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WO1998012135A1 - Tendeur - Google Patents

Tendeur Download PDF

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Publication number
WO1998012135A1
WO1998012135A1 PCT/EP1997/005158 EP9705158W WO9812135A1 WO 1998012135 A1 WO1998012135 A1 WO 1998012135A1 EP 9705158 W EP9705158 W EP 9705158W WO 9812135 A1 WO9812135 A1 WO 9812135A1
Authority
WO
WIPO (PCT)
Prior art keywords
thread
ring
storage drum
brake according
thread brake
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.)
Ceased
Application number
PCT/EP1997/005158
Other languages
German (de)
English (en)
Inventor
Joachim Fritzson
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
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 Iro AB filed Critical Iro AB
Priority to DE59706446T priority Critical patent/DE59706446D1/de
Priority to EP97909298A priority patent/EP0927139B1/fr
Publication of WO1998012135A1 publication Critical patent/WO1998012135A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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

Definitions

  • the invention relates to a thread brake specified in the preamble of claim 1.
  • these thread brakes have a self-compensating effect in practice, i.e. that the tension in the drawn weft when changing speed does not vary as expected and is known from thread brakes used to be extremely varied, but has a relatively high value at low speed, but only a relatively moderate value at high speed.
  • the favorably narrow bandwidth of the tension variation is the main advantage of such thread brakes, since a perfect weft thread control is achieved with a reduced thread breakage rate.
  • the brake band made of thin sheet metal is arranged on the inside of a truncated cone-shaped carrier made of carbon fiber composite material.
  • the carrier is acted upon by a membrane or a spring device in the axial direction against the front end of the storage drum and keeps the brake band in contact with the rounded braking surface which is concentrically shaped on the storage drum.
  • the cone tip angle of the generatrix of the contact surface of the brake band is approximately 120 °.
  • the brake band which is in the form of a truncated cone ring, is fixed in a ring membrane made of rubber or elastomer at the inside diameter thereof.
  • the membrane is held on its outer diameter and is loaded with the axial preload that the brake band applies to the braking surface on the storage drum.
  • the cone tip angle of the brake band is approximately 120 °.
  • the braking surface is rounded, so that there is an approximately linear braking zone.
  • the brake band with the shape of a truncated cone is held in a foam ring which is held in the large-diameter end of a rigid, truncated cone-shaped hollow body.
  • a spring device acts on the hollow body, which generates the axial preload for the brake band.
  • the braking surface of the storage drum is conical, so that there is a flat and conical braking zone.
  • a flat, finite band with generators parallel to the storage drum axis rests under radial prestress on a cylindrical circumferential section of the storage drum.
  • the brake band is tensile but locally deformable.
  • the rigid brake element is made of metal with a disk or funnel shape and is placed under axial spring force against the radial braking surface at the front end of the storage drum.
  • the Brake element is, among other things, axially movably supported and is moved as a whole without any noteworthy deformation by the thread which rotates with the pointer movement between the braking surface and the braking element and is pulled off.
  • the invention has for its object to provide a thread brake for a weft thread drawn with a greatly varying thread speed of a weaving machine and with a response behavior with which a precisely predeterminable, relatively high basic tension in the thread is quickly obtained with a significant reduction in the thread speed.
  • the thread brake should preferably be suitable for rapier weaving machines, in which a precisely predeterminable, relatively high basic tension in the thread is required, especially in the transfer phase from the rapier rapier to the slave rapier, in order to support the cooperation between the weft thread and the bringer and the slave rapier from the weft thread.
  • the problem of centering the braking element on the storage drum is eliminated, which is particularly important because the smallest misalignment of a frustoconical braking element is an undesirable one Variation of the braking effect along the braking zone causes.
  • the combination of the stationary storage drum with the radial and, like the storage drum, non-rotatable ring achieves an optimum response of the thread brake especially for rapier weaving machines, which thanks to the position of the pulling eye and the structural separation between the pulling eye and the ring are free of deflection-related or friction-related axial force components of the thread works.
  • the ring is completely decoupled from the mass of the draw-off eyelet in the radial orientation with respect to the storage drum axis and carries out its work cycle in the braking zone without external influences, the axial preload against the braking surface being transmitted in such a way that the local deformability of the ring is preserved in the passage area of the circumferential weft. Thanks to the radial orientation of the ring, it does not require any measures for centering in relation to the braking surface, ie the center of the braking zone is defined by the center of the braking surface in all operating states.
  • a very uniform tension profile is achieved in the thread, which is possibly subject to dynamic influences that occur at high Thread speeds or strong accelerations can be different than at standstill and low speeds.
  • the deformation performance to be applied by the weft thread in the braking zone changes, but the performance of the weft thread also changes with the speed or with speed changes, for example because at higher speeds the force to be applied by the elastic structure of the thread Performance faster and is provided by a larger thread mass.
  • the rotatingly driven counter brake disc is centered relative to the storage drum by the pull-off eyelet which is connected to it in a materially integral manner.
  • the trigger eye forms a relatively large auxiliary mass, which is connected to the counter brake disc and whose own movements impair the response behavior of the counter brake disc during its working cycle.
  • the braking zone is theoretically flat, so that the braking power is provided with a specifically lower load. This can be cheaper for sensitive thread material. In practice, however, despite the surfaces interacting in the braking zone (braking surface and contact surface of the ring), only an approximately linear braking zone will be created.
  • the weft enters the braking zone early after the first 90 ° deflection. Due to the relatively large diameter of the braking zone, the specific rotational speed of the thread in the braking zone is low even at high thread speed, which can be advantageous for some applications.
  • the rotational speed of the thread is high in the braking zone with a relatively small diameter; however, the inertial forces influencing the response behavior of the ring are reduced, in particular if the outer diameter of the ring is as small as possible.
  • a response that is favorable for almost all thread qualities results according to claim 7, because the ring has a uniform deformation behavior along the braking zone.
  • Copper or steel or particularly durable and wear-resistant metal alloys can be used as the material.
  • Plastic with a wear-resistant surface and high fatigue strength can also be used.
  • the ring can be produced inexpensively because it can be formed from flat material blanks. Since the extremely precise centering of the braking zone in relation to the storage drum axis is determined exclusively by the braking surface, the outer or inner contours of the ring are only of secondary importance, i.e. an exact circular ring shape is not absolutely necessary, but the outer and / or inner circumference of the ring can be polygonal.
  • a largely homogeneous spring body made of elastic material is used to transmit the axial pressing force of the ring.
  • This Fe- the body is inexpensive to manufacture and hardly affects the local deformability of the ring in the passage area of the weft through the braking zone.
  • the total axial pretensioning force is divided, so to speak, into an infinite number of small axial force components, so that despite a relatively high total axial pretension of the thread in the passage area, only the relatively low resistance to deformation of the ring and only a few of the small axial force components of the total pretension have to be overcome.
  • the continuous weft thread forms a crescent-shaped gap between the contact surface of the ring and the braking surface, which rotates in wave-like fashion with the weft thread and is at most jointly responsible for the fact that the contribution of the thread brake to the take-off tension is unexpectedly low in the dynamic phase at a high thread speed level or with strong acceleration remains, that is, then the thread brake contributes as little as possible to the higher tension in the drawn thread due to the acceleration or high speed, while at low speed or when the weft thread is stopped the contribution of the thread brake to the thread tension, which is anyway low, is higher. At most, this results in the advantage of a relatively high basic tension at a low thread speed or at a standstill and a relatively narrow bandwidth of the thread pull tension change between low thread speed and maximum thread speed or at maximum deceleration or accelerations.
  • the ring is connected to the spring body for simplified assembly, e.g. glued. Only point-by-point gluing or continuous gluing is possible.
  • a plurality of coil springs are distributed in the circumferential direction or one or more concentric large coil springs are provided.
  • At least one spring support part is provided, which is expediently elastic.
  • a simple embodiment in terms of assembly and production technology can be found in claim 12.
  • the cap is used to hold the ring and the pull-off eyelet, with inertial forces and axial force components from the thread deflection being reliably kept away from the ring.
  • the axial preload can be changed by adjusting the cap in the holder of the delivery device.
  • the cap can be stably supported with its retaining flange.
  • a balloon limiter and / or thread brake ring is therefore provided, which is expediently carried by the cap and forces the thread into the precisely controlled pointer movement with which it rotates in the braking zone.
  • the balloon limiter or the thread brake ring could also be provided separately from the cap upstream of the braking zone.
  • the cap directly forms the balloon limiter with its edge area for perfect thread control.
  • FIG. 1 is a partially schematic longitudinal section of a weft feeder for a weaving machine with a first embodiment of a thread brake
  • FIG. 2 shows a schematic longitudinal section of another embodiment
  • 3 shows a partial section of a further embodiment
  • Fig. 4 is a plan view to illustrate the Bremsfunktio ⁇ in the thread brake.
  • a weft feeder F for a mechanical, unprotected weaving machine, in particular a rapier weaving machine or possibly also a projectile weaving machine (not shown), has in a housing 1 having a boom 2 a thread take-up element 3 which can be driven by a drive (not shown), the axis of rotation of which coincides with the axis X in an Operation stationary storage drum T is aligned.
  • the storage drum T has, for example, a drum body 4 with an outer circumferential surface that is rotationally symmetrical about the axis X.
  • Feed elements which may be present are not shown, by means of which windings 16 of a weft thread Y tangentially applied to the storage drum T by means of the winding member 3 are subjected to a feed movement from right to left in FIG. 1.
  • the storage drum T has on its front side, via which the weft yarn Y is drawn overhead and then axially pulled off the weaving machine, a braking surface 5 concentric with the axis X, namely a convexly rounded braking surface 5a in the embodiment shown in FIG. 1.
  • the braking surface 5, 5a is arranged and designed in such a way that it lies on a smaller diameter than the maximum outer diameter of the storage drum T, and that it is tangible from a radial plane to the axis X over the full circumference of the storage drum T.
  • a recess 6 in the front of the storage drum is connected inwardly to the braking surface 5, 5a! T on.
  • a thread brake B integrated into the delivery device F is assigned to the front of the storage drum T.
  • the thread brake B has a braking element E in the form of a ring 7 oriented radially to the axis X and made of a thin, flexible but tensile and wear-resistant material, the outside diameter of which in the embodiment shown is larger than the maximum outside diameter of the storage drum, and the inside diameter of which is slightly smaller than the diameter of the braking surface 5, 5a.
  • the ring 7 consists, for example, of thin sheet metal or thin plastic and has a bearing surface 20, the products of which are related to the X axis. is a straight line lying radially to the axis X.
  • the ring 7 is applied with the bearing surface 20 under axial prestress on the braking surface 5, 5a, so that an at least theoretically circular linear braking zone is formed between the ring 7 and the braking surface 5, 5a, the shape and centering of the axis X exclusively from the Formation of the braking surface 5, 5a depends.
  • the ring 7 expediently has a constant wall thickness, for example only a few tenths of a millimeter, and is acted upon on its rear side 21 by a spring body 8 which, in the embodiment shown, consists of a plurality of helical springs 9 distributed in the circumferential direction, which are provided via, expediently elastic, spring supports 10 - or alternatively Via a single spring support ring common to all coil springs 9 and also preferably made of elastic material (as 9 in FIG. 2) with approximately the same inside or outside diameter as the brake ring 7 - act on the rear side 21 of the brake ring 7.
  • a spring body 8 which, in the embodiment shown, consists of a plurality of helical springs 9 distributed in the circumferential direction, which are provided via, expediently elastic, spring supports 10 - or alternatively Via a single spring support ring common to all coil springs 9 and also preferably made of elastic material (as 9 in FIG. 2) with approximately the same inside or outside diameter as the brake ring 7
  • a withdrawal eye 11 is provided coaxially to the axis X, the inlet opening of which in FIG. 1 lies slightly to the right of the radial plane tangent to the braking surface 5, 5a.
  • the inlet mouth of the trigger eye 11 could also be offset further to the right compared to the position shown, but also further to the left, but not further to the left than into the radial plane tangent to the braking surface 5, 5a.
  • the ring 7 is expediently connected to the spring body 8 via the spring supports - alternatively via the common spring support ring mentioned above.
  • the spring body 8 and the trigger eyelet 11 are held in a cap 12 placed over the front of the storage drum T, in such a way that the ring 7 is structurally separated from the trigger eyelet 11.
  • the cap 12 is equipped with an outer holding flange 13, which is held in a holder 14 of the delivery device F.
  • the bracket 14 can be adjusted axially in the direction of a double arrow 15 in order to change the axial preload of the ring against the braking surface 5, 5a.
  • the holder 14 is expediently supported in the arm 2 of the housing 1.
  • a thread control element 25 for example a so-called bristle ring or, can be arranged in the further edge region of the cap 12 a balloon breaker ring.
  • the bristle ring has the task of preventing the thread running from the last of the windings 16 into the braking zone between the ring 7 and the braking surface 5, 5a from forming a balloon and / or forcing it into a pointer movement around the center of the trigger eye 11, ie check the weft Y so that it runs approximately radially into the braking zone and rotates in the circumferential direction with an essentially radial orientation.
  • the cap 12 or an equivalent holding part could also be supported on a stationary holder which is separate from the delivery device F. Furthermore, it is conceivable to support the trigger eye 11 separately from the spring body 8, so that the trigger eye 11 does not change its preselected position when the cap 12 is adjusted axially.
  • the braking surface 5 is displaced radially inward to a considerably smaller diameter than in FIG. 1.
  • the braking surface 5 is here a flat circular ring surface 5b with an alignment radially to the axis X, on which the ring 7, which is also radially aligned, is flat with the axial bias of the spring body 8 is applied.
  • the storage drum T has a conveniently convexly rounded trigger edge 17 near the front, from which a transition 18 to the braking surface 5, 5b extends. Instead of a transition 18 guiding the thread with contact, a stepped or hollowed-out transition 24 could also be provided.
  • the spring body 8 is formed in the embodiment of FIG.
  • a thread control element in the form of a brake ring for example a bristle ring 25 as in the embodiment according to FIG. 1, should be involved, the function and role of which becomes all the more important the smaller the diameter of the brake surface in relation to the maximum storage drum diameter where the braking element E works.
  • Fig. 3 illustrates a further embodiment in which the ring 7 defining the braking element E is connected with its rear side to a spring body 8, which consists of elastic material such as rubber, plastic or foam and can be designed as a type of double spiral spring with an internal cavity.
  • Fig. 4 illustrates in a plan view how the drawn weft Y is pulled in the braking zone between the ring 7 and the braking surface 5, 5a, 5b and rotates in the direction of arrow 23 with the aforementioned pointer movement.
  • the weft Y presses the bearing surface 20 of the ring 7 away from the braking surface 5a, 5b, 5 in an approximately crescent-shaped gap area and thereby also deforms the spring body 8, here a spring body made of elastic, largely homogeneous material 9 *.
  • This local deformation of the ring 7 runs in a wave-like manner with the weft Y.
  • the braking effect for the weft decreases, in addition to that, due to the dynamics with the rapidly rotating and quickly withdrawing weft, the ring can, so to speak, come into a kind of floating state relative to the braking surface, during which the specific braking effect is not to the extent actually expected has increased. If the thread speed drops drastically from the highly dynamic braking state at high thread speed with a relatively mild braking effect, possibly until the weft thread comes to a standstill when changing to a rapier weaving machine, then the thread brake responds immediately thanks to the radial orientation of ring 7 and its decoupling relative to the draw-off eye. so that the draw-off tension in the drawn-off state again exactly achieves the relatively high value of the base draw-off tension, which is required for the properly proceeding transfer process in the rapier weaving machine.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)

Abstract

L'invention concerne un tendeur situé dans un fournisseur de duites (F) pour métier à tisser à navettes à pince, comportant une surface de freinage montée (5, 5a, 5b), sur la face avant, de manière concentrique, sur un tambour d'accumulation (T), un oeillet de dévidage coaxial (11) et un élément de freinage (E) maintenu de manière à ne pas tourner, réalisé dans un matériau résistant à la rupture par traction et à l'usure, à fine paroi et déformable localement, qui est comprimé dans le sens axial contre la surface de freinage de manière à faire ressort, avec une surface d'appui (20) continue dans le sens périphérique, et qui définit conjointement avec la surface de freinage une zone de freinage pour les duites tournant lors du dévidage aoutour de l'oeillet de dévidage (11), avec un mouvement d'aiguille. La surface de freinage (5, 5a, 5b), dans le sens du dévidage, constitue la délimitation du tambour d'accumulation (T) et l'élément de freinage (E) est un anneau plan (7), situé dans le sens radial par rapport au tambour d'accumulation (T) qui est sollicité à la manière d'un ressort sur sa face opposée (21) à la surface d'appui (20), de manière qu'en dépit de cette sollicitation par ressort, sa déformabilité locale demeure inchangée dans la zone de passage de la duite (Y), là où elle traverse la zone de freinage. L'oeillet de dévidage (11) est séparé de l'anneau (7) et son embouchure d'entrée est placée dans le sens axial derrière la surface de freinage (5, 5a, 5b) ou à la rigueur dans son plan radial.
PCT/EP1997/005158 1996-09-20 1997-09-19 Tendeur Ceased WO1998012135A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE59706446T DE59706446D1 (de) 1996-09-20 1997-09-19 Fadenbremse
EP97909298A EP0927139B1 (fr) 1996-09-20 1997-09-19 Tendeur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19638618A DE19638618A1 (de) 1996-09-20 1996-09-20 Fadenbremse
DE19638618.7 1996-09-20

Publications (1)

Publication Number Publication Date
WO1998012135A1 true WO1998012135A1 (fr) 1998-03-26

Family

ID=7806365

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1997/005158 Ceased WO1998012135A1 (fr) 1996-09-20 1997-09-19 Tendeur

Country Status (3)

Country Link
EP (1) EP0927139B1 (fr)
DE (2) DE19638618A1 (fr)
WO (1) WO1998012135A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1292765B1 (it) * 1997-06-11 1999-02-11 Lgl Electronics Spa Perfezionamento ai dispositivi di frenatura modulata autoregolata del filato per apparecchi alimentatori di trama a macchine tessili

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2303746A2 (fr) * 1975-03-10 1976-10-08 Roy Electrotex Spa Dispositif d'amenee de file a tension constante et reglable, particulierement pour l'utilisation dans les machines textiles et de bonneterie
WO1991014032A1 (fr) * 1990-03-12 1991-09-19 Iro Ab Frein de sortie de fil
US5316051A (en) * 1991-09-20 1994-05-31 L.G.L. Electronics S.P.A. Self-adjusting thread braking device for weft feeder units
WO1994020402A1 (fr) * 1993-02-23 1994-09-15 Nuova Roj Electrotex S.R.L. Predelivreur de fil
DE4336994C1 (de) * 1993-10-29 1995-03-30 Heinrich Fabschitz Fadenliefervorrichtung mit stufenlos einstellbarer Fadenabzugspannung
DE9406102U1 (de) * 1994-04-13 1995-08-10 Sobrevin Société de brevets industriels-Etablissement, Vaduz Fadenspeicher mit Fadenabzugsbremse
DE19542045A1 (de) * 1995-11-10 1997-05-15 Iro Ab Fadenliefergerät

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2303746A2 (fr) * 1975-03-10 1976-10-08 Roy Electrotex Spa Dispositif d'amenee de file a tension constante et reglable, particulierement pour l'utilisation dans les machines textiles et de bonneterie
WO1991014032A1 (fr) * 1990-03-12 1991-09-19 Iro Ab Frein de sortie de fil
US5316051A (en) * 1991-09-20 1994-05-31 L.G.L. Electronics S.P.A. Self-adjusting thread braking device for weft feeder units
WO1994020402A1 (fr) * 1993-02-23 1994-09-15 Nuova Roj Electrotex S.R.L. Predelivreur de fil
DE4336994C1 (de) * 1993-10-29 1995-03-30 Heinrich Fabschitz Fadenliefervorrichtung mit stufenlos einstellbarer Fadenabzugspannung
DE9406102U1 (de) * 1994-04-13 1995-08-10 Sobrevin Société de brevets industriels-Etablissement, Vaduz Fadenspeicher mit Fadenabzugsbremse
DE19542045A1 (de) * 1995-11-10 1997-05-15 Iro Ab Fadenliefergerät

Also Published As

Publication number Publication date
DE59706446D1 (de) 2002-03-28
EP0927139B1 (fr) 2002-02-20
EP0927139A1 (fr) 1999-07-07
DE19638618A1 (de) 1998-03-26

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