EP0396501B1 - Machine à tisser avec dispositif de tension flexible pour chaîne - Google Patents

Machine à tisser avec dispositif de tension flexible pour chaîne Download PDF

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Publication number
EP0396501B1
EP0396501B1 EP90810265A EP90810265A EP0396501B1 EP 0396501 B1 EP0396501 B1 EP 0396501B1 EP 90810265 A EP90810265 A EP 90810265A EP 90810265 A EP90810265 A EP 90810265A EP 0396501 B1 EP0396501 B1 EP 0396501B1
Authority
EP
European Patent Office
Prior art keywords
tensioning
warp
tensioning element
weaving machine
drive shaft
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
EP90810265A
Other languages
German (de)
English (en)
Other versions
EP0396501A1 (fr
Inventor
Angelo Stacher
Rudolf Vogel
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
Gebrueder Sulzer 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, Gebrueder Sulzer AG filed Critical Sultex AG
Publication of EP0396501A1 publication Critical patent/EP0396501A1/fr
Application granted granted Critical
Publication of EP0396501B1 publication Critical patent/EP0396501B1/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
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/04—Control of the tension in warp or cloth
    • D03D49/12—Controlling warp tension by means other than let-off mechanisms
    • D03D49/14—Compensating for tension differences during shedding
    • 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
    • D03D49/04—Control of the tension in warp or cloth
    • D03D49/18—Devices for indicating warp tension

Definitions

  • the invention relates to a loom with a tensioning device for tensioning warp threads of a so-called warp, consisting of a spring-loaded tensioning element for the warp threads with simultaneous deflection, one end of a spring being articulated on the tensioning element, the other end of which is mounted on the machine side, and an adjustment mechanism for the bias of the spring (23) in time with the working cycles of the loom.
  • Such a device is known from Japanese Patent Publication 63-67575.
  • the warp threads are deflected by a tensioning boom that runs across the machine width and are kept tensioned, which is held in pivotable end shields.
  • a tension spring engages on an extension of each end shield, which on the other hand engages at the end of a lever which is pivotally fixed in the machine frame and at the other end of which a push rod is articulated.
  • One end shield is attached to this lever near the fulcrum of the lever.
  • the push rod can be moved back and forth in the machine cycle by means of a crank mechanism, which causes the lever to pivot and the bearing plate fixed thereon to move approximately in translation be transferred.
  • the spring end mounted on the lever end is also moved essentially translationally, the movements of the end shield and the fastening point of the spring being directed in opposite directions. Simultaneously with the formation of the warp threads, the combined movements of the lever and the end shield on the one hand shift the warp towards the shedding organs, and on the other hand the warp tension is reduced.
  • the exemplary embodiment in the Japanese publication shows that the tensioning element, a roller, is attached to at least two bearing plates, which in turn are seated on at least two levers, each with two springs. A crank of the crank mechanism engages at each end of the lever.
  • a practical embodiment of the example shown schematically would have numerous individual parts which cannot be moved at high frequency. Too many mass-related parts are between the drive device and the warp threads.
  • Another device for tensioning warp threads is known from EP 0 136 389.
  • the warp beam is followed by a stationary, rod-shaped deflection element for the warp threads in the warp running direction, and a deflection element that is movable under spring action is also connected downstream of the deflection element.
  • a sensing element of a control device is also arranged, through which the tension or the respectively over Deflection element and spanning tree leading path of the warp threads are scanned and the warp thread lowering speed is set accordingly.
  • the tensioning boom is passively movable under spring action, whereby a particularly large, resulting force acts on the feeler element by means of a corresponding pretensioning of its return spring, which enables precise adjustment of the warp thread lowering speed. Due to the inert mass of the tensioning tree and the feeler as well as the passive, springy tensioning of the tensioning tree, this device reacts extremely sluggishly to changes in tension of the warp threads and is therefore unsuitable, for example, to keep the warp threads under an approximately constant tension during the weaving cycle by means of the shafts more or less deflected.
  • This object is achieved in that the adjusting mechanism acts on the machine-side end of the spring in the form of a torsion bar which lies on the pivot axis of the tensioning element for tensioning the warp and in turn with a drive shaft of the tensioning device is connected in a rotationally fixed manner, and in that there are bearing points for the rolling bearing of the tensioning element, which are distributed rotationally symmetrically with respect to its axis of rotation, with the drive shaft being distributed over the weaving width.
  • a deflection element can be arranged in the running direction of the warp threads in front of the tension element, the axis of rotation of the tension element, the pivot axis of the drive shaft and the center of the deflection element forming the corner points of an approximately equilateral triangle.
  • the warp threads are deflected by the deflecting element and the tensioning element approximately by the same angle from an approximately vertical direction in a horizontal direction, the bisector of the angle formed by the warp threads between the deflection element and the tensioning element and the warp threads running off the tensioning element just outside the corner point at the Drive shaft of the triangle mentioned passes.
  • the distance between the bisector and the swivel axis can be very small, for example 1/10 of the distance between the axis of the tensioning element and the swivel axis of the drive shaft.
  • the device can have a sensor for detecting a signal which represents a measure of the relationship between warp thread consumption in the weaving machine and the subsequent delivery of warp threads from the warp beam, which signal is transmitted to a control device for the device.
  • a drive motor for the warp beam for unwinding the warp threads is connected to the control device.
  • the sensor can be designed, for example, as a force sensor for registering the pretensioning force in the device.
  • the drive shaft of the tensioning device is in at least two bearings within the machine frame of the weaving machine carried. Several bearing points for the tensioning element are attached to the drive shaft, which in turn carry rollers in which the tensioning element is mounted.
  • the device can work at an operating point at which the tensioning element is in a position in which the resulting force from the warp threads passes just short of the pivot axis of the tensioning element.
  • the torque in the drive shaft for the tensioning device thus remains very small, which is why a weak spring is sufficient to preload the drive shaft.
  • the forces and loads within the clamping device remain very small, which is why the parts of the clamping device can be easily dimensioned and are therefore suitable for high working frequencies.
  • the weaving machine 1 contains a main drive motor 13, which can be coupled to a main shaft 13 '.
  • a shaft drive unit 15 ' can be coupled to the main shaft 13' by means of a clutch 13 ''.
  • a pair of bevel gears 15 ′′ ensures the transmission of the drive energy to the shafts 15, which are connected to the shaft drive unit 15 ′.
  • the push rod 34 is interrupted by a force sensor 35, which registers the forces in the push rod.
  • the warp threads 11 ' which are processed in the weaving machine, are wound on a warp beam 12 as a warp chain 11.
  • the warp threads 11 ' run through the shafts 15 and are alternately raised and lowered by them.
  • the tensioning device 2 with a deflection element 25 and a tensioning element 22 serves to keep the warp threads 11 'tensioned when these are more or less deflected by means of the shafts.
  • the clamping element 22 of the clamping device 2 has a plurality of bearing points 24 for a rolling mounting of the clamping element 22, these bearing points being firmly connected to a drive shaft 22.
  • a spring 23 extends in the form of a torsion bar to the adjusting mechanism 3, which acts on a hub at the end of the spring 23.
  • a control line 35a runs from the force sensor 35 to the control unit 14, which performs the control functions of, for example, the main drive motor 13 via the control line 13a or the drive motor 12 'for the warp beam 12 via a control line 12a.
  • the force measured by the force sensor 35 increases and exceeds a border guard, the control unit 14 causes a higher speed of the drive motor 12 '.
  • the drive shaft 33 with the eccentric 33 ′ and then the push rod 34 with the built-in force sensor 35 can be seen in an enlarged illustration in a side elevation of the weaving machine according to FIG. 1.
  • the push rod is essentially pushed back and forth in the direction of the double arrow 34 '.
  • An adjusting device 37 for adjusting the length of the push rod 34 can be seen below the double arrow 34 '. This also achieves the basic setting of the clamping device.
  • the push rod 34 engages a hinge point on the lever 36, which is non-rotatably connected to the end of the torsion bar 23.
  • FIG. 2 also shows a cross member 16 ', the deflection element 25 and the tensioning element 22, furthermore a support 16' 'for the deflection element 25 and tensioning element 22, which is screwed onto the cross member 16'.
  • the tensioning element 22, which can be pivoted with the torsion bar 23, ensures a length compensation in the warp threads when these are pulled into different positions by the shafts 15.
  • FIG. 3 is a view of the arrangement according to FIG. 2 in the direction of arrow A.
  • the cross member 16 ' is screwed, which holds several carriers 16''distributed over the width of the weaving machine.
  • the drive shaft 21 which is rotatable about the pivot axis 21 'is mounted in the carriers 16''.
  • the bearings 24 are screwed to the drive shaft 21.
  • the torsion bar 23 is non-rotatably connected to the drive shaft 21 at one end by means of the driver 23 ′′, on the other hand it is non-rotatably seated within the Hub 23 ', which is supported by the cross member 16' in rolling bearings.
  • the lever 36 is screwed onto the hub 23 '.
  • FIG. 4 parts of the tensioning device 2 are again shown enlarged compared to FIG. 2.
  • a stationary deflection element 25 deflects the warp threads 11 'from an approximately vertical position in the direction of the tensioning element 22, which is supported by a plurality of rollers distributed over the weaving width and held by bearing points 24. Due to the multiple mounting of the tensioning element 22 on the rollers 24 ', the tensioning element can be made relatively thin. The rollers 24 'ensure easy rotation of the tensioning element about its own axis.
  • the unit tensioning element 22, bearing points 24, drive shaft 21 can perform rapid pivoting movements, since the mass moment of inertia of this unit is relatively small compared to the device mentioned at the outset according to the Japanese publication.
  • the unit tensioning element', bearing point 24 ', drive shaft 21 can very quickly follow the longitudinal displacement of the warp threads, this being due to the kinematic conditions
  • Clamping element 22 rotates on its own axis on rollers 24 '.
  • the intermediate element 11 ′′ a migrates, for example, from the extended position into the dashed position.
  • the resulting force W or W 'generated by the warp threads 11' or 11a lies on the bisector of the line formed by the warp thread course 11 ', 11''or11'a or 11''a.
  • the values are dimensionless and should indicate the tendency when the clamping element 22 changes position.
  • the torque increases approximately twice as a result of the warp thread tensions with respect to the pivot axis 21 ′.
  • the pivoting angle of the tensioning element 22 is shown in FIG. 5 with ⁇ , the value of which is 9 °.
  • the dimensions of the spring or of the torsion bar 23, that is to say the length and diameter of the spring, are to be selected such that the torque increase during the additional rotation by the angle ⁇ in the torsion bar also increases from the value 480 to the value 1035.
  • the pivot angle ⁇ of the tensioning element 22 is approximately equal to the angle of rotation of the machine-side end of the spring 23 due to the movement of the adjusting mechanism 3, the torsion of the spring 23 also remains approximately constant, so that the torque in the tensioning device 2 due to the torsion of the spring 22 does not varies widely.
  • the pivoting angle of the lever 36 generated by the adjusting mechanism 3, the pretensioning of the torsion bar or the spring 23 and the geometric conditions in the tensioning device 2, that is to say the relative position of the tensioning element 22, the pivot axis 21 'and the deflection element 25 to one another, are selected in a clever manner, so can with a practically constant tension in the warp threads 11 ', 11''or11'a,11''a even with a larger swivel angle ⁇ of the tensioning device can be calculated, which is necessary with a larger longitudinal displacement and change in position of the warp threads 11 '' or 11''a due to larger strokes of the shafts 15.
  • the warp threads 11 would generate frictional forces due to their relative movement on the surface of the tensioning element 22 when the tensioning element changes position and thus also a frictional torque which, in relation to the torque due to Force would be relatively large.
  • the additional frictional moment would disturb the balance between the moment due to the warp thread tension and the torque generated by the prestressing of the torsion bar 23 in the opposite direction, which would also have adverse effects on the tension in the warp threads.
  • the prestressing of the tensioning element 22 is effected with a low-mass spring 23 and that the tensioning element 22 itself is mounted on several rollers and consequently also has only weak dimensions.
  • This is the only way to ensure that the tensioning device can react sensitively to displacements of the warp threads 11 '' or 11''a, the tension fluctuations in the warp threads induced by the inherent dynamics of the tensioning device also remaining negligible.
  • the tension fluctuations i.e. the difference between the largest and the lowest tension values, also remain relatively small.
  • a lower stress in the warp is to be expected, which also results in fewer disruptions in weaving operations, for example due to warp thread breaks.

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

Claims (8)

  1. Machine à tisser équipée d'un dispositif tendeur (2) destiné à tendre les fils de chaîne (11') d'une dénommée chaîne de tissage, ce dispositif se composant d'un élément (22) tendeur des fils de chaîne qui est supporté élastiquement et qui en provoque également une déviation, une extrémité d'un ressort (23) étant articulée sur l'élément tendeur (22), tandis que son autre extrémité est montée du côté machine (23'), ainsi que d'un mécanisme d'ajustement (3) destiné à agir sélectivement sur la précontrainte du ressort (23) à la cadence des, et pendant les, cycles de travail de la machine à tisser, caractérisée en ce que le mécanisme d'ajustement (3) attaque l'extrémité (23') côté machine du ressort (23) qui a la forme d'une barre de torsion qui est située sur l'axe (21') d'oscillation de l'élément tendeur (22) de la chaîne de tissage et qui de son côté est solidarisée en rotation avec un arbre (21) de commande du dispositif tendeur, et en ce que des points d'appui (24) assurant un support à roulement (24') de l'élément tendeur (22) sont solidaires en rotation de l'arbre de commande (21) et son répartis sur l'empeignage, l'élément tendeur (22) étant symétrique de révolution par rapport à son axe de rotation (22').
  2. Machine à tisser selon la revendication 1, caractérisée en ce que le mécanisme d'ajustement (3) est formé d'un levier (36) attaquant le ressort (23), d'une bielle (34) reliée par articulation à ce levier et d'un excentrique (33') monté sur l'autre extrémité de la bielle (34) et disposé sur un arbre (33) de commande du mécanisme d'ajustement (3).
  3. Machine à tisser selon les revendications 1 et 2, caractérisée en ce qu'un dynamomètre (35) est monté dans le mécanisme d'ajustement (3) dans le prolongement de la bielle (34).
  4. Machine à tisser selon les revendications 1 - 3, caractérisée en ce que le dynamomètre (35) est connecté par un conducteur de commande (35a) à un appareil de commande (14) qui est en relation fonctionnelle par un conducteur de commande (12a) avec un moteur (12') de commande d'une ensouple de chaîne (12) sur laquelle la chaîne de tissage (11) est enroulée.
  5. Machine à tisser selon la revendication 1, caractérisée en ce que les points d'appui (24) sont fixés sur l'arbre de commande (21) et supportent des galets (24') sur lesquels l'élément tendeur (22) prend appui en étant librement rotatif.
  6. Machine à tisser selon la revendication 1, caractérisée en ce qu'en complément de l'élément tendeur (22) qui dévie les fils de chaîne (11'), un élément de déviation (25) est disposé devant l'élément tendeur (22) par rapport au sens de défilement des fils de chaîne (11') et en ce que l'axe de rotation (22') de l'élément tendeur (22), l'axe d'oscillation (21') de l'arbre de commande (21) et le centre (25') de l'élément de déviation (25) forment les sommets d'un triangle à peu près équilatéral.
  7. Machine à tisser selon la revendication 6, caractérisée en ce que l'élément de déviation (25) et l'élément tendeur (22) dévient tous deux les fils de chaîne (11') à peu près du même angle, d'une orientation sensiblement verticale à une orientation horizontale, la bissectrice (W) de l'angle formé par les fils de chaîne entre l'élément de déviation (25) et l'élément tendeur (22) et les fils de chaîne (11') défilant à la sortie de l'élément tendeur (22) passe à peine à l'extérieur du sommet du triangle mentionné qui est situé sur l'arbre de commande (21), la distance H2 comprise entre la bissectrice de l'angle et l'axe d'oscillation (21') ne correspondant à peu près qu'à 1/10 de la distance (L) comprise entre l'axe (22') de l'élément tendeur et l'axe d'oscillation (21').
  8. Machine à tisser selon la revendication 5, caractérisée en ce que les surfaces de roulement des galets (24') sont en matière plastique, par exemple en Vulkollan.
EP90810265A 1989-05-02 1990-04-03 Machine à tisser avec dispositif de tension flexible pour chaîne Expired - Lifetime EP0396501B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1670/89A CH681156A5 (fr) 1989-05-02 1989-05-02
CH1670/89 1989-05-02

Publications (2)

Publication Number Publication Date
EP0396501A1 EP0396501A1 (fr) 1990-11-07
EP0396501B1 true EP0396501B1 (fr) 1993-08-18

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ID=4215867

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EP90810265A Expired - Lifetime EP0396501B1 (fr) 1989-05-02 1990-04-03 Machine à tisser avec dispositif de tension flexible pour chaîne

Country Status (7)

Country Link
US (1) US5090453A (fr)
EP (1) EP0396501B1 (fr)
JP (1) JP2706551B2 (fr)
CN (1) CN1023575C (fr)
CH (1) CH681156A5 (fr)
DE (1) DE59002365D1 (fr)
RU (1) RU2001978C1 (fr)

Families Citing this family (14)

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Publication number Priority date Publication date Assignee Title
DE4427129C2 (de) * 1994-07-30 1998-07-30 Dornier Gmbh Lindauer Spanneinheit für die Webkette einer Webmaschine
DE4427126C2 (de) * 1994-07-30 1998-09-17 Dornier Gmbh Lindauer Spanneinheit für die Webkette in einer Webmaschine
DE19538121C1 (de) * 1995-10-13 1997-02-27 Dornier Gmbh Lindauer Ungesteuerte Spanneinheit für die Webkette einer Webmaschine
BE1011184A3 (nl) * 1997-05-28 1999-06-01 Picanol Nv Inrichting voor het bepalen van de kettingspanning.
DE19740309A1 (de) * 1997-09-13 1999-06-10 Dornier Gmbh Lindauer Verfahren und Vorrichtung zum Einstellen eines Streichbaums und Kettwächters einer Webmaschine zur Erzeugung einer bestimmten Fachgeometrie
EP0937796A1 (fr) * 1998-02-18 1999-08-25 Sulzer Rüti Ag Dispositif de tension des fils de chaine pour métier à tisser et métier à tisser avec un tel dispositif
US6056112A (en) * 1998-05-20 2000-05-02 Argonics, Inc. Apparatus for preloading a scraper blade in a conveyor cleaning system
IT1304112B1 (it) * 1998-12-17 2001-03-07 Vamatex Nuova Spa Portafili a sospensione progressiva per telaio di tessitura
ITMI20030182A1 (it) * 2003-02-04 2004-08-05 Promatech Spa Disposizione di portafili perfezionata per un telaio tessile
DE102005028127A1 (de) * 2005-06-10 2006-12-14 Picanol N.V. Frottierwebmaschine
DE102006020586B4 (de) * 2006-05-02 2008-08-28 Oerlikon Textile Gmbh & Co. Kg Verfahren und Vorrichtung zum Erzeugen von Wattewickeln aus textilen Faserwatten
JP4973142B2 (ja) * 2006-11-17 2012-07-11 株式会社豊田自動織機 パイル織り織機における経糸張力制御装置
JP2009293151A (ja) * 2008-06-05 2009-12-17 Tsudakoma Corp 織機のテンションロール支持機構
DE102013219942A1 (de) * 2013-10-01 2015-04-02 Lindauer Dornier Gesellschaft Mit Beschränkter Haftung Verfahren und Vorrichtung zum Aufbringen von Kräften und Bewegungen auf Kettfäden einer Webmaschine

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Publication number Priority date Publication date Assignee Title
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US2912014A (en) * 1956-05-21 1959-11-10 John D Wells Loom attachment
CS190998B1 (en) * 1977-09-07 1979-06-29 Otto Rotrekl Back rail mechanism for weaving looms
EP0109472B1 (fr) * 1982-10-26 1986-09-10 GebràœDer Sulzer Aktiengesellschaft Dispositif pour tendre la chaîne à une machine à tisser
EP0136389B1 (fr) * 1983-10-03 1986-11-12 Maschinenfabrik Sulzer-Rüti Ag Mécanisme de contrôle du déroulement de fils de chaîne pour métier à tisser
CH661754A5 (de) * 1983-10-04 1987-08-14 Saurer Ag Adolph Regeleinrichtung fuer den drehantrieb einer abwickelvorrichtung.
CH667294A5 (de) * 1985-02-14 1988-09-30 Saurer Diederichs Sa Streichbaumanordnung an einer webmaschine.
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DE2910528A1 (de) * 1978-05-09 1979-11-15 Alsacienne Constr Meca Kreuzschienenanordnung fuer einen webstuhl

Also Published As

Publication number Publication date
CN1046948A (zh) 1990-11-14
DE59002365D1 (de) 1993-09-23
JP2706551B2 (ja) 1998-01-28
US5090453A (en) 1992-02-25
RU2001978C1 (ru) 1993-10-30
CH681156A5 (fr) 1993-01-29
EP0396501A1 (fr) 1990-11-07
CN1023575C (zh) 1994-01-19
JPH02293447A (ja) 1990-12-04

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