EP1070163B1 - Drive device for the parting shafts of circular looms - Google Patents

Drive device for the parting shafts of circular looms Download PDF

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Publication number
EP1070163B1
EP1070163B1 EP99936242A EP99936242A EP1070163B1 EP 1070163 B1 EP1070163 B1 EP 1070163B1 EP 99936242 A EP99936242 A EP 99936242A EP 99936242 A EP99936242 A EP 99936242A EP 1070163 B1 EP1070163 B1 EP 1070163B1
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EP
European Patent Office
Prior art keywords
parting
shafts
driving lever
drive device
coupling
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Expired - Lifetime
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EP99936242A
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German (de)
French (fr)
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EP1070163A2 (en
Inventor
Jörg STARK
Klaus Hering
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Karl Mayer Textilmaschinenfabrik GmbH
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Karl Mayer Textilmaschinenfabrik GmbH
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D37/00—Circular looms

Definitions

  • the invention relates to a drive device for the partial shafts of circular looms, on which the partial shafts are driven in opposite directions in pairs and are guided parallel to each other, on which the partial shafts of each pair are lower Belt sections are assigned, at least one of which is by means of a guide roller is guided, and on which the band sections of a pair of partial shafts assigned a drive lever swinging around a frame-fixed bearing is connected to these belt sections via at least one coupling and the at least one sensing roller for interacting with a globiod curve possesses, which is rotatably driven about the vertical axis of the circular loom is.
  • a drive device is u. a. by U.S. Patent 4,579,149 known.
  • the partial shafts interacting in pairs are on their upper Ends connected with a band. This tape is over an upper one Deflection pulley guided. At both ends there are lower ones at the lower end Band sections attached, the outer one at a distance below the shed is guided around a lower guide roller.
  • the two lower band sections are by means of a partially flexible coupling attached to a radially outward arm of a drive lever.
  • the Drive lever has between the plane of movement of the partial shafts and the axis the machine its fixed bearing.
  • On a second, inward facing The arm of the drive lever has a feeler roller rotatably mounted about a radial axis. This tracer roller works with a globoid curve around the vertical axis of the circular knitting machine is guided and driven.
  • Such a drive device can be produced quite inexpensively.
  • the large forces and the unsatisfactory transmission angles on the globoid curve are problematic.
  • the large translations between the globoid curve and the partial shafts and the large increases in the curves on the globoid curve lead to high wear at the necessary speeds. It was usually helped to keep the subject height within limits. However, this also forced the diameter of the coils on the contactors to be limited.
  • An additional spreading of the compartments during the passage of the shooter leads to a higher power requirement and to a strong heating of the warp threads. Excessive heating of the warp threads is highly undesirable.
  • the molecular structures of the threads change at certain high temperatures. These threads then lose their necessary high strength.
  • Such a drive device is therefore not suitable for further increasing the productivity of the circular loom.
  • US Pat. No. 4,821,778 has disclosed a somewhat modified drive device for a pair of partial shafts on circular looms.
  • One of the lower band sections is connected in the region of an elongated run below the shed with a lifting rod which extends in the plane of movement of a partial shaft.
  • This lifting rod has a carriage at its lower end.
  • the slide carries a feeler roller that engages directly in a cylindrical groove curve. With such a design, the groove curve is less stressed.
  • the much greater overall height is disadvantageous.
  • the operation of the machine is significantly more difficult due to the high position of the shed.
  • the cost of guiding the carriage with the lifting rod is considerable because of the large number of similar drive devices in a circular loom. This means that such a device is also unsuitable for solving the problems of the present day - higher productivity with good operability and with a simple and low-maintenance machine construction.
  • the Austrian patent 371 846 has set itself the goal of reducing the extreme height of the machine. It is proposed here that the entire bands - including the strand sections - be flexibly designed for the up and down movements of the strand eyelets for the purpose of forming a shed. With such an arrangement, the overall height of the machine can be reduced, but the quality of the shed formation and the reliability of the guiding of all the warp threads is adversely affected. Such an implementation has not prevailed.
  • the cylindrical drive curve for the flexible belts is arranged directly below the compartment level, within the area of the two lower belt guides. The then shorter carriage for guiding the feeler rollers reduces the costs and the size of the masses to be moved.
  • the partial shafts are guided and driven in a plane inclined upward and outward at approximately 45 °.
  • the opposing partial shafts are connected to an upper band section which is tensioned in the usual way around an upper deflection roller.
  • the lower belt sections are guided around a drive wheel. They are permanently connected to the circumference of the drive wheel by a coupling.
  • the drive wheel in turn is driven by a second belt transmission.
  • the drive wheel has a second drive pulley with a smaller diameter.
  • a carriage is guided in an outwardly displaced, vertically guided section of the second belt, which is moved up and down by a cylindrical cam drum.
  • the height of the drum curve is significantly reduced by the gear ratio provided.
  • the compartment used in this context inclined 45 ° outwards and upwards, improves the usability of the machine.
  • the conditions for the running of the warp threads and for the running and the size of the shooters in the compartment are made much more favorable.
  • the drum curve can have a relatively large diameter.
  • the increases in the curves on the drum curve are flat and lead to good transmission ratios.
  • a disadvantage of this design is the somewhat higher outlay for the second belt drive and for guiding the slide with the feeler rollers and the coupling for each pair of shafts.
  • the object of the present invention is to provide a drive device to create the type mentioned, in which the forces on the curve at low Level can be kept at which the cost of the drive elements are low and which allows a low operating height.
  • This drive device should allow a large compartment opening without the warp threads through Spreading elements are additionally loaded.
  • the object is achieved in a simple manner by the features of claim 1.
  • the arrangement of the drive lever predominantly outside the plane of movement of the inner partial shafts of each pair enables an optimal assignment of the coupling to the belt sections on the one hand and the feeler roller of the drive lever to the drive curve in the center of the machine on the other hand.
  • the large diameter of the globoid curve allows flat curve increases without the movement necessarily having to be translated. In the event that a translation is desired, no additional gear links are required.
  • the size of the compartment opening can be determined in the usual framework solely by the appropriate choice of the dimensions of the elements.
  • the overall height of the machine and thus the operating height can be kept at a low level.
  • the drive device has few and simple parts.
  • the Globiod curve can be produced on modern machine tools with reasonable effort.
  • the lifespan of most components is long because extreme loads are basically avoided.
  • the lower load also offers opportunities for a further increase in the performance of the working speed of the machine.
  • the embodiment according to claim 2 enables relatively flat increases in the globoid curve. It is particularly suitable for an embodiment in which the mass of the drive lever is relatively high.
  • the design according to claim 3 is recommended if the masses in the area of the drive lever are relatively small. 4 allows clear and unambiguous movement conditions of all moving elements.
  • the drive arrangement according to claim 5 allows the moving masses of the drive lever to be minimized.
  • the features of claim 6 lead to a high stability of the drive unit with good operability of all drive elements.
  • the effective radius of the globoid curve can be increased. This allows the slopes of the globoid curve to be made flat. The elements designed in this way are easily accessible for operation and maintenance.
  • the embodiment according to claim 7 enables the device to be easily adapted to the conditions of a sloping compartment.
  • the independent claim 8 defines a drive device specially designed with an inclined shed which also fulfills the task set out above.
  • Claim 9 describes an advantageous embodiment of this drive device according to Claim 8. The advantages consist in the use of a globoid curve with a large mean diameter.
  • the partial shaft drive shown in Fig. 1 is preferably provided for a circular loom, the shed of which is inclined upwards in the direction of the inner fabric stop edge.
  • the warp thread groups 11, 12 are alternately displaced into the two warp thread levels by means of the partial shafts known per se.
  • the shooter 4 is guided through the compartment thus opened in a manner known per se.
  • the warp thread sheet 11 is guided through the partial shaft 22, while the warp thread sheet 12 is guided through the eyelets of the strands of the partial shaft 21.
  • the partial shafts 21 and 22 are guided at an angle of approximately 45 ° along their movement planes 210 and 220, respectively.
  • the size of the specialist stroke should enable the guiding of a contactor 4 with a relatively large coil.
  • the partial shafts 21, 22 are connected to one another at their upper end by the upper band section 23.
  • This band section 23 wraps around the deflection roller 3 by 180 °.
  • the lower ends of the partial shafts 21, 22 are held and tensioned by the lower band sections 24, 25.
  • the lower band section 24 is guided via the guide roller 31 fixed to the frame onto the guide section 56 of the drive lever 5 up to the coupling 52 of the drive lever 5.
  • the belt section 25 partially wraps around the guide roller 32 and is guided from there onto the guide section 57 of the drive lever 5.
  • This lower band section 25 is held by the coupling 53 on the drive lever 5.
  • the drive lever 5 has its bearing 51 between the end sections of the two lower band sections 24, 25. This bearing 51 is fixed to the frame.
  • the drive lever 5 is designed as a segment in its upper region.
  • the curved section of the segment forms the guide sections 56, 57 for the two belt sections 24, 25 and is limited at the bottom by the couplings 52 and 53.
  • the traction roller bearing 54 is arranged between these couplings 52, 53, preferably detachably mounted.
  • This tracer roller bearing 54 carries two tracer rollers 55, which formally enclose the bead of the globoid curve 6 between them.
  • This globoid curve 6 extends below the circularly arranged shedding zone and is guided by the globoid cam carrier 60 around the vertical longitudinal axis 98 of the circular weaving machine and driven in rotation synchronously with the shooter drive by a corresponding drive device.
  • This arrangement has the advantage that the drive movement of the partial shafts 21, 22 can be realized in a compact height.
  • the globoid curve 6 can be arranged on a relatively large, medium radius - based on the vertical machine axis. All guide elements for the partial shafts 21, 22 are subject to stable guidance in each phase of their movement.
  • All drive elements are easily accessible from the operator side.
  • the size of the moving masses can be approximated to an absolutely necessary minimum with the appropriate design and choice of material.
  • the size of the specialist stroke can be designed by simple structural adjustment of the elements so that an optimal functioning of the machine is possible.
  • the embodiment according to FIG. 2 differs from the device according to FIG. 1 initially in that the shed 1 ′ to be formed here is aligned in the horizontal plane.
  • the warp thread groups 11 'and 12' are moved here by the partial shafts 21 ', 22'.
  • the planes of motion 210 ', 220' of the partial shafts 21 ', 22' are oriented essentially vertically.
  • the partial shafts 21 ', 22' are connected to one another by the upper band section 23 '.
  • This band section 23 ' is guided over the deflection roller 3'.
  • the lower band section 24 ' is again guided in the plane of movement 210' by the guide roller 33 and via the guide rollers 36 and 37 outside the drive lever 7 to the guide roller 38, which roughly affects the guide plane 220 '.
  • this band section 24 ' is then directed upwards again and is held by the coupling 72 pivotably mounted on the drive lever 7. From this coupling 72, the lower band section 25 'leads past the guide roller 34 to the lower end of the partial shaft 22'.
  • the drive lever 7 is guided to swing about the frame-fixed bearing 71.
  • This bearing 71 is preferably located between the guide areas of the lower band sections 24 'and 25'. At this point it should be pointed out that the bearing 71 can also be arranged outside the lower band section 24 '. In this case, sufficient space must be available for parts of the drive lever 7 to be able to grip the lower band section 24 'laterally at a free distance.
  • the globoid curve 8 is arranged very close to the plane of movement 220 'of the inner partial shaft 22'.
  • the radius of this globoid curve 8 is very large in relation to the vertical axis of the machine. In this way, relatively flat increases in the drive curve 8 are possible.
  • the globoid curve 8 is designed here as a groove curve.
  • a single feeler roller 75 of the drive lever 7 preferably engages in this groove curve 8.
  • the globoid curve 8 is attached to the globoid cam carrier 80 here. It is guided by the latter about the vertical machine axis 98 and driven in a manner known per se.
  • the advantage of this embodiment is that the moving masses of the drive lever 7 can be significantly reduced.
  • the bearings 71 are easily accessible for maintenance purposes. With such an embodiment, it is also conceivable that the lower band section 24 'can be guided in the movement plane 210' through the movement range of the drive lever 7. In this embodiment, however, the drive lever 7 should be designed such that it has a corresponding recess in the guide region of this band section 24 'and can grip around this band section laterally. You can also significantly reduce the number of guide or deflection rollers. In this case, the guide rollers 33 and 34 would only have securing functions. The guide rollers 36 and 37 are omitted and the guide roller 38 fulfills the function of a lower deflection roller. The latter should therefore be given an appropriate diameter.
  • FIG. 3 shows a drive device for the partial shafts 21, 22 of a circular weaving machine with an inward and upwardly inclined shed.
  • the lower belt sections 24 "and 25" are guided by the guide rollers 31 ' and 32 'deflected vertically downward, guided around the roller 38' and in the area of attack the clutch 92 connected to each other.
  • the feeler roller 95 has its bearing on an upward arm of this drive lever 9. It works with the globoid curve 96, which has its bearing on the curve carrier 97.
  • the globoid cam carrier 97 rotates about the vertical machine axis 98.
  • This version is particularly suitable for circular weaving machines in which, starting from drive means for the partial shafts with a horizontal shed, the inclination of the plane of movement 220, 210 of the partial shafts upwards and outwards would like to increase the length of the shed in front of the stop edge. In this way, space is created for larger coils in the contactors 4.

Abstract

The invention relates to a drive device for the parting shafts of circular looms on which the parting shafts are driven in pairs in opposite directions. Lower band sections are assigned to the parting shafts of each pair. A drive lever which oscillates around a bearing fixed to the frame is connected to said band sections via a coupling. The drive lever comprises at least one jockey roller for interacting with a globoid cam which can be rotationally driven around the vertical axis of the circular loom. In order to reduce the number and the mass of the transmission elements having flat curve inclinations on the globoid cam, the drive device is configured such that the bearing (51; 71) of the drive lever (5; 7), said bearing being fixed to the frame, is arranged outside of the movement plane (220) of each inner parting shaft (22, 22'), and such that the jockey roller (55; 75) and each one of the couplings (52, 53; 72) are arranged on the same side of the bearing (51; 71).

Description

Die Erfindung betrifft eine Antriebsvorrichtung für die Teilschäfte von Rundwebmaschinen, an denen die Teilschäfte paarweise gegenläufig angetrieben und zueinander parallel geführt sind, an denen den Teilschäften jedes Paares untere Bandabschnitte zugeordnet sind, von denen mindestens einer mittels Führungsrolle geführt ist, und an denen den Bandabschnitten eines Paares von Teilschäften ein um ein gestellfestes Lager schwingender Antriebshebel zugeordnet ist, der über mindestens eine Kupplung mit diesen Bandabschnitten verbunden ist und der mindestens eine Tastrolle zum Zusammenwirken mit einer Globiodkurve besitzt, die um die vertikale Achse der Rundwebmaschine drehbar angetrieben ist.The invention relates to a drive device for the partial shafts of circular looms, on which the partial shafts are driven in opposite directions in pairs and are guided parallel to each other, on which the partial shafts of each pair are lower Belt sections are assigned, at least one of which is by means of a guide roller is guided, and on which the band sections of a pair of partial shafts assigned a drive lever swinging around a frame-fixed bearing is connected to these belt sections via at least one coupling and the at least one sensing roller for interacting with a globiod curve possesses, which is rotatably driven about the vertical axis of the circular loom is.

Eine Antriebsvorrichtung gemäß Oberbegriff der Ansprüche 1 und 8 ist u. a. durch die US-Patentschrift 4,579,149 bekannt. Die paarweise zusammenwirkenden Teilschäfte sind an ihren oberen Enden über ein Band miteinander verbunden. Dieses Band wird über eine obere Umlenkrolle geführt. An beiden Teilschäften sind jeweils am unteren Ende untere Bandabschnitte befestigt, von denen der jeweils äußere im Abstand unterhalb des Webfaches um eine untere Führungsrolle geführt wird. A drive device according to the preamble of claims 1 and 8 is u. a. by U.S. Patent 4,579,149 known. The partial shafts interacting in pairs are on their upper Ends connected with a band. This tape is over an upper one Deflection pulley guided. At both ends there are lower ones at the lower end Band sections attached, the outer one at a distance below the shed is guided around a lower guide roller.

Die beiden unteren Bandabschnitte sind mittels einer teilweise flexiblen Kupplung an einem radial nach außen gerichteten Arm eines Antriebshebels befestigt. Der Antriebshebel hat zwischen der Bewegungsebene der Teilschäfte und der Achse der Maschine sein gestellfestes Lager. An einem zweiten, nach innen gerichteten Arm des Antriebshebels ist eine Tastrolle um eine radiale Achse drehbar gelagert. Diese Tastrolle arbeitet mit einer Globoidkurve zusammen, die um die vertikale Achse der Rundwirkmaschine geführt und angetrieben wird.The two lower band sections are by means of a partially flexible coupling attached to a radially outward arm of a drive lever. The Drive lever has between the plane of movement of the partial shafts and the axis the machine its fixed bearing. On a second, inward facing The arm of the drive lever has a feeler roller rotatably mounted about a radial axis. This tracer roller works with a globoid curve around the vertical axis of the circular knitting machine is guided and driven.

Eine solche Antriebsvorrichtung ist recht kostengünstig herstellbar. Problematisch sind jedoch die großen Kräfte und die unbefriedigenden Übertragungswinkel an der Globoidkurve. Die großen Übersetzungen zwischen der Globoidkurve und den Teilschäften und die großen Anstiege der Kurven an der Globoidkurve führen bei den notwendigen Geschwindigkeiten zu einem hohen Verschleiß.
Man half sich meist damit, die Fachhöhe in Grenzen zu halten. Dadurch war man jedoch auch gezwungen, die Durchmesser der Spulen an den Schützen zu begrenzen.
Ein zusätzliches Spreizen der Fächer beim Schützendurchgang führt zu einem höheren Leistungsbedarf und zu einem starken Erwärmen der Kettfäden. Das übermäßige Erwärmen der Kettfäden ist im hohen Maße unerwünscht. Bei bestimmten hohen Temperaturen verändern sich die Molekularstrukturen der Fäden. Diese Fäden verlieren dann ihre notwendige, hohe Festigkeit.
Eine solche Antriebsvorrichtung ist damit nicht geeignet, die Produktivität der Rundwebmaschine weiter zu erhöhen.Such a drive device can be produced quite inexpensively. However, the large forces and the unsatisfactory transmission angles on the globoid curve are problematic. The large translations between the globoid curve and the partial shafts and the large increases in the curves on the globoid curve lead to high wear at the necessary speeds.
It was usually helped to keep the subject height within limits. However, this also forced the diameter of the coils on the contactors to be limited.
An additional spreading of the compartments during the passage of the shooter leads to a higher power requirement and to a strong heating of the warp threads. Excessive heating of the warp threads is highly undesirable. The molecular structures of the threads change at certain high temperatures. These threads then lose their necessary high strength.
Such a drive device is therefore not suitable for further increasing the productivity of the circular loom.

Durch das US-Patent 4,821,778 ist eine etwas abgewandelte Antriebsvorrichtung für ein Teilschaftpaar an Rundwebmaschinen bekannt geworden.
Einer der unteren Bandabschnitte ist im Bereich eines gestreckten Trums unterhalb des Webfaches mit einer Hubstange verbunden, die sich in der Bewegungsebene eines Teilschaftes erstreckt.
Diese Hubstange hat an ihrem unteren Ende einen Schlitten. Der Schlitten trägt eine Tastrolle, die direkt in eine zylindrische Nutkurve eingreift. Bei einer solchen Ausführung wird die Nutkurve weniger belastet. Nachteilig ist jedoch die wesentlich größere Bauhöhe. Die Bedienung der Maschine ist wegen der hohen Lage des Webfaches deutlich erschwert.
Der Kostenaufwand für die Führung des Schlittens mit der Hubstange ist wegen der großen Zahl der gleichartigen Antriebsvorrichtungen in einer Rundwebmaschine erheblich.
Damit ist auch eine solche Vorrichtung nicht geeignet, die Probleme der Gegenwart - eine höhere Produktivität bei guter Bedienbarkeit und mit einem einfachen und wartungsarmen Maschinenaufbau - zu lösen.US Pat. No. 4,821,778 has disclosed a somewhat modified drive device for a pair of partial shafts on circular looms.
One of the lower band sections is connected in the region of an elongated run below the shed with a lifting rod which extends in the plane of movement of a partial shaft.
This lifting rod has a carriage at its lower end. The slide carries a feeler roller that engages directly in a cylindrical groove curve. With such a design, the groove curve is less stressed. However, the much greater overall height is disadvantageous. The operation of the machine is significantly more difficult due to the high position of the shed.
The cost of guiding the carriage with the lifting rod is considerable because of the large number of similar drive devices in a circular loom.
This means that such a device is also unsuitable for solving the problems of the present day - higher productivity with good operability and with a simple and low-maintenance machine construction.

Das Österreichische Patent 371 846 hat sich zum Ziel gestellt, die extreme Höhe der Maschine zu reduzieren. Hier wird vorgeschlagen, die gesamten Bänder-einschließlich der Litzenabschnitte - für die Auf- und Abbewegungen der Litzenösen zum Zweck der Fachbildung flexibel auszuführen. Mit einer derartigen Anordnung kann man zwar die Bauhöhe der Maschine reduzieren, aber die Qualität der Fachbildung und die Zuverlässigkeit der Führung aller Kettfäden wird negativ beeinflußt. Eine solche Ausführung hat sich nicht durchgesetzt.
In der genannten Patentschrift wird die zylindrische Antriebskurve für die flexiblen Bänder unmittelbar unterhalb der Fachebene, innerhalb des Bereiches der beiden unteren Bandführungen angeordnet. Mit dem dann kürzer werdenden Schlitten für die Führung der Tastrollen reduziert man die Kosten und die Größe der zu bewegenden Massen.
Bei einer weiteren, in der Praxis realisierten Antriebsanordnung für die Teilschäfte werden die Teilschäfte in einer auf etwa 45° nach oben und außen geneigten Ebene geführt und angetrieben. Die gegenläufig arbeitenden Teilschäfte sind mit einem oberen Bandabschnitt verbunden, der in üblicher Weise um eine obere Umlenkrolle gespannt ist. Die unteren Bandabschnitte werden um ein Antriebsrad geführt. Sie sind an einer Stelle mit dem Umfang des Antriebsrades durch eine Kupplung fest verbunden. The Austrian patent 371 846 has set itself the goal of reducing the extreme height of the machine. It is proposed here that the entire bands - including the strand sections - be flexibly designed for the up and down movements of the strand eyelets for the purpose of forming a shed. With such an arrangement, the overall height of the machine can be reduced, but the quality of the shed formation and the reliability of the guiding of all the warp threads is adversely affected. Such an implementation has not prevailed.
In the cited patent, the cylindrical drive curve for the flexible belts is arranged directly below the compartment level, within the area of the two lower belt guides. The then shorter carriage for guiding the feeler rollers reduces the costs and the size of the masses to be moved.
In a further drive arrangement for the partial shafts, which is implemented in practice, the partial shafts are guided and driven in a plane inclined upward and outward at approximately 45 °. The opposing partial shafts are connected to an upper band section which is tensioned in the usual way around an upper deflection roller. The lower belt sections are guided around a drive wheel. They are permanently connected to the circumference of the drive wheel by a coupling.

Das Antriebsrad seinerseits wird über ein zweites Riemengetriebe angetrieben. Dazu hat das Antriebsrad eine zweite Antriebsscheibe mit kleinerem Durchmesser. In einem nach außen verlagerten, senkrecht geführten Abschnitt des zweiten Riemens ist ein Schlitten geführt, der durch eine zylindrische Kurventrommel auf und ab bewegt wird.
Bei dieser Antriebsanordnung kann man die Bauhöhe der Maschine ebenfalls reduzieren. Die Höhe der Trommelkurve wird durch das vorgesehene Übersetzungsverhältnis deutlich reduziert.
Das in diesem Zusammenhang verwendete, um 45° nach außen und oben geneigte Fach verbessert die Bedienbarkeit der Maschine. Zum anderen werden die Bedingungen für den Lauf der Kettfäden und für den Lauf und die Größe der Schützen im Fach wesentlich günstiger gestaltet. Vorteilhaft ist auch, daß die Trommelkurve einen relativ großen Durchmesser aufweisen kann. Die Anstiege der Kurven an der Trommelkurve sind flach und führen zu guten Übertragungsverhältnissen.
Nachteilig ist bei dieser Ausführung jedoch der etwas höhere Aufwand für den zweiten Riementrieb und für die Führung des Schlittens mit den Tastrollen und der Kupplung für jedes Teilschaftpaar.The drive wheel in turn is driven by a second belt transmission. For this purpose, the drive wheel has a second drive pulley with a smaller diameter. A carriage is guided in an outwardly displaced, vertically guided section of the second belt, which is moved up and down by a cylindrical cam drum.
With this drive arrangement, the overall height of the machine can also be reduced. The height of the drum curve is significantly reduced by the gear ratio provided.
The compartment used in this context, inclined 45 ° outwards and upwards, improves the usability of the machine. On the other hand, the conditions for the running of the warp threads and for the running and the size of the shooters in the compartment are made much more favorable. It is also advantageous that the drum curve can have a relatively large diameter. The increases in the curves on the drum curve are flat and lead to good transmission ratios.
A disadvantage of this design, however, is the somewhat higher outlay for the second belt drive and for guiding the slide with the feeler rollers and the coupling for each pair of shafts.

Die Aufgabe der vorliegenden Erfindung ist es, eine Antriebsvorrichtung der eingangs genannten Art zu schaffen, bei der die Kräfte an der Kurve auf niedrigem Niveau gehalten werden können, bei der die Kosten für die Antriebselemente niedrig sind und die eine niedrige Bedienhöhe erlaubt. Diese Antriebsvorrichtung soll eine große Fachöffnung ermöglichen, ohne daß die Kettfäden durch Spreizelemente zusätzlich belastet werden.The object of the present invention is to provide a drive device to create the type mentioned, in which the forces on the curve at low Level can be kept at which the cost of the drive elements are low and which allows a low operating height. This drive device should allow a large compartment opening without the warp threads through Spreading elements are additionally loaded.

Erfindungsgemäß wird die Aufgabe durch die Merkmale des Anspruch 1 auf einfache Art gelöst. Die Anordnung des Antriebshebels überwiegend außerhalb der Bewegungsebene der innen befindlichen Teilschäfte jedes Paares ermöglicht eine optimale Zuordnung der Kupplung zu den Bandabschnitten einerseits und der Tastrolle des Antriebshebels zu der Antriebskurve im Zentrum der Maschine andererseits. Der große Durchmesser der Globoidkurve erlaubt flache Kurvenanstiege, ohne daß zwingend die Bewegung übersetzt werden muß.
Für den Fall, daß man eine Übersetzung wünscht, sind keine zusätzlichen Getriebeglieder erforderlich. Die Größe der Fachöffnung kann im üblichen Rahmen allein durch die entsprechende Wahl der Abmessungen der Elemente bestimmt werden.
Die Bauhöhe der Maschine und damit die Bedienhöhe kann auf einem niedrigen Niveau gehalten werden. Die Antriebsvorrichtung hat wenige und einfache Teile. Die Globiodkurve ist auf moderenen Werkzeugmaschinen mit vertretbarem Aufwand herstellbar. Die Lebensdauer der meisten Bauelemente ist hoch, weil extreme Belastungen dem Grunde nach vermieden werden.
Die geringere Belastung bietet auch Möglichkeiten für eine weitere Leistungssteigerung der Arbeitsdrehzahl der Maschine.According to the invention, the object is achieved in a simple manner by the features of claim 1. The arrangement of the drive lever predominantly outside the plane of movement of the inner partial shafts of each pair enables an optimal assignment of the coupling to the belt sections on the one hand and the feeler roller of the drive lever to the drive curve in the center of the machine on the other hand. The large diameter of the globoid curve allows flat curve increases without the movement necessarily having to be translated.
In the event that a translation is desired, no additional gear links are required. The size of the compartment opening can be determined in the usual framework solely by the appropriate choice of the dimensions of the elements.
The overall height of the machine and thus the operating height can be kept at a low level. The drive device has few and simple parts. The Globiod curve can be produced on modern machine tools with reasonable effort. The lifespan of most components is long because extreme loads are basically avoided.
The lower load also offers opportunities for a further increase in the performance of the working speed of the machine.

Die Ausführung nach Anspruch 2 ermöglicht relativ flache Anstiege in der Globoidkurve. Sie eignet sich insbesondere für eine Ausführung, bei der die Masse des Antriebshebels relativ hoch ist.
Die Gestaltung nach Anspruch 3 empfiehlt sich, wenn die Massen im Bereich des Antriebshebels relativ klein sind.
Die Vorrichtung nach Fig. 4 erlaubt klare und eindeutige Bewegungsverhältnisse aller bewegten Elemente.
Die Antriebsanordnung nach Anspruch 5 gestattet es, die bewegten Massen des Antriebshebels zu minimieren.
Die Merkmale des Anspruches 6 führen zu einer hohen Stabilität der Antriebseinheit bei guter Bedienbarkeit aller Antriebselemente. Die Vergrößerung des wirksamen Radius der Globoidkurve wird möglich. Damit können die Anstiege der Globoidkurve flach gestaltet werden. Die so gestalteten Elemente sind für die Bedienung und Wartung leicht zugänglich. The embodiment according to claim 2 enables relatively flat increases in the globoid curve. It is particularly suitable for an embodiment in which the mass of the drive lever is relatively high.
The design according to claim 3 is recommended if the masses in the area of the drive lever are relatively small.
4 allows clear and unambiguous movement conditions of all moving elements.
The drive arrangement according to claim 5 allows the moving masses of the drive lever to be minimized.
The features of claim 6 lead to a high stability of the drive unit with good operability of all drive elements. The effective radius of the globoid curve can be increased. This allows the slopes of the globoid curve to be made flat. The elements designed in this way are easily accessible for operation and maintenance.

Die Ausführung nach Anspruch 7 ermöglicht die einfache Anpassung der Vorrichtung an die Bedingungen eines Schrägfaches.
Der unabhängige Anspruch 8 definiert eine speziell mit geneigtem Webfach ausgebildete Antriebsvorrichtung, die die eingangs gestellte Aufgabe ebenfalls erfüllt.
Der Anspruch 9 beschreibt eine vorteilhafte Ausführung dieser Antriebsvorrichtung nach Anspruch 8. Die Vorteile bestehen in der Verwendung einer Globoidkurve mit großem mittleren Durchmesser.The embodiment according to claim 7 enables the device to be easily adapted to the conditions of a sloping compartment.
The independent claim 8 defines a drive device specially designed with an inclined shed which also fulfills the task set out above.
Claim 9 describes an advantageous embodiment of this drive device according to Claim 8. The advantages consist in the use of a globoid curve with a large mean diameter.

Die Erfindung soll an zwei Ausführungsbeispielen näher erläutert werden. In den dazugehörigen Zeichnungen zeigen:

Fig. 1:
eine bevorzugte Anordnung der erfinderischen Antriebsanordnung an einer Rundwebmaschine mit einem geneigten Webfach,
Fig. 2:
eine erfindungsgemäße Antriebsvorrichtung für die Teilschäfte eines horizontalen Webfaches und
Fig. 3:
eine zweite Variante einer Antriebsanordnung mit geneigtem Webfach.
The invention will be explained in more detail using two exemplary embodiments. In the accompanying drawings:
Fig. 1:
a preferred arrangement of the inventive drive arrangement on a circular loom with an inclined shed,
Fig. 2:
a drive device according to the invention for the partial shafts of a horizontal shed and
Fig. 3:
a second variant of a drive arrangement with an inclined shed.

Der in Fig. 1 gezeigte Teilschaftantrieb ist vorzugsweise für eine Rundwebmaschine vorgesehen, deren Webfach in Richtung der innenliegenden Gewebeanschlagkante nach oben geneigt ist.
Die Kettfadenscharen 11, 12 werden mittels der an sich bekannten Teilschäfte wechselweise in die beiden Kettfadenebenen versetzt. Durch das so geöffnete Fach wird in an sich bekannter Weise der Schützen 4 geführt.
Die Kettfadenschar 11 wird durch den Teilschaft 22 geführt, während die Kettfadenschar 12 durch die Ösen der Litzen des Teilschaftes 21 geführt wird.
Die Teilschäfte 21 und 22 werden in einem Winkel von etwa 45° entlang ihrer Bewegungsebenen 210 bzw. 220 geführt. Die Größe des Fachhubes soll die Führung eines Schützens 4 mit einer relativ großen Spule ermöglichen. The partial shaft drive shown in Fig. 1 is preferably provided for a circular loom, the shed of which is inclined upwards in the direction of the inner fabric stop edge.
The warp thread groups 11, 12 are alternately displaced into the two warp thread levels by means of the partial shafts known per se. The shooter 4 is guided through the compartment thus opened in a manner known per se.
The warp thread sheet 11 is guided through the partial shaft 22, while the warp thread sheet 12 is guided through the eyelets of the strands of the partial shaft 21.
The partial shafts 21 and 22 are guided at an angle of approximately 45 ° along their movement planes 210 and 220, respectively. The size of the specialist stroke should enable the guiding of a contactor 4 with a relatively large coil.

Die Teilschäfte 21, 22 sind an ihrem oberen Ende durch den oberen Bandabschnitt 23 miteinander verbunden. Dieser Bandabschnitt 23 umschlingt die Umlenkrolle 3 um 180°.
Die unteren Enden der Teilschäfte 21, 22 sind durch die unteren Bandabschnitte 24, 25 gehalten und gespannt. Der untere Bandabschnitt 24 wird über die gestellfeste Führungsrolle 31 auf den Führungsabschnitt 56 des Antriebshebels 5 bis zur Kupplung 52 des Antriebshebels 5 geführt.
Der Bandabschnitt 25 umschlingt teilweise die Führungsrolle 32 und wird von dort auf den Führungsabschnitt 57 des Antriebshebels 5 geführt. Dieser untere Bandabschnitt 25 wird durch die Kupplung 53 am Antriebshebel 5 gehalten.
Der Antriebshebel 5 hat sein Lager 51 zwischen den Endabschnitten der beiden unteren Bandabschnitte 24, 25. Dieses Lager 51 ist gestellfest.
Der Antriebshebel 5 ist in seinem oberen Bereich als Segment ausgebildet. Der Bogenabschnitt des Segmentes bildet die Führungsabschnitte 56, 57 für die beiden Bandabschnitte 24, 25 und wird durch die Kupplungen 52 und 53 nach unten hin begrenzt.
Zwischen diesen Kupplungen 52, 53 ist - vorzugsweise lösbar montiert - das Tastrollenlager 54 angeordnet. Dieses Tastrollenlager 54 trägt zwei Tastrollen 55, die zwischen sich formschlüssig den Wulst der Globoidkurve 6 umschließen. Diese Globoid-Kurve 6 erstreckt sich unterhalb der kreisförmig angeordneten Fachbildezone und wird durch den Globoidkurventräger 60 um die vertikale Längsachse 98 der Rundwebmaschine geführt und durch eine entsprechende Antriebsvorrichtung synchron zu dem Schützenantrieb umlaufend angetrieben.The partial shafts 21, 22 are connected to one another at their upper end by the upper band section 23. This band section 23 wraps around the deflection roller 3 by 180 °.
The lower ends of the partial shafts 21, 22 are held and tensioned by the lower band sections 24, 25. The lower band section 24 is guided via the guide roller 31 fixed to the frame onto the guide section 56 of the drive lever 5 up to the coupling 52 of the drive lever 5.
The belt section 25 partially wraps around the guide roller 32 and is guided from there onto the guide section 57 of the drive lever 5. This lower band section 25 is held by the coupling 53 on the drive lever 5.
The drive lever 5 has its bearing 51 between the end sections of the two lower band sections 24, 25. This bearing 51 is fixed to the frame.
The drive lever 5 is designed as a segment in its upper region. The curved section of the segment forms the guide sections 56, 57 for the two belt sections 24, 25 and is limited at the bottom by the couplings 52 and 53.
The traction roller bearing 54 is arranged between these couplings 52, 53, preferably detachably mounted. This tracer roller bearing 54 carries two tracer rollers 55, which formally enclose the bead of the globoid curve 6 between them. This globoid curve 6 extends below the circularly arranged shedding zone and is guided by the globoid cam carrier 60 around the vertical longitudinal axis 98 of the circular weaving machine and driven in rotation synchronously with the shooter drive by a corresponding drive device.

Diese Anordnung hat den Vorteil, daß bei gedrungener Bauweise in der Höhe die Antriebsbewegung der Teilschäfte 21, 22 realisiert werden kann. Die Globoidkurve 6 kann dabei auf einem relativ großen, mittleren Radius - bezogen auf die vertikale Maschinenachse - angeordnet werden.
Alle Führungselemente für die Teilschäfte 21, 22 unterliegen in jeder Phase ihrer Bewegung einer stabilen Führung. This arrangement has the advantage that the drive movement of the partial shafts 21, 22 can be realized in a compact height. The globoid curve 6 can be arranged on a relatively large, medium radius - based on the vertical machine axis.
All guide elements for the partial shafts 21, 22 are subject to stable guidance in each phase of their movement.

Alle Antriebselemente sind von der Bedienseite her sehr gut zugänglich. Die Größe der bewegten Massen kann bei entsprechender Gestaltung und Werkstoffwahl einem unbedingt notwendigen Minimum angenähert werden.
Die Größe des Fachhubes kann durch einfache konstruktive Anpassung der Elemente so gestaltet werden, daß eine optimale Arbeitsweise der Maschine möglich wird.All drive elements are easily accessible from the operator side. The size of the moving masses can be approximated to an absolutely necessary minimum with the appropriate design and choice of material.
The size of the specialist stroke can be designed by simple structural adjustment of the elements so that an optimal functioning of the machine is possible.

Die Ausführungsform nach Fig. 2 unterscheidet sich von der Vorrichtung nach Fig. 1 zunächst dadurch, daß das hier zu bildene Webfach 1' in horizontaler Ebene ausgerichtet ist. Die Kettfadenscharen 11' und 12' werden hier durch die Teilschäfte 21', 22' bewegt. Die Bewegungsebenen 210', 220' der Teilschäfte 21', 22' sind im wesentlichen senkrecht ausgerichtet.
Die Teilschäfte 21', 22' sind durch den oberen Bandabschnitt 23' miteinander verbunden. Dieser Bandabschnitt 23' wird über die Umlenkrolle 3' geführt.
Der untere Bandabschnitt 24' wird in der Bewegungsebene 210' durch die Führungsrolle 33 und über die Führungsrollen 36 und 37 außerhalb des Antriebshebels 7 wieder bis zur Führungsrolle 38, die etwa die Führungsebene 220' tangiert, geführt.
Das Ende dieses Bandabschnittes 24' ist dann wieder nach oben gerichtet und wird durch die am Antriebshebel 7 schwenkbar gelagerte Kupplung 72 gehalten. Von dieser Kupplung 72 führt der untere Bandabschnitt 25' an der Führungsrolle 34 vorbei zum unteren Ende des Teilschaftes 22'.
Der Antriebshebel 7 wird um das gestellfeste Lager 71 schwingend geführt. Dieses Lager 71 befindet sich vorzugsweise zwischen den Führungsbereichen der unteren Bandabschnitte 24' und 25'.
An dieser Stelle soll darauf hingewiesen werden, daß das Lager 71 auch außerhalb des unteren Bandabschnittes 24' angeordnet sein kann. In diesem Fall muß ausreichend Raum vorhanden sein, daß Teile des Antriebshebels 7 den unteren Bandabschnitt 24' im freien Abstand seitlich umgreifen können. The embodiment according to FIG. 2 differs from the device according to FIG. 1 initially in that the shed 1 ′ to be formed here is aligned in the horizontal plane. The warp thread groups 11 'and 12' are moved here by the partial shafts 21 ', 22'. The planes of motion 210 ', 220' of the partial shafts 21 ', 22' are oriented essentially vertically.
The partial shafts 21 ', 22' are connected to one another by the upper band section 23 '. This band section 23 'is guided over the deflection roller 3'.
The lower band section 24 'is again guided in the plane of movement 210' by the guide roller 33 and via the guide rollers 36 and 37 outside the drive lever 7 to the guide roller 38, which roughly affects the guide plane 220 '.
The end of this band section 24 'is then directed upwards again and is held by the coupling 72 pivotably mounted on the drive lever 7. From this coupling 72, the lower band section 25 'leads past the guide roller 34 to the lower end of the partial shaft 22'.
The drive lever 7 is guided to swing about the frame-fixed bearing 71. This bearing 71 is preferably located between the guide areas of the lower band sections 24 'and 25'.
At this point it should be pointed out that the bearing 71 can also be arranged outside the lower band section 24 '. In this case, sufficient space must be available for parts of the drive lever 7 to be able to grip the lower band section 24 'laterally at a free distance.

Die Globoidkurve 8 ist in diesem Ausführungsbeispiel sehr nahe an der Bewegungsebene 220' des inneren Teilschaftes 22' angeordnet. Der Radius dieser Globoidkurve 8 ist - bezogen auf die vertikale Achse der Maschine - sehr groß. Auf diese Weise sind relativ flache Anstiege der Antriebskurve 8 möglich. Die Globoidkurve 8 ist hier als Nutkurve ausgebildet. In diese Nutkurve 8 greift vorzugsweise eine einzige Tastrolle 75 des Antriebshebels 7 ein. Die Globoidkurve 8 wird hier am Globoidkurventräger 80 befestigt. Sie wird von diesem um die vertikale Maschinenachse 98 geführt und in an sich bekannter Weise angetrieben.
Der Vorteil dieser Ausführung besteht darin, daß die bewegten Massen des Antriebshebels 7 deutlich reduziert werden können. Die Lager 71 sind zum Zwecke der Wartung leicht zugängig.
Es ist bei einer derartigen Ausführung auch denkbar, daß der untere Bandabschnitt 24' in der Bewegungsebene 210' durch den Bewegungsbereich des Antriebshebels 7 geführt werden kann. Bei dieser Ausführung sollte der Antriebshebel 7 jedoch so gestaltet sein, daß er im Führungsbereich dieses Bandabschnittes 24' eine entsprechende Ausnehmung hat und diesen Bandabschnitt seitlich umgreifen kann.
Man kann so auch die Zahl der Führungs- oder Umlenkrollen deutlich reduzieren. In diesem Fall hätten die Führungsrollen 33 und 34 nur noch Sicherungsfunktionen. Die Führungsrollen 36 und 37 entfallen und die Führungsrolle 38 erfüllt die Funktion einer unteren Umlenkrolle. Letztere sollte deshalb mit einem entsprechenden Durchmesser versehen werden.In this exemplary embodiment, the globoid curve 8 is arranged very close to the plane of movement 220 'of the inner partial shaft 22'. The radius of this globoid curve 8 is very large in relation to the vertical axis of the machine. In this way, relatively flat increases in the drive curve 8 are possible. The globoid curve 8 is designed here as a groove curve. A single feeler roller 75 of the drive lever 7 preferably engages in this groove curve 8. The globoid curve 8 is attached to the globoid cam carrier 80 here. It is guided by the latter about the vertical machine axis 98 and driven in a manner known per se.
The advantage of this embodiment is that the moving masses of the drive lever 7 can be significantly reduced. The bearings 71 are easily accessible for maintenance purposes.
With such an embodiment, it is also conceivable that the lower band section 24 'can be guided in the movement plane 210' through the movement range of the drive lever 7. In this embodiment, however, the drive lever 7 should be designed such that it has a corresponding recess in the guide region of this band section 24 'and can grip around this band section laterally.
You can also significantly reduce the number of guide or deflection rollers. In this case, the guide rollers 33 and 34 would only have securing functions. The guide rollers 36 and 37 are omitted and the guide roller 38 fulfills the function of a lower deflection roller. The latter should therefore be given an appropriate diameter.

Die Vorrichtung nach Fig. 3 zeigt eine Antriebsvorrichtung für die Teilschäfte 21, 22 einer Rundwebmaschine mit einem nach innen und oben geneigten Webfach. Die unteren Bandabschnitte 24" und 25" werden durch die Führungsrollen 31' und 32' senkrecht nach unten abgelenkt, um die Rolle 38' geführt und im Angriffsbereich der Kupplung 92 miteinander verbunden. 3 shows a drive device for the partial shafts 21, 22 of a circular weaving machine with an inward and upwardly inclined shed. The lower belt sections 24 "and 25" are guided by the guide rollers 31 ' and 32 'deflected vertically downward, guided around the roller 38' and in the area of attack the clutch 92 connected to each other.

Ein Antriebshebel 9, der um das gestellfeste Lager 91 schwingt, ist über eine Koppel mit der Kupplung 92 verbunden. An einem nach oben gerichteten Arm dieses Antriebshebels 9 hat die Tastrolle 95 ihr Lager. Sie arbeitet mit der Globoidkurve 96 zusammen, die am Kurventräger 97 ihr Lager hat. Der Globoidkurventräger 97 rotiert um die vertikale Maschinenachse 98.
Diese Ausführung eignet sich insbesondere für solche Rundwebmaschinen, bei denen man, ausgehend von Antriebsmitteln für die Teilschäfte mit horizontalem Webfach, durch das Neigen der Bewegungsebene 220, 210 der Teilschäfte nach oben und außen die Länge des Webfaches vor der Anschlagkante vergrößern möchte. Auf diese Weise schafft man Raum für größere Spulen in den Schützen 4. A drive lever 9, which swings about the bearing 91 fixed to the frame, is connected to the clutch 92 via a coupling. The feeler roller 95 has its bearing on an upward arm of this drive lever 9. It works with the globoid curve 96, which has its bearing on the curve carrier 97. The globoid cam carrier 97 rotates about the vertical machine axis 98.
This version is particularly suitable for circular weaving machines in which, starting from drive means for the partial shafts with a horizontal shed, the inclination of the plane of movement 220, 210 of the partial shafts upwards and outwards would like to increase the length of the shed in front of the stop edge. In this way, space is created for larger coils in the contactors 4.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1, 1'1, 1 '
Webfachshed
11, 11'11, 11 '
Kettfadenscharwarp
12, 12'12, 12 '
Kettfadenscharwarp
(2)(2)
Teilschaft AntriebseinheitPart of drive unit
21, 21'21, 21 '
Teilschaftpart shaft
210, 210'210, 210 '
Bewegungsebene des TeilschaftesMovement level of the partial shaft
22, 22'22, 22 '
Teilschaftpart shaft
220, 220'220, 220 '
Teilschaft BewegungsebenePartial plane of movement
23, 23'23, 23 '
oberer Bandabschnittupper band section
24, 24',24"24, 24 ', 24 "
unterer Bandabschnittlower band section
25, 25',25"25, 25 ', 25 "
unterer Bandabschnittlower band section
3, 3'3, 3 '
Umlenkrolle, obenDeflection roller, top
31, 31'31, 31 '
Führungsrolle (in Teilschaftebene, Fig. 1)Leadership role (in part level, Fig. 1)
32, 32'32, 32 '
Führungsrolle (in Teilschaftebene, Fig. 1)Leadership role (in part level, Fig. 1)
33, 3433, 34
Führungsrolle (in Teilschaftebene, Fig. 2)Guide role (in part level, Fig. 2)
36, 3736, 37
Führungsrollenguide rollers
38, 38'38, 38 '
Umlenkrolleidler pulley
44
SchützenProtect
55
Antriebshebeldrive lever
5151
Lagercamp
52, 5352, 53
Kupplungclutch
5454
TastrollenlagerTastrollenlager
5555
Tastrollenfeeler rolls
56, 5756, 57
Führungsabschnitt guide section
66
Globoidkurvegloboid cam
6060
GloboidkurventrägerGloboidkurventräger
77
Antriebshebeldrive lever
7171
Lagercamp
7272
Kupplungclutch
7575
Tastrollefollower roll
88th
Globoidkurvegloboid cam
8080
GloboidkurventrägerGloboidkurventräger
99
Antriebshebeldrive lever
9191
Lagercamp
9292
Kupplungclutch
9595
Tastrollefollower roll
9696
Globoidkurvegloboid cam
9797
Kurventrägercam support
9898
Maschinenachse, vertikalMachine axis, vertical

(In Klammern stehende Ziffern haben nur ordnende Funktionen. Sie sind in den Zeichnungen und in der Beschreibung nicht enthalten)(Numbers in brackets only have an ordering function. They are in the Drawings and not included in the description)

Claims (9)

  1. A drive device for the parting shafts of circular looms
    where the parting shafts (21, 22), in pairs, are driven in opposite directions and guided parallel to each other,
    where lower ribbon sections (24, 25) are assigned to the parting shafts (21, 22) of each pair, and where at least one of said sections is guided by a guide roller (32, 38), and
    where a driving lever (5, 7), swinging around a frame-fixed bearing (51, 71), is assigned to the ribbon sections (24, 25) of a pair of parting shafts (21, 22), and where said driving lever is connected to these ribbon sections by at least one coupling (52, 72) and contains at least one feeler roller (55, 75) for interacting with a globoid cam, which is rotatably driven around the vertical axis (98) of the circular loom,
    characterized in that the frame-fixed bearing (51; 71) of the driving lever (5; 7) is arranged outside of the motion plane (220) of the respective inner parting shaft (22, 22'), and
    that the feeler roller (55; 75) and per one of the couplings (52, 53; 72) are arranged on the same side of the bearing (51; 71).
  2. A drive device according to Claim 1, characterized in that the feeler roller (55) on the driving lever (5) is arranged radially within the motion radius of the coupling (52, 53), and
    that per one coupling (52, 54) is designated for each lower ribbon section (24, 25) on both sides of the feeler roller (55) on the driving lever (5).
  3. A drive device according to Claim 1, characterized in that the feeler roller (75) of the driving lever (7) is supported radially outside the coupling (72), and
    that both ends of the lower ribbon sections (24', 25') are held by the single coupling (72).
  4. A drive device according to Claim 1 and one of the Claims 2 or 3,
    characterized in that guiding elements (56, 57; 34, 38) are assigned to the lower ribbon sections (24; 24', 25; 25) close to the motion area of the coupling (52, 53; 72).
  5. A drive device according to Claim 4, characterized in that the guiding elements are curvilinear guiding sections (56, 57) on the driving lever (5), which are adjacent to the respective coupling (52, 53) and directed to the first point of contact of the respective ribbon section (24, 25).
  6. A drive device according to Claim 4, characterized in that the guiding elements are frame-fixed guide rollers (34, 38), whose tangential operating point in the central position of the driving lever (7) is approximately vertical above the radius of the assigned coupling (72).
  7. A drive device according to Claim 1, characterized in that frame-fixed guide rollers (31, 32), which are tangent to the outer motion plane of their parting shafts (21, 22), are designated for each lower ribbon section (24, 25), and
    that guiding cams (56, 57) for the ribbon sections (24, 25) are assigned to the couplings (52, 53) on the driving lever (5) on both sides of the feeler roller (55).
  8. A drive device for the parting shafts of circular looms
    where the parting shafts (21, 22), in pairs, are driven in opposite directions and guided parallel to each other in a single plane,
    where lower ribbon sections (25") are assigned to the parting shafts (21, 22) of each pair, and where at least one of said sections is guided by a guide roller (38'), and
    where a driving lever (9), swinging around a frame-fixed bearing (91), is assigned to the ribbon sections of a pair of parting shafts (21, 22), and where said driving lever which is provided at a distance from its frame-fixed bearing (91) with a bearing for a feeler roller (95), which is connected to the ribbon sections (24", 25") by at least one coupling, and which is driven either directly or via intermediate elements by a cam mechanism consisting of a cam, which is rotatably driven around the vertical axis (98) of the circular loom, and of at least one feeler roller (95) on the driving lever (9), characterized in that the parting shafts (21, 22) are guided in an upwardly and outwardly inclined plane,
    that the swinging driving lever is designed as an angular driving lever (9), and
    that the rotatably driven cam is a globoid cam (96), arranged on the end face of its carrier, and which is matched to the trajectory of the feeler roller (95).
  9. A drive device according to Claim 8 characterized in that each lower ribbon section (24", 25") has one assigned guide roller (31', 32') immediately below the motion area of the parting shafts (21, 22),
    which are tangent to the outer motion plane of the parting shafts (21, 22), and
    which are, at least partially, wrapped by the lower ribbon sections (24", 25"), and
    that the coupling (92) between the driving lever (9) and the lower ribbon sections (24", 25") is arranged below these guide rollers (31', 32').
EP99936242A 1998-04-08 1999-04-03 Drive device for the parting shafts of circular looms Expired - Lifetime EP1070163B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19815821A DE19815821C1 (en) 1998-04-08 1998-04-08 Drive device for the partial shafts of circular looms
DE19815821 1998-04-08
PCT/DE1999/001343 WO1999051805A2 (en) 1998-04-08 1999-04-03 Drive device for the parting shafts of circular looms

Publications (2)

Publication Number Publication Date
EP1070163A2 EP1070163A2 (en) 2001-01-24
EP1070163B1 true EP1070163B1 (en) 2002-09-04

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EP (1) EP1070163B1 (en)
AT (1) ATE223526T1 (en)
AU (1) AU5147299A (en)
DE (1) DE19815821C1 (en)
WO (1) WO1999051805A2 (en)

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CN103205847A (en) * 2013-03-11 2013-07-17 安徽省沙克塑料机械设备有限公司 Circular weaving machine with small plane cam
TWI776921B (en) * 2017-07-21 2022-09-11 奧地利商史太林格有限公司 Circular loom

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CN101984167A (en) * 2010-08-06 2011-03-09 屠洪明 Heald belt transmission mechanism of high-speed plastic circular weaving machine
CN109371538A (en) * 2018-12-10 2019-02-22 温州亿科塑料机械有限公司 A kind of plastic circular loom

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CH601530A5 (en) * 1975-09-04 1978-07-14 Indupack Ag
AT371846B (en) * 1981-11-25 1983-08-10 Chemiefaser Lenzing Ag ROUND WEAVING MACHINE
CH660042A5 (en) * 1983-07-20 1987-03-13 Huemer Franz Xaver ROUND WEAVING MACHINE.
AT387797B (en) * 1985-11-26 1989-03-10 Huang Ching Long Weft thread monitor for a circular weaving machine
AT385783B (en) * 1986-07-14 1988-05-10 Chemiefaser Lenzing Ag ROUND WEAVING MACHINE

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103205847A (en) * 2013-03-11 2013-07-17 安徽省沙克塑料机械设备有限公司 Circular weaving machine with small plane cam
TWI776921B (en) * 2017-07-21 2022-09-11 奧地利商史太林格有限公司 Circular loom

Also Published As

Publication number Publication date
EP1070163A2 (en) 2001-01-24
WO1999051805A3 (en) 1999-12-16
DE19815821C1 (en) 1999-12-02
ATE223526T1 (en) 2002-09-15
AU5147299A (en) 1999-10-25
WO1999051805A2 (en) 1999-10-14

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