EP0396501A1 - Loom with easy-going warp tension device - Google Patents

Loom with easy-going warp tension device Download PDF

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Publication number
EP0396501A1
EP0396501A1 EP90810265A EP90810265A EP0396501A1 EP 0396501 A1 EP0396501 A1 EP 0396501A1 EP 90810265 A EP90810265 A EP 90810265A EP 90810265 A EP90810265 A EP 90810265A EP 0396501 A1 EP0396501 A1 EP 0396501A1
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EP
European Patent Office
Prior art keywords
tensioning
warp threads
drive shaft
tensioning element
warp
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.)
Granted
Application number
EP90810265A
Other languages
German (de)
French (fr)
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EP0396501B1 (en
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
Sulzer AG
Sultex AG
Gebrueder Sulzer AG
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Publication date
Application filed by Sulzer AG, Sultex AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0396501A1 publication Critical patent/EP0396501A1/en
Application granted granted Critical
Publication of EP0396501B1 publication Critical patent/EP0396501B1/en
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    • 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 shedding 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 fastened 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.
  • 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 deflecting 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 is 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 prestressing 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 past 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, according to FIG. 1, a main drive motor 13 which can be coupled to a main shaft 13 '.
  • a clutch 13 mit a shaft drive unit 15 'can be coupled to the main shaft 13'.
  • a bevel gear pair 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 loom, are wound on a warp beam 12 as a warp 11.
  • the warp threads 11 ' run through the shafts 15 and are alternately raised and lowered by them.
  • the tensioning device 2 with a deflecting 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 engages a hub at the end of the spring 23.
  • a control line 35a runs to the control unit 14, which performs the control functions, for example, of 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 a side view of the loom according to FIG. 1 in an enlarged view.
  • the push rod is pushed back and forth in the direction of the double arrow 34 '.
  • Below the double arrow 34 'an adjusting device 37 for adjusting the length of the push rod 34 can be seen. 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 is still a cross member 16 ', the deflecting element 25 and the clamping element 22 can be seen, further a support 16' for deflecting element 25 and clamping element 22, which is screwed to the cross member 16 '.
  • the warp threads 11 'come in Fig. 2 from below from the warp beam, not shown, are deflected by the deflecting element 25 and the tensioning element 22.
  • 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 of FIG. 2 in the direction of arrow A.
  • the cross member 16 ' is screwed, which holds several across the width of the weaving machine 16 Anlagen.
  • rotatable drive shaft 21 is mounted in the carriers 16 'about the pivot axis 21' rotatable drive shaft 21 is mounted.
  • 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 a mecanic, on the other hand it is rotatably seated within the Hub 23 ', which is carried in rolling bearings by the cross member 16'.
  • the lever 36 is screwed.
  • 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 several rollers distributed over the weaving width and held by bearing points 24. Due to the multiple storage 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 clamping element about its own axis.
  • the unit clamping element 22 ', bearings 24', drive shaft 23 can perform swivel 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 33 can follow the longitudinal displacement of the warp threads very quickly, due to the kinematic conditions Clamping element 22 'rotates about its own axis on the rollers 24'.
  • the intermediate element 11a moves the tensioning element 22, for example, from the extended position to 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 ⁇ or 11'a or 11 ⁇ a.
  • the values are dimensionless and should indicate the tendency when the clamping element 22 changes position.
  • 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 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 chosen so so can with a practically constant tension in the warp threads 11 ', 11 ⁇ or 11'a, 11 ⁇ a even with a larger pivot 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 rotatability of the relatively thin tensioning element 22 on several rollers 24 'in the bearing points 24 makes it possible to choose the geometry of the entire tensioning device in such a way that the resulting force W of the warp threads in the extended position of the tensioning element 22 is only a short distance away the pivot axis 21 'passes.
  • the torque generated thereby is therefore comparatively small, so that the torsion bar 23, the lever 36 and the entire adjustment mechanism 3 can be dimensioned weak.
  • the warp threads 11 would generate frictional forces due to their relative movement on the surface of the tensioning element 22 in the event of a change in position of the tensioning element 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 pretensioning 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.
  • 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)

Abstract

A tension device (2) of a loom (1) is formed from a tension element (22) mounted rotatably on a plurality of rollers (24') and resting on a drive shaft (21) at a plurality of bearing points (24) distributed over the length of the tension element. The drive shaft (21) is prestressed by a torsion bar (23), on the end (23') of which engages an adjusting mechanism (3) driven by means of an eccentric (33). The tension device (2) consists of only a few parts of small dimensions and it can therefore adapt very quickly to changes in position of the warp yarns (11). It is consequently suitable for high-speed looms, by means of which sensitive warp yarns are processed. …<IMAGE>…

Description

Die Erfindung betrifft eine Webmaschine mit einer Spann­vorrichtung zum Spannen von Kettfäden einer sogenannten Webkette, bestehend aus einem federnd abgestützten Spann­element für die Kettfäden bei gleichzeitiger Umlenkung, wobei am Spannelement ein Ende einer Feder angelenkt ist, dessen anderes Ende maschinenseitig gelagert ist, und ei­nem Verstellmechanismus für die Vorspannung der Feder (23) im Takt mit den Arbeitszyklen der Webmaschine.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.

Eine derartige Einrichtung ist aus der japanischen Patent­publikation 63-67575 bekannt. Die Kettfäden werden von einem über die Maschinenbreite verlaufenden Spannbaum um­gelenkt und dabei gespannt gehalten, wobei dieser in schwenkbaren Lagerschilden gehalten wird. An einem Fort­satz jeweils eines Lagerschildes greift eine Zugfeder an, welche andererseits am Ende eines schwenkbar im Maschinen­gestell fixierten Hebels angreift, an dessen anderes Ende eine Schubstange angelenkt ist. Jeweils ein Lagerschild ist auf diesem Hebel nahe dem Drehpunkt des Hebels befe­stigt. Die Schubstange kann mittels eines Kurbeltriebes im Maschinentakt hin und her bewegt werden, wodurch der Hebel in eine Schwenkbewegung und der darauf fixierte Lager­schild in eine angenähert translatorische Bewegung versetzt werden. Das am Hebelende gelagerte Federende wird ebenfalls im wesentlichen translatorisch bewegt, wobei die Bewegungen des Lagerschildes und des Befestigungspunktes der Feder gegensinnig gerichtet sind. Gleichzeitig mit der Fachbildung der Kettfäden soll durch die kombinierten Be­wegungen des Hebels und des Lagerschildes einerseits die Webkette in Richtung auf die Fachbildungsorgane verschoben werden, andererseits wird die Kettspannung reduziert. Das Ausführungsbeispiel in der japanischen Publikation lässt erkennen, dass das Spannelement, eine Walze, an mindestens zwei Lagerschilden befestigt ist, welche wiederum auf min­destens zwei Hebeln mit jeweils zwei Federn sitzen. Je­weils an einem Hebelende greift eine Kurbel des Kurbel­triebs an. Eine praktische Ausführung des schematisch ge­zeigten Beispieles würde zahlreiche Einzelteile aufweisen, welche nicht mit hoher Frequenz bewegt werden können. Zu viele massenbehaftete Teile befinden sich zwischen der Antriebsvorrichtung und den Kettfäden. Demzufolge müsste man mit unkontrollierbaren Schwingungen im System rechnen, insbesondere bei einer Ausführungsform für schweres Gewebe und bei höheren Drehzahlen, die bei Luftwebmaschinen bis zu 1000 Umdrehungen pro Min. betragen können. Die Schwin­gungen würden starke Spannungsschwankungen in den Kettfä­den erzeugen, was zu Kettfadenbrüchen führen kann und den Betriebsnutzeffekt der Webmaschine mindert.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 shedding 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 fastened 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. Accordingly, one would have to expect uncontrollable vibrations in the system, in particular in an embodiment for heavy fabrics and at higher speeds, which can be up to 1000 revolutions per minute in air-jet weaving machines. The vibrations would produce large fluctuations in tension in the warp threads, which can lead to warp thread breaks and reduce the operating efficiency of the weaving machine.

Es ist Aufgabe der Erfindung, ein leichtgängiges angetrie­benes Spannsystem für eine Webkette einer Webmaschine zu schaffen, das auch für schweres Gewebe geeeignet ist und sensibel auf Spannungsschwankungen in der Kette bzw. auf Positionsänderungen im Antrieb des Systems reagiert. Diese Aufgabe wird dadurch gelöst, dass der Verstellmachanismus am maschinenseitigen Ende der Feder in Form eines Torsi­onsstabes angreift, der auf der Schwenkachse des Spannele­mentes zum Spannen der Webkette liegt und seinerseits mit einer Antriebswelle der Spannvorrichtung drehfest verbun­den ist, und dass drehfest mit der Antriebswelle über die Webbreite verteilte Lagerstellen für eine rollende Lage­rung des Spannelements vorhanden sind, welches bezüglich seiner Drehachse rotationssymmetrisch ist. Zusätzlich zu dem die Kettfäden umlenkenden Spannelement kann ein Um­lenkelement in Laufrichtung der Kettfäden vor dem Spann­element angeordnet sein, wobei die Drehachse des Spannele­mentes, die Schwenkachse der Antriebswelle und das Zentrum des Umlenkelementes die Eckpunkte eines annähernd gleich­seitigen Dreiecks bilden. Die Kettfäden werden durch das Umlenkelement und das Spannelement annähernd um je densel­ben Winkel aus einer annähernd vertikalen Richtung in eine horizontale Richtung umgelenkt, wobei die Winkelhalbieren­de des durch die Kettfäden zwischen Umlenkelement und Spannelement und die vom Spannelement ablaufenden Kett­fäden gebildeten Winkels knapp ausserhalb des Eckpunktes bei der Antriebswelle des erwähnten Dreiecks vorbeiläuft. Die Distanz zwischen der Winkelhalbierenden und der Schwenkachse kann sehr klein sein, beispielsweise 1/10 des Abstands zwischen der Achse des Spannelements und der Schwenkachse der Antriebswelle.It is an object of the invention to provide a smooth-running driven tensioning system for a weaving chain of a weaving machine, which is also suitable for heavy fabrics and which reacts sensitively to tension fluctuations in the warp or to changes in position in the drive of the system. 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. In addition to the tension element deflecting the warp threads, 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 deflecting 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.

Die Vorrichtung kann einen Sensor zur Erfassung eines Si­gnals aufweisen, das ein Mass für das Verhältnis zwischen Kettfadenverbrauch in der Webmaschine und der Nachliefe­rung von Kettfäden vom Kettbaum her darstellt, welches Signal an ein Steuergerät für die Vorrichtung übermittelt wird. An das Steuergerät wird in einer vorteilhaften Aus­führung der Vorrichtung ein Antriebsmotor für den Kettbaum zum Abwickeln der Kettfäden angeschlossen. Der Sensor kann beispielsweise als Kraftsensor zur Registrierung der Vor­spannkraft in der Vorrichtung ausgebildet sein. Die An­triebswelle der Spannvorrichtung wird in mindestens zwei Lagern innerhalb des Maschinengestells der Webmaschine getragen. An der Antriebswelle sind mehrere Lagerstellen für das Spannelement befestigt, welche ihrerseits Rollen tragen, in welchen das Spannelement gelagert ist.The device can have a sensor for detecting a signal, which is 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. In an advantageous embodiment of 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 prestressing 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.

Durch die grosse Empfindlichkeit aufgrund der geringen Masse und der reibungsarmen Lagerung des Spannelementes kann die Vorrichtung in einem Betriebspunkt arbeiten, bei dem das Spannelement in einer Position steht, in der die resultierende Kraft von den Kettfäden knapp an der Schwenkachse des Spannelementes vorbeigeht. Das Drehmoment in der Antriebswelle für die Spannvorrichtung bleibt somit sehr klein, weshalb auch eine schwache Feder zur Vorspan­nung der Antriebswelle genügt. Somit bleiben die Kräfte und Belastungen innerhalb der Spannvorrichtung sehr klein, weshalb die Teile der Spannvorrichtung leicht dimensio­niert werden können und dadurch für hohe Arbeitsfrequenzen geeignet sind.Due to the high sensitivity due to the low mass and the low-friction mounting of the tensioning element, 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 past 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. Thus, 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.

Im folgenden wird die Erfindung anhand der Zeichnungen 1 - 5 näher erläutert.

  • Fig. 1 zeigt einen schematischen Grundriss einer Webma­schine mit der Erfindung zusammenhängende Funk­tionselementen einer Webmaschine,
  • Fig. 2 ist eine Detailansicht einer Spannvorrichtung in Längsrichtung der Webmaschine,
  • Fig. 3 ist eine Detailansicht der Spannelemente mit dem Kettfadenverlauf in einer Ansicht gemäss Pfeil A in Fig. 2,
  • Fig. 4 zeigt Details der Vorrichtung ähnlich wie in Fig. 2,
  • Fig. 5 zeigt zwei Arbeitsstellungen der Spannvorrich­tung in schematischer Darstellung mit den Kräf­teverhältnissen aufgrund der Spannung der Kett­fäden.
The invention is explained in more detail below with reference to drawings 1-5.
  • 1 shows a schematic plan view of a weaving machine functional elements of a weaving machine related to the invention,
  • 2 is a detailed view of a tensioning device in the longitudinal direction of the weaving machine,
  • 3 is a detailed view of the tensioning elements with the warp thread course in a view according to arrow A in FIG. 2,
  • 4 shows details of the device similar to that in FIG. 2,
  • Fig. 5 shows two working positions of the tensioning device in a schematic representation with the force relationships due to the tension of the warp threads.

Die Webmaschine 1 enthält gemäss Fig. 1 unten einen Haupt­antriebsmotor 13, der mit einer Hauptwelle 13′ kuppelbar ist. Mittels einer Kupplung 13˝ kann ein Schafttriebsag­gregat 15′ mit der Hauptwelle 13′ gekuppelt werden. Ein Kegelradpaar 15 ˝ sorgt für die Uebertragung der Antriebs­energie zu den Schäften 15, die mit dem Schafttriebsaggre­gat 15′ verbunden sind. Auf einer Antriebswelle 33, mit der Hauptantriebswelle 13′ koppelbar, sitzt ein Exzenter 33′, der eine Schubstange 34 eines Verstellmechanismus 3 für die Spannvorrichtung 2 antreibt. Die Schubstange 34 ist durch einen Kraftsensor 35 unterbrochen, der die Kräf­te in der Schubstange registriert. Die Kettfäden 11′, wel­che in der Webmaschine verarbeitet werden, sind auf einem Kettbaum 12 als Webkette 11 aufgewickelt. Sie werden mit­tels eines Antriebsmotors 12′ vom Kettbaum 12 abgewickelt, wobei der Kettbaum 12 mit dem Antriebsmotor 12′ über ein Zahnradpaar 12˝ verbunden ist. Die Kettfäden 11′ laufen durch die Schäfte 15 und werden durch diese abwechselnd gehoben und gesenkt. Die Spannvorrichtung 2 mit einem Um­lenkelement 25 und einem Spannelement 22 dient dazu, die Kettfäden 11′ gespannt zu halten, wenn diese mittels der Schäfte mehr oder weniger ausgelenkt werden. Das Spannele­ment 22 der Spannvorrichtung 2 besitzt mehrere Lagerstel­len 24 für eine rollende Lagerung des Spannelements 22, wobei diese Lagerstellen fest mit einer Antriebswelle 22 verbunden sind. Konzentrisch mit der Schwenkachse 21′ des Spannelements und gleichzeitig Drehachse der Antriebswelle 21 erstreckt sich eine Feder 23 in Form eines Torsionssta­bes zum Verstellmechanismus 3, welcher an eine Nabe am Ende der Feder 23 angreift. Vom Kraftsensor 35 verläuft eine Steuerleitung 35a zum Steuergerät 14, das die Steuer­funktionen beispielsweise des Hauptantriebsmotors 13 über die Steuerleitung 13a oder des Antriebsmotors 12′ für den Kettbaum 12 über eine Steuerleitung 12a wahrnimmt. Nimmt die vom Kraftsensor 35 gemessene Kraft zu und übersteigt einen Grenzweft, wird vom Steuergerät 14 eine höhere Dreh­zahl des Antriebsmotors 12′ bewirkt.The weaving machine 1 contains, according to FIG. 1, a main drive motor 13 which can be coupled to a main shaft 13 '. By means of a clutch 13 mit a shaft drive unit 15 'can be coupled to the main shaft 13'. A bevel gear pair 15 ˝ ensures the transmission of the drive energy to the shafts 15, which are connected to the shaft drive unit 15 '. On a drive shaft 33, with the main drive shaft 13 'can be coupled, an eccentric 33' sits, which drives a push rod 34 of an adjusting mechanism 3 for the clamping device 2. 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 loom, are wound on a warp beam 12 as a warp 11. They are processed by means of a drive motor 12 'from the warp beam 12, the warp beam 12 being connected to the drive motor 12' via a gear pair 12 '. The warp threads 11 'run through the shafts 15 and are alternately raised and lowered by them. The tensioning device 2 with a deflecting 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. Concentric with the pivot axis 21 'of the clamping element and at the same time the axis of rotation of the drive shaft 21, a spring 23 extends in the form of a torsion bar to the adjusting mechanism 3, which engages a hub at the end of the spring 23. From the force sensor 35, a control line 35a runs to the control unit 14, which performs the control functions, for example, of 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 '.

In Fig. 2 sind in einem Seitenriss der Webmaschine gemäss Fig. 1 in vergrösserter Darstellung die Antriebswelle 33 mit dem Exzenter 33′ und daran anschliessend die Schub­stange 34 mit dem eingebauten Kraftsensor 35 zu sehen. Die Schubstange wird in Richtung des Doppelpfeils 34′ im we­sentlichen hin und her geschoben. Unterhalb des Doppel­pfeils 34′ ist eine Einstellvorrichtung 37 zur Verstellung der Länge der Schubstange 34 zu sehen. Damit wird auch die Grundeinstellung der Spannvorrichtung erreicht. Die Schub­stange 34 greift an einen Gelenkpunkt am Hebel 36 an, wel­cher drehfest mit dem Ende des Torsionsstabes 23 verbunden ist. In Fig. 2 ist weiterhin eine Traverse 16′, das Umlenk­element 25 und das Spannelement 22 zu sehen, weiterhin ein Träger 16˝ für Umlenkelement 25 und Spannelement 22, wel­cher an die Traverse 16′ angeschraubt ist. Die Kettfäden 11′ kommen in Fig. 2 von unten vom nicht dargestellten Kettbaum, werden durch das Umlenkelement 25 und das Spann­element 22 umgelenkt. Das mit dem Torsionsstab 23 schwenk­bare Spannelement 22 sorgt für einen Längenausgleich in den Kettfäden, wenn diese durch die Schäfte 15 in ver­schiedene Positionen gezogen werden.In Fig. 2, 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 a side view of the loom according to FIG. 1 in an enlarged view. The push rod is pushed back and forth in the direction of the double arrow 34 '. Below the double arrow 34 'an adjusting device 37 for adjusting the length of the push rod 34 can be seen. 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. In Fig. 2 is still a cross member 16 ', the deflecting element 25 and the clamping element 22 can be seen, further a support 16' for deflecting element 25 and clamping element 22, which is screwed to the cross member 16 '. The warp threads 11 'come in Fig. 2 from below from the warp beam, not shown, are deflected by the deflecting element 25 and the tensioning element 22. 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 ist eine Ansicht der Anordnung gemäss Fig. 2 in Richtung des Pfeils A. Am Gestell 16 ist die Traverse 16′ angeschraubt, welche mehrere über die Breite der Webma­schine verteilte Träger 16˝ hält. In den Trägern 16˝ ist die um die Schwenkachse 21′ drehbare Antriebswelle 21 ge­lagert. Die Lagerstellen 24 sind an die Antriebswelle 21 angeschraubt. Der Torsionsstab 23 ist am einen Ende mit­tels des Mitnehmers 23˝ mit der Antriebswelle 21 drehfest verbunden, andererseits sitzt er drehfest innerhalb der Nabe 23′, welche in Wälzlagern von der Traverse 16′ getra­gen wird. An die Nabe 23′ ist der Hebel 36 angeschraubt.Fig. 3 is a view of the arrangement of FIG. 2 in the direction of arrow A. On the frame 16, the cross member 16 'is screwed, which holds several across the width of the weaving machine 16 Träger. In the carriers 16 'about the pivot axis 21' rotatable drive shaft 21 is mounted. 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 andererseits, on the other hand it is rotatably seated within the Hub 23 ', which is carried in rolling bearings by the cross member 16'. At the hub 23 ', the lever 36 is screwed.

In Fig. 4 sind gegenüber Fig. 2 nochmals Teile der Spann­vorrichtung 2 vergrössert dargestellt. Ein ortsfestes Um­lenkelement 25 lenkt die Kettfäden 11′ aus einer annähernd vertikalen Lage in Richtung auf das Spannelement 22 um, welches von mehreren über die Webbreite verteilten und durch Lagerstellen 24 gehaltene Rollen abgestützt ist. Aufgrund der mehrfachen Lagerung des Spannelementes 22 auf den Rollen 24′ kann das Spannelement relativ dünn ausge­führt werden. Die Rollen 24′ gewährleisten eine leichte Drehbarkeit des Spannelementes um seine eigene Achse. Ausserdem kann die Einheit Spannelement 22′, Lagerstellen 24′, Antriebswelle 23 rasche Schwenkbewegungen ausführen, da das Massenträgheitsmoment dieser Einheit im Vergleich zu der eingangs erwähnten Einrichtung gemäss der Japani­schen Publikation relativ klein ist. Wenn die Kettfäden 11′ aufgrund der Bewegungen der Webschäfte 15 in Längs­richtung verschoben werden und dadurch Ausgleichsbewegun­gen der Spannvorrichtung 2 bewirken, kann die Einheit Spannelement′, Lagerstelle 24′, Antriebswelle 33 sehr rasch der Längsverschiebung der Kettfäden folgen, wobei aufgrund der kinematischen Verhältnisse sich das Spannele­ment 22 um die eigene Achse auf den Rollen 24′ dreht. Die Rollen 24′ können eine Lauffläche aus Kunststoff, bei­spielsweise Vulkollan, aufweisen, was den Vorteil hat, dass Ablagerungen aus der möglicherweise staubhaltigen Luft des Websaals durch die elastische Deformation der Rollen 24′ im Kontakt mit dem Spannelement 22 von den Kon­taktflächen weggeschoben werden. Im folgenden wird die Funktion der Spannvorrichtung anhand Fig. 5 diskutiert.In 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 several rollers distributed over the weaving width and held by bearing points 24. Due to the multiple storage 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 clamping element about its own axis. In addition, the unit clamping element 22 ', bearings 24', drive shaft 23 can perform swivel 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. If the warp threads 11 'are displaced in the longitudinal direction due to the movements of the heald frames 15 and thereby cause compensating movements of the tensioning device 2, the unit tensioning element', bearing point 24 ', drive shaft 33 can follow the longitudinal displacement of the warp threads very quickly, due to the kinematic conditions Clamping element 22 'rotates about its own axis on the rollers 24'. The rollers 24 'can have a tread made of plastic, for example Vulkollan, which has the advantage that deposits from the possibly dusty air of the weaving room are pushed away by the elastic deformation of the rollers 24' in contact with the tensioning element 22 from the contact surfaces. The function of the tensioning device is discussed below with reference to FIG. 5.

Bei einer Positionsänderung der Kettfäden 11˝ während der sogenannten Fachbildung in der Webmaschine in eine Zwischenposition 11˝a wandert das Spannelement 22 bei­spielsweise von der ausgezogenen Stellung in die gestri­chelte Stellung. Die von den Kettfäden 11′ bzw. 11a er­zeugte resultierende Kraft W bzw. W′ liegt auf der Winkel­halbierenden des durch den Kettfadenverlauf 11′, 11˝ bzw. 11′a bzw. 11˝a gebildeten Linienzuges. Die resultierenden Kräfte W bzw. W′, welche sich aus vektorieller Addition der Kettfadenkräfte K bzw. K′ ergeben, laufen als linien­flüchtige Vektoren im Abstand H2 bzw. H1 an der Schwenk­achse 21′ der Antriebswelle 21 vorbei. Werden die Beträge der Kräfte W bzw. W′ jeweils von den zugehörigen Linienzü­gen der Kettfäden bis zu ihrer Spitze in einer beliebigen Einheit gemessen, ergeben sich folgende Werte:
W = 80; W′ = 69When the position of the warp threads 11˝ changes during the so-called shedding in the weaving machine into one The intermediate element 11a moves the tensioning element 22, for example, from the extended position to 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˝ or 11'a or 11˝a. The resulting forces W and W ', which result from vectorial addition of the warp thread forces K and K', run as line-volatile vectors at a distance H2 and H1 from the pivot axis 21 'of the drive shaft 21. If the magnitudes of the forces W and W ′ are measured in any unit from the associated lines of the warp threads to their apices, the following values result:
W = 80; W ′ = 69

Mit den Abständen H1 und H2 multipliziert haben die Dreh­momente imfolge der Kräfte folgende Werte:
M1 = H1 x W′ = 15 x 69 = 1035
M2 = H2 x W = 6 x 80 = 480Multiplied by the distances H1 and H2, the torques have the following values as a result of the forces:
M1 = H1 x W ′ = 15 x 69 = 1035
M2 = H2 x W = 6 x 80 = 480

Die Werte sind dimensionslos und sollen um die Tendenz bei der Stellungsänderung des Spannelementes 22 angeben. Bei seiner Positionsänderung aus der ausgezogenen Lage in die gestrichelte Lage entsprechend den Stellungen der Kettfä­den 11˝ bzw. 11˝a nimmt also das Drehmoment aufgrund der Kettfadenspannungen bezüglich der Schwenkachse 21′ etwa um das Doppelte zu. Der Schwenkwinkel des Spannelementes 22 ist in Fig. 5 mit α eingezeichnet, dessen Wert 9° be­trägt. Die Dimensionen der Feder bzw. des Torsionsstabes 23, also Länge und Durchmesser der Feder sind so zu wäh­len, dass der Drehmomentanstieg bei der zusätzlichen Ver­drehung um den Winkel α im Torsionsstab ebenfalls vom Wert 480 auf den Wert 1035 ansteigt. Die Vorspannung der Feder 23 ist so zu wählen, dass das Drehmoment durch die Vorspannung der Feder 23 in der ausgezogenen Stellung des Spannelementes 22 ebenfalls den Wert 480 erreicht. Unter diesen Voraussetzungen wäre eine konstante Kettfadenspan­nung bei der Positionsänderung der Kettfäden von der Lage 11˝ in die Lage 11˝a gewährleistet. Ohne Verstellvor­richtung 3 würde der effektive Schwenkwinkel des Spannele­mentes 22 den Winkel α = 9° übersteigen, so dass es nicht gelingen würde, in allen Stellungen des Spannelemen­tes 22 die Veränderung des Drehmomentes aufgrund der geän­derten Lage der Kettfadenkräfte mit der entsprechenden veränderten Verdrehung der Feder 23 zu kompensieren. Hier setzt die Wirkung des Verstellmechanismus 3 ein, in dem das maschinenseitige Ende der Feder 23 in der Nabe 23′ in einer harmonischen Schwingung infolge der Drehung des Ex­zenters 33′ auf der Antriebswelle 33 hin und her ver­schwenkt wird. Diese harmonische Schwingung erfolgt syn­chron mit der Auf- und Abbewegung der Schäfte, welche ebenfalls ein annähernd harmonisches Hin- und Herschwingen des Spannelementes 22 um die Achse 21′ aufgrund der Ver­schiebung der Kettfäden 11′ bewirken. Wenn der Schwenkwin­kel α des Spannelementes 22 annähernd gleich dem Ver­drehwinkel des maschinenseitigen Endes der Feder 23 infol­ge der Bewegung des Verstellmechanismus 3 ist, bleibt auch die Verwindung der Feder 23 annähernd konstant, so dass das Drehmoment in der Spannvorrichtung 2 infolge der Ver­windung der Feder 22 nicht stark variiert. Werden der durch den Verstellmechanismus 3 erzeugte Schwenkwinkel des Hebels 36 die Vorspannung des Torsionsstabes bzw. der Fe­der 23 und die geometrischen Verhältnisse in der Spannvor­richtung 2, also die relative Lage des Spannelementes 22, der Schwenkachse 21′ und des Umlenkelementes 25 zueinander geschickt gewählt, so kann mit einer praktisch konstanten Spannung in den Kettfäden 11′, 11˝ bzw. 11′a, 11˝a auch bei einem grösseren Schwenkwinkel α der Spannvorrichtung gerechnet werden, welcher sich bei grösserer Längsver­schiebung und Positionsänderung der Kettfäden 11˝ bzw. 11˝a infolge grösserer Hübe der Schäfte 15 ergibt nötig ist.The values are dimensionless and should indicate the tendency when the clamping element 22 changes position. When changing its position from the extended position to the dashed position corresponding to the positions of the warp threads 11˝ and 11˝a, the torque due to the warp thread tensions with respect to the pivot axis 21 'increases approximately twice. The pivoting angle of the tensioning element 22 is shown in FIG. 5 with α, 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 α in the torsion bar also increases from the value 480 to the value 1035. The bias of the Spring 23 is to be selected such that the torque also reaches the value 480 due to the pretensioning of spring 23 in the extended position of tensioning element 22. Under these conditions, a constant warp thread tension would be guaranteed when changing the position of the warp threads from position 11˝ to position 11˝a. Without the adjusting device 3, the effective swivel angle of the tensioning element 22 would exceed the angle α = 9 °, so that it would not be possible to change the torque in all positions of the tensioning element 22 due to the changed position of the warp thread forces with the corresponding change in the torsion of the spring 23 compensate. Here is the effect of the adjustment mechanism 3, in which the machine-side end of the spring 23 in the hub 23 'in a harmonic oscillation due to the rotation of the eccentric 33' on the drive shaft 33 is pivoted back and forth. This harmonic oscillation takes place synchronously with the up and down movement of the shafts, which also cause an approximately harmonic back and forth swinging of the tensioning element 22 about the axis 21 'due to the displacement of the warp threads 11'. If the pivot angle α 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. If 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 chosen so so can with a practically constant tension in the warp threads 11 ', 11˝ or 11'a, 11˝a even with a larger pivot angle α 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.

Durch die Drehbarkeit des relativ dünnen Spannelementes 22 auf mehreren Rollen 24′ in den Lagerstellen 24 wird es möglich, die Geometrie der ganzen Spannvorrichtung so zu wählen, dass die resultierende Kraft W der Kettfäden in der ausgezogenen Stellung des Spannelementes 22 in einem nur geringen Abstand an der Schwenkachse 21′ vorbeiläuft. Das dadurch erzeugte Drehmoment ist deshalb vergleichswei­se klein, so dass der Torsionsstab 23, der Hebel 36 und der ganze Verstellmechanismus 3 schwach dimensioniert wer­den können. Wenn das Spannelement 22 nicht bzw. nur er­schwert um die eigene Achse drehbar wäre, würden die Kett­fäden 11′ infolge ihrer Relativbewegung an der Oberfläche des Spannelementes 22 bei einer Lageänderung des Spannele­mentes Reibungskräfte und somit auch ein Reibungsmoment erzeugen, das im Verhältnis zum Drehmoment infolge der Kraft relativ gross wäre. Durch das zusätzliche Reibungs­moment wäre der Ausgleich zwischen dem Moment aufgrund der Kettfadenspannung und dem durch die Vorspannung des Torsi­onsstabes 23 im Gegensinn erzeugten Moment gestört, wo­durch sich auch nachteile Rückwirkungen auf die Spannungen in den Kettfäden ergeben würden.The rotatability of the relatively thin tensioning element 22 on several rollers 24 'in the bearing points 24 makes it possible to choose the geometry of the entire tensioning device in such a way that the resulting force W of the warp threads in the extended position of the tensioning element 22 is only a short distance away the pivot axis 21 'passes. The torque generated thereby is therefore comparatively small, so that the torsion bar 23, the lever 36 and the entire adjustment mechanism 3 can be dimensioned weak. If the tensioning element 22 were not or only difficult to rotate about its own axis, the warp threads 11 'would generate frictional forces due to their relative movement on the surface of the tensioning element 22 in the event of a change in position of the tensioning element 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 pretensioning of the torsion bar 23 in the opposite direction, which would also have adverse effects on the tension in the warp threads.

Die Vorrichtung kann in der Ausführung gemäss der Erfin­dung also unter geometrischen Verhältnissen betrieben wer­den, wenn die resultierende Kraft W die Schwenkachse 23 nur gering verfehlt. Gibt man den Abstand zwischen der Schwenkachse 21′ und dem Umlenkpunkt der Kettfäden 11′ am Spannelement 22 mit L an, so lässt sich ein Verhältnis L / H2 im Bereich zwischen 10 und 15 definieren, bei dem mit der Spannvorrichtung 2 gemäss der Erfindung noch störungsfrei gearbeitet werden kann. Bei den bekannten Spannvorrichtungen nach dem Stand der Technik muss dieses Verhältnis L / H2 wesentlich kleiner sein, damit die Spannvorrichtung genügend weit von der Selbsthemmung, bei der H2 = 0 wird, entfernt arbeitet. Für die vorliegende Erfindung ist es also wesentlich, dass die Vorspannung des Spannelementes 22 mit einer massenarmen Feder 23 bewirkt wird und dass das Spannelement 22 selbst auf mehreren Rol­len gelagert ist und demzufolge auch nur schwache Dimensi­onen aufweist. Nur so ist gewährleistet, dass die Spann­vorrichtung sensibel auf Verschiebungen der Kettfäden 11˝ bzw. 11˝a reagieren kann, wobei auch die durch die Eigen­dynamik der Spannvorrichtung induzierten Spannungsschwan­kungen in den Kettfäden vernachlässigbar bleiben. Auf die­se Weise gelingt es, den Webbetrieb unter bestimmten tex­tiltechnischen Voraussetzungen auf einem wesentlich nied­rigeren Spannungsniveau der Kettfäden verglichen mit Spannvorrichtungen nach dem Stand der Technik durchzufüh­ren, wobei auch die Spannungsschwankungen, also die Diffe­renz zwischen den grössten und den geringsten Spannungs­werten, relativ gering bleibt. So ist mit einer geringeren Beanspruchung in der Webkette zu rechnen, woraus auch we­niger Störungen im Webbetrieb beispielsweise aufgrund von Kettfadenbrüchen resultieren.In the embodiment according to the invention, the device can thus be operated under geometric conditions if the resulting force W only slightly misses the pivot axis 23. If one specifies the distance between the pivot axis 21 'and the deflection point of the warp threads 11' on the tensioning element 22 with L, then a ratio L / H2 can be defined in the range between 10 and 15, in which the tensioning device 2 according to the invention is still used can be worked without interference. In the known tensioning devices according to the prior art, this ratio L / H2 must be significantly smaller so that the tensioning device works sufficiently far from the self-locking, at which H2 = 0. It is therefore essential for the present invention that 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. In this way it is possible to carry out the weaving operation under certain textile conditions at a significantly lower tension level of the warp threads compared to tensioning devices according to the prior art, whereby 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.

Claims (8)

1. Webmaschine mit einer Spannvorrichtung (2) zum Spannen von Kettfäden (11′) einer sogenannten Webkette, beste­hend aus einem federnd abgestützten Spannelement (22) für die Kettfäden bei gleichzeitiger Umlenkung, wobei am Spannelement (22) ein Ende einer Feder (23) ange­lenkt ist, dessen anderes Ende maschinenseitig (23′) gelagert ist, und einem Verstellmechanismus (3) für die Vorspannung der Feder (23) im Takt mit den Arbeitszy­klen der Webmaschine, dadurch gekennzeich­net, dass der Verstellmechanismus (3) am maschinen­seitigen Ende (23′) der Feder (23) in Form eines Tor­sionsstabes angreift, der auf der Schwenkachse (21′) des Spannelementes (22) zum Spannen der Webkette liegt und seinerseits mit einer Antriebswelle (21) der Spann­vorrichtung drehfest verbunden ist, und dass drehfest mit der Antriebswelle (21) über die Webbreite verteilte Lagerstellen (24) für eine rollende Lagerung (24′) des Spannelements (22) vorhanden sind, welches bezüglich seiner Drehachse (22′) rotationssymmetrisch ist.1. Loom with a tensioning device (2) for tensioning warp threads (11 ') of a so-called weaving chain, consisting of a spring-supported tensioning element (22) for the warp threads with simultaneous deflection, one end of a spring (23) on the tensioning element (22) is articulated, the other end of which is mounted on the machine side (23 '), and an adjusting mechanism (3) for the pretensioning of the spring (23) in time with the working cycles of the weaving machine, characterized in that the adjusting mechanism (3) is on the machine side end (23 ') Of the spring (23) in the form of a torsion bar, which lies on the pivot axis (21') of the tensioning element (22) for tensioning the warp and is in turn rotatably connected to a drive shaft (21) of the tensioning device, and that rotatably with Drive shaft (21) over the weaving width bearing points (24) for a rolling bearing (24 ') of the tensioning element (22) are present, which with respect to its axis of rotation (22') red is symmetrical. 2. Webmaschine nach Anspruch 1, dadurch gekennzeichnet, dass der Verstellmechanismus (3) aus einem an der Feder (23) angreifenden Hebel (36), einer mit diesem gelenkig verbundenen Schubstange (34) und einem am anderen Ende der Schubstange (34) sitzenden Exzenter (33′), der auf einer Antriebswelle (33) für den Verstellmechanismus (3) sitzt, gebildet wird.2. Weaving machine according to claim 1, characterized in that the adjusting mechanism (3) from a lever (36) engaging on the spring (23), a push rod (34) articulatedly connected thereto and a seat on the other end of the push rod (34) Eccentric (33 ') which is seated on a drive shaft (33) for the adjusting mechanism (3). 3. Webmaschine nach Anspruch 1 und 2, dadurch gekennzeichnet, dass im Verstellmechanismus (3) in der Verlängerung der Schubstange (34) ein Kraftsensor (35) sitzt.3. Loom according to claim 1 and 2, characterized in that a force sensor (35) is seated in the adjustment mechanism (3) in the extension of the push rod (34). 4. Webmaschine nach den Ansprüchen 1 - 3, dadurch gekennzeichnet, dass der Kraftsensor (35) über eine Steuerleitung (35a) mit einem Steuergerät (14) verbun­den ist, welches über eine Steuerleitung (12a) in Wir­kungsverbindung mit einem Antriebsmotor (12′) für einen Kettbaum (12) steht, auf dem die Webkette (11) aufge­wickelt ist.4. Loom according to claims 1-3, characterized in that the force sensor (35) is connected via a control line (35a) to a control device (14) which is operatively connected to a drive motor (12 ') via a control line (12a) stands for a warp beam (12) on which the warp (11) is wound. 5. Webmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Lagerstellen (24) fest auf der Antriebswelle (21) sitzen und Rollen (24′) tragen, auf welchen sich das Spannelement (22) frei drehbar abgestützt ist..5. Loom according to claim 1, characterized in that the bearing points (24) sit firmly on the drive shaft (21) and carry rollers (24 ') on which the tensioning element (22) is supported in a freely rotatable manner. 6. Webmaschine nach Anspruch 1, dadurch gekennzeichnet, dass zusätzlich zu dem die Kettfäden (11′) umlenkenden Spannelement (22) ein Umlenkelement in Laufrichtung der Kettfäden (11′) vor dem Spannelement (22) angeordnet ist, und dass die Drehachse (22′) des Spannelementes (22), die Schwenkachse (21′) der Antriebswelle (21) und das Zentrum des Umlenkelementes (25′) die Eckpunkte eines annähernd gleichseitigen Dreiecks bilden.6. loom according to claim 1, characterized in that in addition to the warp threads (11 ') deflecting tensioning element (22), a deflection element in the running direction of the warp threads (11') is arranged in front of the tensioning element (22), and that the axis of rotation (22nd ') Of the clamping element (22), the pivot axis (21') of the drive shaft (21) and the center of the deflecting element (25 ') form the corner points of an approximately equilateral triangle. 7. Webmaschine nach Anspruch 6, dadurch gekennzeichnet, dass die Kettfäden (11′) durch das Umlenkelement (25) und das Spannelement (22) annähernd um je denselben Winkel aus einer annähernd vertikalen Richtung in eine horizontale Richtung umlenkt, wobei die Winkelhalbie­rende (W) des durch die Kettfäden zwischen Umlenkele­ment (25) und Spannelement (22) und die vom Spannele­ment (22) ablaufenden Kettfäden (11′) gebildeten Win­kels knapp ausserhalb des Eckpunktes bei der Antriebs­welle (21) des erwähnten Dreiecks vorbeiläuft, wobei die Distanz H2 zwischen der Winkelhalbierenden und der Schwenkachse (21′) nur etwa 1/10 des Abstandes (L) zwischen der Achse (22′) des Spannelementes und der Schwenkachse (21′) beträgt.7. Loom according to claim 6, characterized in that the warp threads (11 ') by the deflecting element (25) and the tensioning element (22) deflects approximately by the same angle from an approximately vertical direction in a horizontal direction, the bisector (W ) of the angle formed by the warp threads between the deflecting element (25) and the tensioning element (22) and the warp threads (11 ') running off the tensioning element (22) runs just outside the corner point at the drive shaft (21) of the triangle mentioned, the distance H2 between the bisector and the swivel axis (21 ′) only about 1/10 of the distance (L) between the axis (22 ') of the clamping element and the pivot axis (21'). 8. Webmaschine nach Anspruch 5, dadurch gekennzeichnet, dass die Laufflächen der Rollen (24′) aus Kunststoff, beispielsweise Vulkollan, bestehen.8. loom according to claim 5, characterized in that the running surfaces of the rollers (24 ') made of plastic, for example Vulkollan.
EP90810265A 1989-05-02 1990-04-03 Loom with easy-going warp tension device Expired - Lifetime EP0396501B1 (en)

Applications Claiming Priority (2)

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

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EP0396501A1 true EP0396501A1 (en) 1990-11-07
EP0396501B1 EP0396501B1 (en) 1993-08-18

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EP90810265A Expired - Lifetime EP0396501B1 (en) 1989-05-02 1990-04-03 Loom with easy-going warp tension device

Country Status (7)

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

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DE4427126A1 (en) * 1994-07-30 1996-02-01 Dornier Gmbh Lindauer Clamp element for loom warp
DE4427129A1 (en) * 1994-07-30 1996-02-01 Dornier Gmbh Lindauer Tensioning unit for the weaving chain of a weaving machine
DE19538121C1 (en) * 1995-10-13 1997-02-27 Dornier Gmbh Lindauer Warp tensioner useful for loom esp. for tension sensitive yarns
WO1998054386A1 (en) * 1997-05-28 1998-12-03 Picanol N.V. Device for tensioning warp threads in a loom
EP0937796A1 (en) * 1998-02-18 1999-08-25 Sulzer Rüti Ag Warp threads tensioning device for a loom and loom with such a device
EP1031652A2 (en) * 1998-12-17 2000-08-30 NUOVA VAMATEX S.p.A. Warp tension device with a gradual-action suspension for weaving looms
US6135162A (en) * 1997-09-13 2000-10-24 Lindauer Dornier Gesellschaft Mbh Method and device for regulating a back rest and/or a drop wire position of a weaving machine
WO2015049216A1 (en) * 2013-10-01 2015-04-09 Lindauer Dornier Gesellschaft Mit Beschränkter Haftung Method and device for applying forces and motions to warp threads of weaving machine

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US6056112A (en) * 1998-05-20 2000-05-02 Argonics, Inc. Apparatus for preloading a scraper blade in a conveyor cleaning system
ITMI20030182A1 (en) * 2003-02-04 2004-08-05 Promatech Spa ARRANGEMENT OF YARNS PERFECTED FOR A TEXTILE FRAME
DE102005028127A1 (en) * 2005-06-10 2006-12-14 Picanol N.V. terry
DE102006020586B4 (en) * 2006-05-02 2008-08-28 Oerlikon Textile Gmbh & Co. Kg Method and device for producing cotton wool from textile fiber wadding
JP4973142B2 (en) * 2006-11-17 2012-07-11 株式会社豊田自動織機 Warp tension controller for pile weaving loom
JP2009293151A (en) * 2008-06-05 2009-12-17 Tsudakoma Corp Tension roll-supporting mechanism of loom

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EP0109472B1 (en) * 1982-10-26 1986-09-10 GebràœDer Sulzer Aktiengesellschaft Warp tensioning device on a weaving loom
EP0136389A1 (en) * 1983-10-03 1985-04-10 Maschinenfabrik Sulzer-Rüti Ag Warp let-off control mechanism for looms
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4427126A1 (en) * 1994-07-30 1996-02-01 Dornier Gmbh Lindauer Clamp element for loom warp
DE4427129A1 (en) * 1994-07-30 1996-02-01 Dornier Gmbh Lindauer Tensioning unit for the weaving chain of a weaving machine
US5558132A (en) * 1994-07-30 1996-09-24 Lindauer Dornier Gesellschaft Mbh Adjustable warp tension roll support in a weaving loom
DE4427129C2 (en) * 1994-07-30 1998-07-30 Dornier Gmbh Lindauer Tensioning unit for the weaving chain of a weaving machine
DE4427126C2 (en) * 1994-07-30 1998-09-17 Dornier Gmbh Lindauer Tensioning unit for the warp in a weaving machine
DE19538121C1 (en) * 1995-10-13 1997-02-27 Dornier Gmbh Lindauer Warp tensioner useful for loom esp. for tension sensitive yarns
EP0771896A1 (en) * 1995-10-13 1997-05-07 Lindauer Dornier Gesellschaft M.B.H Not controlled tensioning device for the warp of a loom
US5755268A (en) * 1995-10-13 1998-05-26 Lindauer Dornier Gesellschaft Mbh Loom warp tensioning device with torque moment compensation
WO1998054386A1 (en) * 1997-05-28 1998-12-03 Picanol N.V. Device for tensioning warp threads in a loom
BE1011184A3 (en) * 1997-05-28 1999-06-01 Picanol Nv Device for determining the chain ​​tension.
US6135162A (en) * 1997-09-13 2000-10-24 Lindauer Dornier Gesellschaft Mbh Method and device for regulating a back rest and/or a drop wire position of a weaving machine
EP0937796A1 (en) * 1998-02-18 1999-08-25 Sulzer Rüti Ag Warp threads tensioning device for a loom and loom with such a device
US6098670A (en) * 1998-02-18 2000-08-08 Sulzer Ruti Ag Apparatus for tensioning warp threads for a weaving machine and a weaving machine with an apparatus of this kind
EP1031652A2 (en) * 1998-12-17 2000-08-30 NUOVA VAMATEX S.p.A. Warp tension device with a gradual-action suspension for weaving looms
EP1031652A3 (en) * 1998-12-17 2000-09-06 NUOVA VAMATEX S.p.A. Warp tension device with a gradual-action suspension for weaving looms
WO2015049216A1 (en) * 2013-10-01 2015-04-09 Lindauer Dornier Gesellschaft Mit Beschränkter Haftung Method and device for applying forces and motions to warp threads of weaving machine

Also Published As

Publication number Publication date
CH681156A5 (en) 1993-01-29
CN1046948A (en) 1990-11-14
CN1023575C (en) 1994-01-19
JP2706551B2 (en) 1998-01-28
DE59002365D1 (en) 1993-09-23
US5090453A (en) 1992-02-25
EP0396501B1 (en) 1993-08-18
JPH02293447A (en) 1990-12-04
RU2001978C1 (en) 1993-10-30

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