EP0584432B1 - Rotor de tissage pour un métier à tisser multiphasé à foule linéaire - Google Patents

Rotor de tissage pour un métier à tisser multiphasé à foule linéaire Download PDF

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Publication number
EP0584432B1
EP0584432B1 EP92810663A EP92810663A EP0584432B1 EP 0584432 B1 EP0584432 B1 EP 0584432B1 EP 92810663 A EP92810663 A EP 92810663A EP 92810663 A EP92810663 A EP 92810663A EP 0584432 B1 EP0584432 B1 EP 0584432B1
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EP
European Patent Office
Prior art keywords
rotor
delivery
rotation
rotor according
weft
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
EP92810663A
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German (de)
English (en)
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EP0584432A1 (fr
Inventor
Marcel Christe
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.)
Itema Switzerland Ltd
Original Assignee
Sultex AG
Maschinenfabrik Rueti 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 Sultex AG, Maschinenfabrik Rueti AG filed Critical Sultex AG
Priority to EP92810663A priority Critical patent/EP0584432B1/fr
Priority to DE59206061T priority patent/DE59206061D1/de
Priority to US08/095,329 priority patent/US5406985A/en
Priority to JP21315093A priority patent/JP3486636B2/ja
Publication of EP0584432A1 publication Critical patent/EP0584432A1/fr
Application granted granted Critical
Publication of EP0584432B1 publication Critical patent/EP0584432B1/fr
Anticipated expiration legal-status Critical
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
    • D03D47/28—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein the weft itself is projected into the shed
    • D03D47/30—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein the weft itself is projected into the shed by gas jet
    • D03D47/3026—Air supply systems
    • D03D47/306—Construction or details of parts, e.g. valves, ducts
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D41/00—Looms not otherwise provided for, e.g. for weaving chenille yarn; Details peculiar to these looms
    • D03D41/005—Linear-shed multiphase looms
    • 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
    • D03D47/28—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein the weft itself is projected into the shed
    • D03D47/30—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein the weft itself is projected into the shed by gas jet
    • D03D47/3006—Construction of the nozzles
    • D03D47/302—Auxiliary nozzles
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/70—Devices for cutting weft threads

Definitions

  • the invention relates to a weaving rotor for a row shed weaving machine, in which relay nozzles are installed along the weft channels and can be actuated with air pulses.
  • a stationary and constantly pressurized air distribution system is installed inside the weaving rotor, which has transfer stations distributed on axis sections along the rotor axis. the transfer openings of which are offset from one another by an angle of rotation and the air in supply openings rotating relative to them feed air into supply channels for relay nozzles during the covering of the cross sections in order to generate a traveling field relative to the weaving rotor.
  • Such a weaving rotor is shown in patent specification EP 0 143 859.
  • a fixed switch tube with openings in the outer surface is close to the inside of the cylinder surface of a weaving rotor and feeds air into rotating holes in the cylinder jacket.
  • the openings in the switching tube lie on a helical line so that a traveling field is generated via the holes assigned to a row of combs, to which relay nozzles are connected.
  • a disadvantage of this arrangement is that the traveling field is predetermined by the geometry of the switching tube.
  • the maximum of the weft entry possible entry speed can only be used with a certain weaving width. If the weaving width is smaller than this, there will be unused pauses between the individual weft stops at the maximum possible entry speed.
  • the invention provides a remedy here.
  • the object of the invention is to use a certain weft insertion speed, which is provided for a maximum weaving width, even with smaller weaving widths, in that the shortening of the weft insertion leads to a corresponding shortening of the weaving cycle. According to the invention, the object is achieved by the features of independent claim 1.
  • the advantages of the invention can be seen in the fact that the total rotation angle available for the weft insertion can be set independently of the weaving width for a specific weft insertion speed. Furthermore, it is possible to optimize the blowing pressure and the helix of the transfer openings from the outside while the row shed weaving machine is running. At the transfer stations, there are only low frictional forces that are independent of the blowing pressure of the relay nozzles, which, due to the low heat generation, also allow heat-insulating and light materials such as relatively cheap plastics as wear-resistant sliding partners.
  • the dependent subclaims 2 to 17 relate to advantageous developments of the invention.
  • the figures show weaving rotors with relay nozzles, which are fed with compressed air within the weaving rotor by an air distribution system via transfer stations distributed in the axial direction in order to generate a traveling field relative to the weaving rotor.
  • the transfer stations each feeding a group of relay nozzles via a feed channel, are in The direction of rotation is adjustable and is connected to an adjusting device, by means of which the angle of rotation between the transfer openings of different transfer stations on the broad side of the weaving rotor can be adjusted. This enables the maximum possible weft insertion angle to be used at the highest possible weft insertion speed even with a reduced weaving width.
  • FIG. 1a a hatched traveling field 22 is plotted over the weaving width 36 for a weaving rotor 1 and depending on the weft insertion angle ⁇ developed for a weft channel 2 of the weaving rotor.
  • transfer openings 7 and transfer openings 17 are projected which, when covered, each supply air to a group 31 of relay nozzles 3 in the double-hatched area of the traveling field for axis sections 4.
  • the weaving rotor 1 is shown schematically in section across the weaving width 36 in FIG. 1a in FIG. 1b.
  • the weaving rotor 1 is equipped along its weft channels 2 with relay nozzles 3, which are combined in groups 31.
  • Each group 31 is supplied with compressed air on the inside of the weaving rotor by an associated transfer station 6, all transfer stations being part of an air distribution system 10 which is under constant pressure.
  • the transfer stations 6 are rotatably mounted within the weaving rotor 1 and can be adjusted in the direction of rotation via an adjusting device 33 on the broad side 73 and / or an adjusting device 27 (not shown here) on the opposite broad side 72.
  • the transfer stations 6 are supported by suitable torsion spring sections 9 in the direction of rotation against one another and to the broad sides 72, 73, and the air distribution system 10 connects the individual transfer stations 6 with hoses that are movable in the direction of rotation, a connecting tube being led out of the hollow weaving rotor 1 rotating in rotor bearings 67 is.
  • Weft channel 2 is interrupted at the end of weaving width 36 by a cutting gap 34, in which there is a cutting device 12 which limits the stretched weft thread to the final length.
  • the weft thread is stretched with a stretching device 13 located behind it, which generates a stretching field 35 shown in FIG. 1a.
  • the transfer stations 6 have, for each group 31 of the relay nozzles, a transfer opening 7 distorted in the direction of rotation, via which air is blown into rotating transfer openings 17 of the weaving rotor 1.
  • the blowing duration of the relay nozzles 3 is determined via a blowing angle 69, which corresponds to the distortion of the transfer opening 7 in the direction of rotation.
  • the transfer openings 7 of two adjacent transfer stations 6 are offset from one another by an angle of rotation 8 in the direction of rotation.
  • the angle of rotation 8 between two adjacent transfer stations can be changed and the total gradient of the traveling field 22 can be adapted to a new weaving width 36 in order to be able to keep the weft insertion angle ⁇ constant regardless of the weaving width.
  • the weaving width 36 was shortened for an embodiment corresponding to FIGS. 1a, b by removing the associated combs 37 of the outermost transfer station 6 from the weaving rotor 1 and the stretching device 13 and the cutting device 12 by the corresponding amount in the direction of Rotor axis were moved inwards.
  • the associated takeover opening 68 is blinded.
  • the original weft insertion angle ⁇ is achieved by increasing the angle of rotation 8 between the adjacent transfer stations which are adjustable in the direction of rotation.
  • an adjustment of the outermost torsion spring section in the direction of rotation is carried out on the adjusting device 33 and a greater torque is generated.
  • the angle of rotation 8 between adjacent transfer stations 6 increases. This rotation maintains the weft insertion angle and evenly divides the reduction in overlap between the groups 31 of relay nozzles involved.
  • FIG. 5 shows a preferred arrangement for the takeover openings 17 of a transfer station 6, which lie on a circle 38 in a parting plane 18 which is perpendicular to the rotor axis 5 of the weaving rotor 1.
  • the take-over openings 17 lie in the end face of a rotating ring body 48, which rotates connected to the weaving rotor.
  • the transfer opening 7 distorted in the direction of rotation 41 lies in a stationary ring 47, which is designed as a slip ring and bears against the rotating ring body 48 under slight pressure.
  • a stationary ring 47 For the duration of the covering of transfer and take-over openings, an air flow 16 arises which leads from a bore 92 via the parting plane 18 into the feed channel 11 to a group 31 of relay nozzles 3.
  • the stationary ring 47 is provided on its rear side with bores 46 which are intended for contact springs 44 and a pin provided as a rotation lock 30. Compensate the contact springs the position - tolerances in the end face of the rotating ring body 48.
  • FIGS. 8 and 9 show a compensation of the pressure-dependent opening force 23, which acts on the stationary ring 47 in an effective sealing surface 25 by the same pressure generating a closing force 24 on a counter surface 26, which corresponds approximately to the amount of the opening force 23.
  • the counter surface 26 is incorporated as the end face of a cylinder bore 59 from the rear of the stationary ring 47, a piston 49 protruding from a carrier body 20 with a soft seal 50 sealing against the blowing pressure on the cylindrical outer surface and permitting axial displacements of the stationary ring 47.
  • the blowing air passes through a bore 21 in the piston 49 and through a bore 92 into the transfer opening 7.
  • the blowing angle 69 is determined by the distortion of the transfer opening on the circle 38.
  • FIG. 3 shows a double-acting transfer station 6, in which an axially displaceable stationary ring 47 is held on the left and right by a carrier body 20 via pressure springs 44 and rotation lock 30.
  • the relay nozzle group is divided into a left and a right area, each of which is supplied with air by a piston 49.
  • the two pistons 49 with the transfer openings 7 are offset from one another in the direction of rotation by a fixed amount and also form an intermediate level in the hiking field.
  • Each of the two stationary rings 47 has a balance of the pressure-dependent opening force 23 and closing force 24.
  • FIGS. 3, 4, 6, 7 show a weaving rotor which has an air distribution system 10 with a tube 15 mounted concentrically in the weaving rotor.
  • the transfer stations 6 are rotatably supported with their carrier body 20 on the tube 15, which is supported on the rotating ring body 48 for better guidance via bearings 42 with attachment 65.
  • the ring bodies 48 rotating with the weaving rotor have a take-over opening 17 for each row of combs with a firing channel 2, followed by a feed channel 11 and a transition piece 39 to the relay nozzles 3, which at the same time seals and connects the rotating ring body 48 against the weaving rotor.
  • the carrier body 20 is sealed against the tube 15 with two O-rings 70, which include a slot 57 in the tube 15 between them, and is displaceable in the direction of rotation.
  • the torsion spring sections 9 are combined in a torsion bar 29 which is arranged concentrically in the tube 15 and has a square cross section.
  • the twist of the torsion bar 29 is transmitted at each transfer station by a rider 54, which is fastened on the torsion bar with a clamping screw 56 without play, via a driver screw 55 to the carrier body 20.
  • the slot 57 in the tube 15 is dimensioned so large that a desired adjustment range can be traversed in the direction of rotation and that there is sufficient free cross section from the tube 15 as an air passage to an annular groove between the O-rings 70 to the holes 21 in the Feed piston 49.
  • the riders 54 are dimensioned such that they can be rotated in the tube 15 and that they leave enough free cross-section in the axial direction for the air passage.
  • FIG. 3 shows this connection via a coupling piece 58, which is supported by a bearing 51 in the weaving rotor 1 and which seals the tube 15 at its end with an O-ring 53 and a locking screw 88 airtight.
  • the actual rotationally fixed connection takes place via a pin 52.
  • a soft seal 50 and a bearing lock 43 are shown for the bearing 51.
  • the tube 15, which is substantially more torsionally rigid than the torsion bar 29, serves as a mechanical transmission in order to transmit a twisting movement from a first adjusting device 27 on the broad side 73, as shown in FIG. 4, via an intermediate piece 32, while a further twisting movement on the same broad side 73 is carried out via a second adjusting device 33 at the other end of the torsion bar 29.
  • Both adjusting devices 27, 33 and tube 15 with intermediate piece 32 are fastened to the housing 28 via a sleeve 90. Independently of this, the weaving rotor 1 is supported in the housing 28 via a rotor bearing 67.
  • the first adjusting device 27 consists of a clamping flange 61 which is tightened by the intermediate piece 32 after the rotation.
  • the rotation is carried out on the torsion bar 29 via the screw 62 and the screw edge 63 and is then secured with a clamping flange 64.
  • the necessary screw connections are labeled 65.
  • FIGS. 10 and 11 An axially adjustable stretching device 13 is shown in FIGS. 10 and 11.
  • a ring 74 co-rotating with the weaving rotor 1 and axially displaceable is at a distance from the cutting gap 34 on the weaving rotor with fastening elements 87 e.g. Locking screws secured.
  • the weft channels 2 interrupted by the cutting gap 34 are continued in this ring 74, the ring 74 having an injector-like extension nozzle 71, which is interrupted transversely to each weft channel 2 and which deflects the weft thread tip while maintaining a stretching force transversely to the weft channel and the weft thread 40 in front the insertion into a cutting device and blows the cut weft tip through a nozzle half designed as a pull-off channel 78 into a stationary collecting device 77.
  • the ring 74 On the side facing away from the cutting gap 34, the ring 74 has an end face which is perpendicular to the rotor axis and in which an oblique bore 82 with a take-over opening 80 ends for each stretching nozzle 71.
  • the take-over openings 80 are at the same distance from the rotor axis 5 and are fed with compressed air for the duration of the overlap by a stationary air feed 79 via a transfer opening 75 distorted in the direction of rotation 41.
  • a stretching device 13 is also useful without a cutting device 12 in order to stretch the weft 40 before it strikes the fabric, in which case a cutting gap 34 can then be dispensed with.
  • FIG. 11 shows an embodiment in which the stationary air feed 79 takes place via a compressed air connection 81 on a first race, which is braced with a second race via coil springs 85 to form a pair of rings 83 between the ring 74 and a counter ring 84 fastened thereon.
  • Air feed 79 and the pair of rings 83 are prevented from rotating via an axially adjustable support arm 91 (see FIG. 2 b) connected to the housing 28 secured.
  • This arrangement with the pair of rings 83 has the advantage, as with the transfer stations 6, that the high-quality sliding surfaces, which have transfer and transfer openings, are covered by a counter surface of the same size in order to keep the risk of contamination and wear small.
  • a wedge for dirt particles can only arise at the transfer and take-over openings themselves, but this does not promote wear, since the latter is only flowed through by conditioned and pressurized air.
  • the pressure-independent balancing of forces at the transfer stations 6 and the low risk of contamination allow plastic to be used as a material for slide rings.

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

Claims (17)

  1. Rotor de tissage pour un métier à tisser à foules en série, dans lequel des buses alignées en série (3), qui peuvent être commandées par des impulsions d'air, sont installées le long des canaux pour duite (2), tandis qu'à l'intérieur du rotor de tissage (1) est installé un système stationnaire de distribution d'air (10) placé sous une pression constante, qui présente des postes de transfert (6) distribués sur des tronçons axiaux (4), le long de l'axe du rotor (5) et dont les ouvertures de transfert (7) sont décalées l'une par rapport à l'autre d'un angle de rotation (8) et qui, pendant le recouvrement des sections transversales, par des ouvertures de reprise (17) tournant par rapport à elles, introduisent de l'air dans des canaux d'amenée (11) vers les buses alignées en série (3) pour créer un champ d'ondes progressives (22) par rapport au rotor de tissage, caractérisé en ce que les postes de transfert (6) sont chacun reliés par l'intermédiaire d'un canal d'amenée (11) à au moins un groupe (31) de buses alignées en série (3), en ce que les postes de transfèrt (6) sont montés de manière ajustable dans le sens de la rotation à l'intérieur du rotor de tissage (1), et en ce qu'un ajustement de l'angle de rotation (8) entre les ouvertures de transfert (7) de différents postes de transfert (6) s'effectue par des éléments d'ajustement (27, 33), sur un des côtés transversaux ou sur les deux côtés transversaux (72, 73) du rotor de tissage.
  2. Rotor de tissage selon la revendication 1, caractérisé en ce que le système de distribution d'air (10) présente un tube (15) monté concentriquement dans le rotor de tissage, sur lequel les postes de transfert (6) sont montés à rotation et par lequel les postes de transfert (6) peuvent être alimentés en air par l'intermédiaire de fentes (57) s'étendant dans le sens de la rotation (41), même en cas d'ajustement mutuel de l'angle de rotation (8).
  3. Rotor de tissage selon la revendication 1 ou 2, caractérisé en ce que les postes de transfert (6) sont reliés les uns aux autres sur la largeur du rotor de tissage (1), par des éléments à ressort de torsion (9) qui ont pour effet une modification de l'angle de rotation (8) entre les ouvertures de transfert (7) de différents postes de transfert (6), en exerçant un couple de rotation ou par un ajustement en rotation de l'appui des éléments à ressort de torsion (9) contre les côtés transversaux (72, 73) du rotor de tissage.
  4. Rotor de tissage selon la revendication 3, caractérisé en ce que les éléments à ressort de torsion (9) sont reliés à une barre de torsion (29) continue, montée concentriquement dans le rotor de tissage, et par laquelle les postes de transfert (6) sont reliés à rotation solidaire.
  5. Rotor de tissage selon la revendication 4, caractérisé en ce que le tube (15) du système de distribution d'air (10) et la tige de torsion (29) sont reliés rigidement l'un à l'autre sur un côté transversal (72) du rotor de tissage (1) et peuvent être tournés l'un par rapport à l'autre par un dispositif d'ajustement (33) sur l'autre côté transversal (73) du rotor de tissage.
  6. Rotor de tissage selon l'une des revendications 1 à 5, caractérisé en ce que les ouvertures de transfert (7) vers les groupes (31) de buses alignées en série et les ouvertures de reprise (17) des canaux d'amenée (11) sont situées dans un plan de séparation (18) qui est perpendiculaire à l'axe (5) du rotor, et qu'elles se recouvrent momentanément pendant la rotation du rotor de tissage.
  7. Rotor de tissage selon la revendication 6, caractérisé en ce que chaque fois deux groupes (31) de buses alignées en série peuvent être alimentées par un poste de transfert (6), tandis que les ouvertures de transfert (7) sont décalées l'une de l'autre d'un angle de rotation (8) qui correspond au décalage moyen dans le sens de la rotation d'un champ d'ondes progressives entre ces deux groupes de buses alignées en série.
  8. Rotor de tissage selon la revendication 6 ou 7, caractérisé en ce que l'ouverture de transfert (7) et les ouvertures de reprise (17) associées à chaque série de dents de peigne (37) sont situées sur un cercle commun (38) dans le plan de séparation (18), et en ce que l'ouverture de transfert (7) attaque sur ce cercle (38) une plage angulaire plus grande qu'une ouverture de reprise (17).
  9. Rotor de tissage selon l'une des revendications 1 à 8, caractérisé en ce que l'ouverture de transfert (7) est montée de manière mobile par rapport aux ouvertures de reprise (17) et est comprimée sous une force élastique.
  10. Rotor de tissage selon l'une des revendications 6 à 9, caractérisé en ce qu'à une force d'ouverture (23) dépendant de la pression de distribution (21) et s'exerçant dans l'interstice d'étanchéité (19) entre l'ouverture de transfert et l'ouverture de reprise (7, 17) s'oppose une force de fermeture (24) dépendant également de la pression de distribution (21), par le fait que sur le corps porteur (20) de l'ouverture de transfert (7), une surface opposée (26) est attaquée par la pression de distribution.
  11. Rotor de tissage selon la revendication 10, caractérisé en ce que la somme des forces d'ouverture (23) créées dans l'interstice d'étanchéité par la pression de distribution et la surface d'étanchéité efficace (25) et la somme des forces de fermeture (24) créées sur la surface opposée (26) sont de même valeur.
  12. Rotor de tissage selon la revendication 11, caractérisé en ce que la surface opposée (26) est la surface qui, déduction faite de la section transversale de l'ouverture de transfert (7), est enfermée par un joint d'étanchéité cylindre/piston disposé entre le poste de transfert (6) et le corps porteur (20).
  13. Rotor de tissage selon l'une des revendications 1 à 5, caractérisé en ce que du côté de la sortie des fils de trame hors de la foule série, des tronçons des canaux pour duite sont fixés de manière à pouvoir être démontés avec les buses alignées en série (3) associées, et en ce que les canaux d'amenée (11) pour les buses alignées en série démontées peuvent être refermés pour utiliser les postes de transfert (6) restant pour une largeur de tissage (36) raccourcie, avec un écartement angulaire (8) mutuel agrandi.
  14. Rotor de tissage selon l'une des revendications 1 à 13, caractérisé en ce que du côté de la sortie de la duite, le rotor de tissage possède un dispositif d'étirage (13) pour la pointe du fil de trame, qui est constitué d'une bague (74) entraînée à rotation avec le rotor de tissage (1), qui présente transversalement à chaque canal pour duite une buse d'étirage (71) ressemblant à un injecteur et interrompue par le canal pour duite, et qui présente une alimentation stationnaire en air (79) comportant une ouverture de transfert (75) qui injecte dans des ouvertures de reprise (80) de la bague (74), tournant sur le même rayon, de l'air comprimé vers chaque buse d'étirage (71) associée ressemblant à un injecteur.
  15. Rotor de tissage selon la revendication 14, caractérisé en ce qu'en avant des buses d'étirage (71), transversalement par rapport aux canaux pour duite, il existe un interstice de coupe (34) pour le montage d'un dispositif de coupe (12) stationnaire, pour séparer les pointes des fils de trame des fils de trame (40) étirés, et pour les propulser dans un dispositif de reprise (77) par les buses d'étirage (71).
  16. Rotor de tissage selon la revendication 14, caractérisé en ce que la bague (74) tournant avec le rotor de tissage et l'alimentation stationnaire en air (79) peuvent être déplacées axialement sur le rotor de tissage pour remplir leur fonction avec différentes largeurs de tissage.
  17. Rotor de tissage selon la revendication 14, caractérisé en ce que l'alimentation stationnaire en air (79) est constituée d'une paire de bagues (83) reprise par la bague (74) entraînée en rotation et une bague opposée (84), et qui repose contre chaque bague entraînée en rotation (74, 84) avec un équilibrage des forces.
EP92810663A 1992-08-28 1992-08-28 Rotor de tissage pour un métier à tisser multiphasé à foule linéaire Expired - Lifetime EP0584432B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP92810663A EP0584432B1 (fr) 1992-08-28 1992-08-28 Rotor de tissage pour un métier à tisser multiphasé à foule linéaire
DE59206061T DE59206061D1 (de) 1992-08-28 1992-08-28 Webrotor für eine Reihenfachwebmaschine
US08/095,329 US5406985A (en) 1992-08-28 1993-07-21 Series-shed loom with adjustable airjet delivery system for different loom widths
JP21315093A JP3486636B2 (ja) 1992-08-28 1993-08-27 開口直列配置型の織機のロータ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP92810663A EP0584432B1 (fr) 1992-08-28 1992-08-28 Rotor de tissage pour un métier à tisser multiphasé à foule linéaire

Publications (2)

Publication Number Publication Date
EP0584432A1 EP0584432A1 (fr) 1994-03-02
EP0584432B1 true EP0584432B1 (fr) 1996-04-17

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EP92810663A Expired - Lifetime EP0584432B1 (fr) 1992-08-28 1992-08-28 Rotor de tissage pour un métier à tisser multiphasé à foule linéaire

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US (1) US5406985A (fr)
EP (1) EP0584432B1 (fr)
JP (1) JP3486636B2 (fr)
DE (1) DE59206061D1 (fr)

Families Citing this family (5)

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Publication number Priority date Publication date Assignee Title
DE59408476D1 (de) * 1994-05-30 1999-08-12 Rueti Ag Maschf Verfahren und Vorrichtung zum Eintrag von Schussfäden in eine Reihenfachwebmaschine
WO1996038612A1 (fr) * 1995-06-02 1996-12-05 SULZER RüTI AG Dispositif de repartition du fil de trame pour metier a tisser a ouverture des fils en serie
JPH11505898A (ja) * 1995-06-02 1999-05-25 ズルツァー・リューティ・アクチェンゲゼルシャフト エアージェット式織機
EP0980923A1 (fr) * 1998-08-19 2000-02-23 Sulzer Rüti Ag Dispositif pour l'insertion des fils de trame dans un métier à tisser multiphase et métier à tisser multiphase avec un tel dispositif
JP4420223B2 (ja) * 2004-11-16 2010-02-24 信越化学工業株式会社 スルフィド鎖含有有機珪素化合物の製造方法

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EP0049297B1 (fr) * 1980-10-02 1984-04-04 GebràœDer Sulzer Aktiengesellschaft Dispositif de commande pour les tuyères d'un métier à tisser à insertion par jet
DE3173916D1 (en) * 1981-11-25 1986-04-03 Sulzer Ag Control device for the jets of a jet weaving machine
EP0143859B1 (fr) * 1983-12-01 1987-03-11 Maschinenfabrik Sulzer-Rüti Ag Rotor de tissage pour métier à tisser pneumatique multiphasé à foule linéaire
JP2848684B2 (ja) * 1989-11-16 1999-01-20 ゲブリユーダー ズルツアー アクチエンゲゼルシヤフト よこ糸分配機構

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JP3486636B2 (ja) 2004-01-13
JPH07238440A (ja) 1995-09-12
DE59206061D1 (de) 1996-05-23
US5406985A (en) 1995-04-18
EP0584432A1 (fr) 1994-03-02

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