97915362A EP 97915362 A EP97915362 A EP 97915362A EP 0886688 B1 EP0886688 B1 EP 0886688B1
Authority
EP
European Patent Office
Prior art keywords
holder
axial
carrier ring
stroke adjustment
yarn feeder
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 - Lifetime
Application number
EP97915362A
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German (de)
English (en)
Other versions
EP0886688A1 (fr
Inventor
Kurt Arne Gunnar Jacobsson
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.)
Iro AB
Original Assignee
Iro AB
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Publication date
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Publication of EP0886688A1 publication Critical patent/EP0886688A1/fr
Application granted granted Critical
Publication of EP0886688B1 publication Critical patent/EP0886688B1/fr
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Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/364—Yarn braking means acting on the drum
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/364—Yarn braking means acting on the drum
    • D03D47/365—Brushes
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/364—Yarn braking means acting on the drum
    • D03D47/366—Conical
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2551/00—Means for control to be used by operator; User interfaces
    • B65H2551/20—Display means; Information output means

Definitions

  • the invention relates to a thread delivery device specified in the preamble of claim 1 Art.
  • the support ring can be only through the same stroke within the axial play in the bracket move the slide drives back and forth. Because the bracket in the boom in the axial direction can be adjusted, is also the braking effect between the brake body and the Thread take-off area of the storage drum either when the support ring is in contact with the an axial counterstop or when the support ring rests on the opposite one axial counter stop adjustable. However, the stroke of the Do not change the support ring, i.e. the difference between the braking effects in the two attachment points.
  • the object of the invention is to provide a thread delivery device of this type improve that the stroke of the support ring within the given axial play in the bracket is convenient and quick to change in addition to the given Adjustability of the bracket the difference between the braking effects in both End positions of the support ring can vary.
  • the offers in addition to the first axial Counterstop provided additional axial counterstop, which also has a stroke adjustment ramp can interact, another adjustment for the stroke the support ring in the holder.
  • the support ring can be easily rotated, to change the stroke.
  • the sloping transition surfaces also convey clearly noticeable movement transitions.
  • the rotary stops of the embodiment prevent a too wide Rotation adjustment of the support ring.
  • the cooperation takes place between everyone axial counterstop and a stroke adjustment ramp offset in the circumferential direction to the sliding drive instead.
  • the first axial counter-stop is in the area of the slide drive.
  • first axial Counter-facing axial side of the support ring stroke adjustment ramps arranged are connected to the first axial counter-stop in the direction of rotation of the support ring a receiving recess, which, if necessary, a further axial counter-stop forms, and the cooperation between the first axial counterstop and a lower stroke adjustment ramp in that the higher stroke adjustment ramp can enter the recess.
  • the sliding element forms of the sliding drive itself the first axial counter-stop of the bracket, the the support ring or the stroke adjustment ramps works together.
  • the support ring in the direction a slight brake intervention or -releasing position pushing elements pneumatically or magnetically only at Operated as needed, while the sliding elements acting in the opposite direction are permanent are acted upon.
  • both sliding drives are one Pair of pneumatic or magnetic slide actuators, which, preferably, in both Sliding directions are active and optionally applied.
  • the embodiment according to claim 15 is technically simple.
  • the stroke adjustment ramp groups can be realized with little formal effort.
  • the embodiment is according to claim 16 expedient.
  • the embodiment according to claim serves 17 the turning aid on the support ring.
  • the braking effect with elastic bristles, Fingers, lamellae or by means of an elastic ring membrane with a brake pad executes.
  • the basic braking effect can be achieved using the axial adjustment device the bracket in the boom.
  • the stroke of the support ring in the bracket is variable thanks to the stroke adjustment ramp, so that the difference between the Braking effects can change in the two end positions of the support ring.
  • FIGS. 1 and 2 which is a housing, not shown, with a drive motor and a bearing for one Storage drum 1 belongs.
  • the front end of the storage drum 1 is controllable Thread take-up brake B assigned, which is housed in a boom 6 fixed to the housing which extends along the outside of the storage drum 1.
  • Thread take-up brake B assigned, which is housed in a boom 6 fixed to the housing which extends along the outside of the storage drum 1.
  • Guides 24 arranged for a carriage 22, which is by means of an adjusting spindle or screw 23 can be adjusted parallel to the axis of the storage drum 1.
  • the boom carries a thread eyelet 5 for from one on the storage drum 1 in turns formed thread supply overhead and thread drawn off by the take-off brake B. (Not shown).
  • an annular holder 7 is connected, the one cone-shaped brake body 8, which in Fig. 1 from the right side through a removal opening E in the holder 7 and an outer, closed Support ring 9, preferably with a square cross section, and (in this Embodiment) of which bristles or tufts of bristles pointing obliquely inwards has whose inner ends defining a braking region 8a via a flexible Middle area 8b are supported on the support ring 9 and with a braking area 4 'in one Thread take-off area 4 of the storage drum work together in the usual way to slow down the thread running around the take-off.
  • the bracket 7 has the Scope distributed several pairs of sliding drives 10, 11 with which the support ring 9 within an axial play between axial counter-stops 20 and 21 of the holder 7 in the direction of the axis of the storage drum 1 is adjustable to and fro To change the braking effect between the braking area 8a and the braking area 4 '.
  • the axial counter stop 20 is, for example, a radial surface of the bracket 7 defined.
  • the opposite axial end stop 21 is, however, by the End faces of a plurality of housings 14 are formed, which are in rotary receptacles 16 of the holder 7 between an engagement position (FIGS. 1 to 3) and one in the release position (in FIG. 3 dash-dotted lines) are rotatable about the axis of a retaining screw 15.
  • each sliding drive 10 is a pneumatic one Sliding drive with a piston 10a in a chamber lined with a sleeve 13 12, which is connected to a pressure medium control 12 '.
  • Any sliding drive 11, on the other hand, consists of a spring 19 loaded in the housing 14 by a return spring Sleeve 18.
  • the sleeve 18 and the piston 10a form sliding elements that directly attack on the support ring 9 and this within the axial play between the axial Slide counter stops 20, 21 back and forth.
  • the sleeve 18 with the permanent acting return spring 19 could also be a piston in each sliding drive 11 provided and optionally pressurized from a controller.
  • Each axial counter-stop 20 could on the area of the sliding drive 10 be limited in the circumferential direction, so that the support ring at four in the circumferential direction distributed axial counter-stops can be intercepted. Between the counterstops 20 recesses 25 could be formed, the purpose of which will be explained later becomes.
  • Fig. 1 the pistons 10a are not acted upon pneumatically. Via the return spring 19 and the sleeves 18, the support ring 9 is held on the axial counter-stops 20. This corresponds to the position for a strong braking effect, e.g. using the adjusting spindle or screw 23 is adjustable.
  • Fig. 2 the pistons 10a are pressurized and extended so that the Support ring 9 is intercepted on the opposite axial counter-stops 21. This corresponds to a position for easier braking or a release position with little or no contact pressure of the braking area 8a against the braking area 4 'of the storage drum 1.
  • the thread delivery device F with the controlled draw-off brake B is preferred for or projectile looms for weft delivery to be used with every weft to vary the braking effect by controlling the trigger brake B.
  • the application the piston 10a takes place, for example, as a function of the work cycle of the assigned one Weaving machine.
  • Fig. 3 it can be seen how after pivoting away the housing 14 in the receptacle 16 in the dash-dotted position of the support ring 9 removed from the bracket 7 can be. It is also indicated how the housing 14 is in the engaged position of reaches inwards over the support ring 9 and supports it.
  • a turning aid 3 e.g. a molded-on pin can be provided, which is in the installed position the brake body 8 is accessible by hand and allows the support ring relatively to rotate the bracket 7. It is also on the axial side surface shown in FIG.
  • the support ring 9 a group 2 of several stroke adjustment ramps 2a, 2b and 2c different relative heights are provided, of which a stroke adjustment ramp is optional can be aligned with the axial counter-stop 21 formed by the housing 14.
  • the stroke adjustment ramp 2a, 2b or considered to be appropriate 2c the stroke of the support ring can be within the axial play in the holder 7 change, in the embodiment of FIG. 3 such that the support ring 9 each after selecting a stroke adjustment ramp 2a, 2b or 2c in the light braking or - Release position further or less far from the axial end stop 20.
  • the brake body 8 shown in FIG. 3 is a so-called bristle brake ring, which is equipped with bristles 33.
  • bristles 33 elastic fingers could also be used or plastic or steel slats can be anchored in the support ring 9.
  • Fig. 4 a section in the plane IV-IV of Fig. 3, it can be seen that the sliding drive 10 'in contrast to the pneumatic sliding drive of FIGS. 1 and 2, a magnetic Sliding drive with a magnet armature 10a 'and an actuating magnet 10' in the holder 7, while the sliding drive 11 is the sliding drive shown in FIG. 1 11 corresponds and is accommodated in a housing 14.
  • the support ring 9 is with two axial side surfaces 31 and 32 are formed.
  • the axial side surface 31 is flat and cooperates with the axial counter-stop 20 of the holder 7.
  • On the axial side surface 32 are offset in the circumferential direction and in alignment on the housing 14 - groups 2 of stroke adjustment ramps 2a, 2b, 2c different Heights provided.
  • the stroke adjustment ramp 2c lies here in the plane of the axial side surface 32.
  • the stroke adjustment ramp 2b is slightly opposite the axial side surface 32 before.
  • the stroke adjustment ramp 2a occurs even further opposite the axial side surface 32 before.
  • Between the stroke adjustment ramps 2a, 2b, 2c are oblique or rounded Transition surfaces 5 are provided.
  • One of the stroke adjustment ramps 2a, 2b, 2c works with the axial one Counterstop 21 together.
  • the stroke adjustment ramp 2a is on the axial counterstop 21 aligned, then the stroke of the support ring 9 is within the axial Game S between the axial counter-stops 20 and 21 a dimension a. However, it is Stroke adjustment ramp 2b aligned with the axial counter-stop 21, then that is Measure of the stroke of the support ring 9 b. Finally, the stroke adjustment ramp 2c on the axial counter stop 21 aligned, then the dimension of the stroke of the support ring 9 c. Otherwise, the slide drive 11 in FIG. 4 could also be a magnetic slide drive be, corresponding to the sliding drive shown in Fig. 4 above.
  • Fig. 5 is a section similar to that of Fig. 4 of an embodiment in which the Support ring 9 on the axial side surface 31 facing the piston 10a of the holder 7 with the number of axial counter-stops 20 corresponding to many groups 2 'of stroke adjustment ramps 2a ', 2b', 2c 'is formed.
  • group 2 'three are again different high stroke adjustment ramps shown, one of which with the axial side surface 31 matches.
  • the support ring 9 relative to the holder 7 on the axial counter-stop 20 receiving recesses 25 into which the higher Stroke adjustment ramps 2a ', 2b' can occur when the axial counter-stop 20 with the deepest stroke adjustment ramp 2c 'works together.
  • the axial counter-stop of the bracket 7 is here from the sliding element itself, i.e. the piston 10a formed in the chamber 12 in the retracted state can be intercepted at a stop 27 such that it extends far enough over the holder 7 protrudes to interact with the lowest stroke adjustment ramp of group 2 ' to be able to.
  • the brake body 8 having the support ring 9 is approximately frustoconical Rubber membrane 29 covering the elastic central area 8b of the brake body 8 and a brake pad 30 (indicated by dashed lines) as the braking area 8a wearing that in the form of a truncated cone-clad band made of steel or a low-wear Alloy is formed and adhered to the rubber membrane 29 such that the brake pad 30 cooperates with the braking area 4 'of the storage drum 1.
  • Fig. 7 that on the support ring 9 and on the bracket 7 on each other alignable markings 28 and 29 are provided to visually represent which stroke path is selected by selecting the respective stroke setting ramp of group 2 has been.
  • the slide drive 10 or the piston 10a offset in relation to the axial counter-stop 20 in the circumferential direction of the holder 7, so that the cooperation between the axial counter-stop 20 and one each Stroke adjustment ramp 2a ', 2b', 2c 'of group 2' not in the area of the slide drive 10 entry.
  • the middle stroke adjustment ramp 2b ' lies in the plane of the axial side surface 31; the stroke adjustment ramp 2c 'withdraws from the axial side surface 31; the stroke adjustment ramp 2a ', however, occurs opposite the axial side surface 31.
  • the axial counterstop 20 is delimited on both sides by receiving recesses 25.
  • the stroke adjustment ramps are not necessarily flat surfaces, but also domed or otherwise profiled to be able to have a certain centering positive fit when working together to reach.
  • the sliding drive could 10, however, can also be provided in the area of the axial counterstop 20 (dash-dotted line).
  • the axial counter-stops 20 and 21 work depending on the rotational position of the Support ring 9 with the stroke adjustment ramps so that the stroke of the support ring within the given axial play between the axial counter-stops 20 and 21 is not only changeable, but also in both shooting directions within the axial play is displaceable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Braking Arrangements (AREA)
  • Transmission Devices (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Actuator (AREA)

Claims (18)

  1. Système d'alimentation en fil comprenant un tambour d'enroulement (1) situé sur un carter, une console (6) de carter fixée sur le carter et un frein (8) de déroulement du fil commandé et maintenu de manière réglable dans le sens axial dans la console (6) de carter qui comprend un corps de freinage (8) annulaire coopérant avec la zone de déroulement du fil du tambour d'enroulement (1) et pourvu d'un anneau porteur (9) extérieur qui peut être déplacé dans le sens axial, dans une fixation (7) annulaire, dans les limites d'un jeu prédéterminé par des contre-butées axiales (20, 21) de la fixation (7), et comprenant au moins une paire de commandes coulissantes (10, 11) situées sur la fixation (7) et se mettant en prise dans des sens opposés sur l'anneau porteur (9) en vue du déplacement axial de l'anneau porteur (9) entre les contre-butées axiales (20, 21), caractérisé en ce que, pour allonger ou raccourcir la course de l'anneau porteur (9) dans les limites du jeu axial (S) dans la fixation (7), on prévoit, sur au moins une surface latérale axiale (31, 32) de l'anneau porteur (9), au moins une rampe (2a, 2b, 2a', 2b', 2c') de réglage de la course en saillie ou en retrait par rapport à cette surface latérale qui peut être alignée, par rotation de l'anneau porteur (9) dans la fixation (7), sur une première contre-butée axiale (21, 20, 10a, 20b, 20a, 20c) de la fixation (7) dirigée vers cette surface latérale axiale.
  2. Système d'alimentation en fil selon la revendication 1, caractérisé en ce qu'au moins une contre-butée axiale supplémentaire (25, 20c, 20b) est située dans la fixation (7) en plus de la première contre-butée axiale (20, 20a), et en ce que la contre-butée axiale supplémentaire fait saillie ou est en retrait dans le sens axial par rapport à la première contre-butée axiale.
  3. Système d'alimentation en fil selon la revendication 1, caractérisé en ce que la surface latérale axiale (31, 32) de l'anneau porteur (9) lui-même forme une rampe (2c, 2c', 2b', 2a', 2a) de réglage de la course à l'intérieur d'un groupe (2, 2') de rampes de réglage de la course.
  4. Système d'alimentation en fil selon au moins une des revendications 1 à 3, caractérisé en ce que l'on prévoit plusieurs paires de commandes coulissantes (10, 11) et plusieurs contre-butées axiales (20, 21) réparties sur la circonférence de la fixation (7), et en ce que l'on prévoit, sur la - au moins une - surface latérale axiale (31, 32) de l'anneau porteur (9), un nombre de groupes (2, 2') de rampes de réglage de la course correspondant au nombre des premières contre-butées (20, 21) tournées vers cette surface latérale axiale de l'anneau porteur et présentant des espacements circonférentiels qui correspondent aux espacements circonférentiels des premières contre-butées axiales.
  5. Système d'alimentation en fil selon au moins une des revendications 1 à 4, caractérisé en ce que la fixation (7) est pourvue, sur son côté axial dirigé vers la zone de déroulement (4) du tambour d'enroulement (1), d'une ouverture (E) de retrait de l'anneau porteur, en ce que plusieurs logements (14) comprenant chacun une commande coulissante (11) sont répartis autour du bord de l'ouverture de retrait (E) sur ce côté axial, en ce que chaque logement (14) sur la fixation (7) est installé de manière mobile entre une position d'engagement dans l'ouverture de retrait (E) et une position de dégagement qui libère l'ouverture de retrait et forme, dans la position d'engagement, la contre-butée axiale (21) pour l'anneau porteur (9), et en ce que les groupes (2) de rampes de réglage de la course sur l'anneau porteur (9) sont situés sur le côté axial (32) de celui-ci qui est tourné vers les logements (14).
  6. Système d'alimentation en fil selon l'une des revendications 1 ou 2, caractérisé en ce que l'on prévoit des groupes (2, 2') de rampes de réglage de la course sur les deux surfaces latérales axiales (31, 32) de l'anneau porteur (9) et des contre-butées resp. groupes de contre-butées sur les deux côtés axiaux dans la fixation (7).
  7. Système d'alimentation en fil selon la revendication 1, caractérisé en ce que l'on prévoit, dans chaque groupe (2), sur l'anneau porteur (9), au moins trois rampes (2a, 2b, 2c) de réglage de la course de hauteur différente.
  8. Système d'alimentation en fil selon la revendication 7, caractérisé en ce que l'on prévoit, à chaque fois, une surface de transition (5) oblique entre les rampes de réglage de la course successives du groupe (2, 2').
  9. Système d'alimentation en fil selon la revendication 7, caractérisé en ce que l'on prévoit des contre-butées de rotation (26) saillantes à l'extrémité de la première et de la dernière rampe (2a, 2c) de réglage de la course d'au moins un groupe (2, 2').
  10. Système d'alimentation en fil selon la revendication 1, caractérisé en ce que chaque première contre-butée axiale (20), le cas échéant avec la contre-butée supplémentaire (25), est décalée dans la direction circonférentielle de la fixation (7) par rapport à une commande coulissante (10a, 10).
  11. Système d'alimentation en fil selon la revendication 1, caractérisé en ce que la première contre-butée axiale (20, 21) de la fixation (7) entoure une ouverture de sortie d'un élément coulissant (10a, 18), et en ce qu'un évidement de réception (25) est contigu à la première contre-butée dans la direction circonférentielle de la fixation (7), lequel évidement forme, le cas échéant, une contre-butée supplémentaire.
  12. Système d'alimentation en fil selon la revendication 1, caractérisé en ce que la contre-butée axiale de la fixation (7) est un élément coulissant (10a, 18) d'une commande coulissante (10, 11), par exemple un piston ou une armature d'aimant, qui fait saillie hors d'une ouverture de sortie de la fixation (7) et peut prendre appui en rentrant dans la fixation (7), et en ce que le porte-à-faux de l'élément coulissant, lorsque l'élément coulissant (10a) est rentré dans la fixation (7) jusqu'à l'appui (27), correspond au moins à la différence de hauteur totale des rampes de réglage de la course du groupe (2').
  13. Système d'alimentation en fil selon au moins une des revendications 1 à 12, caractérisé en ce que la commande coulissante (10) de la paire (10, 11) qui se met en prise sur l'anneau porteur (9) dans le sens d'une position de prise légère pour freiner resp. position de dégagement est une commande coulissante pneumatique avec un piston (10a) ou une commande coulissante magnétique avec une armature d'aimant (10a'), en tant qu'élément coulissant respectif, et en ce que la commande coulissante (11) de la même paire qui se met en prise dans le sens opposé, de préférence sur une rampe de réglage de la course, comprend un élément coulissant (18) soumis à l'action d'un ressort de rappel (19) ou d'un aimant permanent.
  14. Système d'alimentation en fil selon au moins une des revendications 1 à 12, caractérisé en ce que les deux commandes coulissantes (10, 11) d'une paire sont des commandes coulissantes pneumatiques avec piston ou des commandes coulissantes magnétiques avec armature d'aimant en tant qu'éléments coulissants.
  15. Système d'alimentation en fil selon au moins une des revendications 1 à 14, caractérisé en ce que l'anneau porteur (9) est un préformé en matière plastique pourvu de groupes (2, 2') de rampes de réglage de la course formés de manière solidaire avec lui.
  16. Système d'alimentation en fil selon au moins une des revendications précédentes, caractérisé en ce que l'on trouve, sur l'anneau porteur (9) et sur la fixation (7), des marques (28, 29) pouvant être alignées les unes sur les autres dans le sens de rotation de l'anneau porteur (9) et indiquant des alignements par rotation entre les rampes de réglage de la course et les contre-butées axiales de la fixation, représentant différentes courses de l'anneau porteur (9).
  17. Système d'alimentation en fil selon au moins une des revendications précédentes, caractérisé en ce que l'on prévoit, sur l'anneau porteur (9), au moins un auxiliaire de rotation (3), par exemple une saillie, accessible dans la position d'encastrement du corps de freinage (8) dans la fixation (7).
  18. Système d'alimentation en fil selon au moins une des revendications 1 à 17, caractérisé en ce que le corps de freinage (8) comprenant l'anneau porteur (9) pourvu des rampes de réglage de la course est pourvu de poils, doigts, lamelles (33) élastiques ou d'une membrane annulaire élastique (29) avec une garniture de freinage (30) sous forme d'un anneau périphérique en cône tronqué, et son action de freinage au niveau de la zone de déroulement (4, 4') du tambour d'enroulement (1) peut être réglée au moyen d'un dispositif de réglage axial (22, 23, 24) de la fixation (7) situé dans la console (6).
EP97915362A 1996-03-13 1997-03-12 Systeme d'alimentation en fil Expired - Lifetime EP0886688B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19609871 1996-03-13
DE19609871A DE19609871A1 (de) 1996-03-13 1996-03-13 Fadenliefergerät
PCT/EP1997/001277 WO1997034035A1 (fr) 1996-03-13 1997-03-12 Systeme d'alimentation en fil

Publications (2)

Publication Number Publication Date
EP0886688A1 EP0886688A1 (fr) 1998-12-30
EP0886688B1 true EP0886688B1 (fr) 2000-06-21

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EP97915362A Expired - Lifetime EP0886688B1 (fr) 1996-03-13 1997-03-12 Systeme d'alimentation en fil

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US (1) US6095199A (fr)
EP (1) EP0886688B1 (fr)
DE (2) DE19609871A1 (fr)
WO (1) WO1997034035A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19839272B4 (de) * 1997-09-11 2007-02-01 Iro Sweden Ab Steuerbare Fadenbremse
DE202009017125U1 (de) * 2009-12-18 2010-04-15 Flexi-Bogdahn Technik Gmbh & Co. Kg Bremseinrichtung für eine Seilrolle einer mechanisch auf- und abrollbaren Leine zum Führen von Tieren

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4007131C2 (de) * 1990-03-07 1999-12-30 Iro Patent Ag Baar Liefervorrichtung für laufende Fäden
IT1251209B (it) * 1991-09-20 1995-05-04 Lgl Electronics Spa Dispositivo di frenatura autoregolante del filato per apparecchi alimentatori di trama.
IT1261331B (it) * 1993-11-05 1996-05-14 Lgl Electronics Spa Perfezionamento ai dispositivi di frenatura modulata positiva del filato per apparecchi alimentatori di trama.
SE9400248D0 (sv) * 1994-01-26 1994-01-26 Iro Ab Styrbar utgångsbroms för garnmatningsanordning till textilmaskiner, i synnerhet vävmaskiner av projektil eller gripar-typ
IT1268111B1 (it) * 1994-10-10 1997-02-20 Lgl Electronics Spa Dispositivo di frenatura modulata positiva del filato, per apparecchi alimentatori di trama

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Publication number Publication date
EP0886688A1 (fr) 1998-12-30
WO1997034035A1 (fr) 1997-09-18
DE19609871A1 (de) 1997-09-18
US6095199A (en) 2000-08-01
DE59701913D1 (de) 2000-07-27

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