EP0418195A1 - Shuttle picking mechanism for a loom - Google Patents

Shuttle picking mechanism for a loom Download PDF

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Publication number
EP0418195A1
EP0418195A1 EP90810657A EP90810657A EP0418195A1 EP 0418195 A1 EP0418195 A1 EP 0418195A1 EP 90810657 A EP90810657 A EP 90810657A EP 90810657 A EP90810657 A EP 90810657A EP 0418195 A1 EP0418195 A1 EP 0418195A1
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EP
European Patent Office
Prior art keywords
lever
acceleration
drive shaft
coupling gear
impact
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
EP90810657A
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German (de)
French (fr)
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EP0418195B1 (en
Inventor
Erwin Pfarrwaller
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 EP0418195A1 publication Critical patent/EP0418195A1/en
Application granted granted Critical
Publication of EP0418195B1 publication Critical patent/EP0418195B1/en
Anticipated expiration legal-status Critical
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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/24—Mechanisms for inserting shuttle in shed
    • D03D49/26—Picking mechanisms, e.g. for propelling gripper shuttles or dummy shuttles
    • D03D49/28—Driving mechanisms for the picker stick
    • D03D49/32—Driving mechanisms for the picker stick operated by previously-loaded spring or equivalent
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/12—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein single picks of weft thread are inserted, i.e. with shedding between each pick
    • D03D47/24—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein single picks of weft thread are inserted, i.e. with shedding between each pick by gripper or dummy shuttle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18288—Cam and lever

Definitions

  • the invention relates to a projectile acceleration device of a weaving machine with a drive shaft, acceleration shaft, impact lever, oil brake and a knee joint on a roller lever.
  • Such devices are known for example from CH-PS 313 155 or US-PS 2,813,549.
  • the impact lever and a torsion bar connected to it are tensioned by a cam on the drive shaft via the roller lever and the knee joint.
  • the relatively heavy roller lever must now also take part in the entire movement of the striking lever. This requires a great deal of energy and power to accelerate and to slow down the movement again after the projectile has been fired. So this means a considerable expenditure of energy, large mechanical loads and wear and increasing braking problems, with which the performance limits of the weaving machines are reached.
  • this object is achieved by the features of claim 1.
  • the introduction of a coupling gear with two articulated positions greatly reduces the movement of the relatively heavy roller lever when firing it, and the tensioning element for tensioning the impact lever or the torsion bar beyond its extended position also allows a much more favorable geometric arrangement to be achieved. Overall, energy consumption, forces and wear are significantly reduced and the performance of the loom is increased accordingly.
  • a particularly simple embodiment has a roller lever with two rollers, both of which run on only one cam disk of the drive shaft.
  • a simple version of the tensioning element has an eccentric rocker arm on the drive shaft and a tensioning tab on the acceleration shaft.
  • Particularly high weaving machine performance can be achieved with a striking lever that has an end piece that acts directly on the impact surface of the projectile when shot, without an intermediate striking piece. Because this allows larger acceleration angles and thus higher performance.
  • a striking lever 4 a tensioning flap 9 with a bearing groove 24 and an arm 18 of an oil brake 17 are firmly connected to the acceleration shaft 10.
  • a swivel bracket 22 also rotates on shaft 10.
  • a cam disk 34 with locking and release cams 2 and tensioning cams 30 and an eccentric rocker arm 20 are connected to the drive shaft 12.
  • Corresponding locking and release roller 1 and tension roller 31 are assigned to cams 2 and 30.
  • the rollers 1 and 31 carry a roller lever 32 with an axis of rotation 33.
  • a bracket 7 is coupled to the roller lever 32 via a knee joint 15 and to the striking lever 4 via a further joint 16. Tab 7 and joints 15 and 16 form the coupling gear 8.
  • the striking lever 4 opens into an end piece 5, which strikes the projectile 6 in direct launch and accelerates it in the direction 14.
  • the end piece 5 is here directly fixed or rotatable only on the striking lever 4, in contrast to previous striking pieces which run in an external guide.
  • the function of the projectile acceleration device according to the invention is shown schematically in FIG. 2.
  • Fig. 1a shows the device in its starting position a with the first buckling position 8a of the coupling gear before the projectile is fired.
  • the roller 1 of the roller lever 32a runs on the locking and release cam 2 up to its release point 3 and thereby holds the knee joint 15 and the striking lever 4a under tension.
  • the trigger point 3 is exceeded, the knee joint 15 is bent, the striking lever 4 moves through the angle W1 to position 4b and thereby accelerates the projectile 6 in direction 14 to maximum speed.
  • the coupling gear 8b is stretched with its second joint 16 and the roller lever 32b here undergoes a reversal of movement, that is to say it has the speed 0 and thus also the kinetic energy 0.
  • the heavy roller lever has one in this position large kinetic energy absorbed, which is lost for the acceleration of the projectile.
  • the striking lever 4 is then braked via the angle W2 by the oil brake 17 to a standstill in its end position 4c, the coupling gear reaching its second articulation position 8c.
  • the striking lever as desired, sweeps very large angles W1 and W2 at high speed, the movement of the roller lever 32 is very greatly reduced in accordance with the small angles W3 and W4.
  • the subsequent tensioning of the striking lever or its torsion bar is now carried out by the tensioning member 13 with the eccentric rocker arm 20, the coupling gear 8 with the joint 16 moving through the angle W6 beyond the extended position 8a (FIG. 2).
  • the impact lever is then tensioned further by the tensioning roller 31 of the roller lever via the coupling gear 8 by the angle W7 until the firing position 4a, 8a and 32a.
  • the tensioning element in addition to the eccentric rocker 20, consists of a swivel bracket 22 with a hinge pin 21 which engages in a bearing groove 24 of the tensioning lug 9 and thereby tensions the striking lever 4.
  • Fig. 4 shows a clamping member with a bolt 37 on the eccentric rocker 20, which is in an arcuate Guide groove 36 of the flap 9 engages.
  • a bolt 39 of the tensioning lug 9 runs in an arcuate fork guide 38 of the eccentric rocker 20.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)
  • Braking Arrangements (AREA)

Abstract

Die Projektilbeschleunigungsvorrichtung weist ein an einen Rollenhebel (32) angelenktes Koppelgetriebe (8) mit zwei Knicklagen (8a, 8c) und ein von der Antriebswelle angetriebenes Spannorgan (13) auf. Das Spannorgan spannt das Koppelgetriebe über seine Strecklage (8b) hinaus. Damit werden grosse Bewegungswinkel des Schlaghebels (W1, W2) bei stark reduzierten Bewegungen des Rollenhebels (W3, W4) erreicht.The projectile acceleration device has a coupling gear (8) articulated on a roller lever (32) with two buckling positions (8a, 8c) and a tensioning element (13) driven by the drive shaft. The tensioning element tensions the coupling gear beyond its extended position (8b). Large movement angles of the striking lever (W1, W2) are thereby achieved with greatly reduced movements of the roller lever (W3, W4).

Description

Die Erfindung betrifft eine Projektilbeschleunigungsvor­richtung einer Webmaschine mit Antriebswelle, Beschleuni­gungswelle, Schlaghebel, Oelbremse und einem Kniegelenk an einem Rollenhebel. Solche Vorrichtungen sind beispielswei­se aus CH-PS 313 155 bzw. US-PS 2 813 549 bekannt. Dabei wird der Schlaghebel und ein mit ihm verbundener Torsions­stab von einer Kurvenscheibe auf der Antriebswelle über den Rollenhebel und das Kniegelenk gespannt. Beim Abschuss muss nun auch der relativ schwere Rollenhebel die ganze Bewegung des Schlaghebels zwangsläufig mitmachen. Dies erfordert einen grossen Energie- und Leistungsaufwand zum Beschleunigen wie auch zum wieder Abbremsen der Bewegung nach dem Abschuss des Projektils. Dies bedeutet also einen erheblichen Energieaufwand, grosse mechanische Belastungen und Abnützungen und zunehmende Bremsprobleme, womit die Leistungsgrenzen der Webmaschinen erreicht werden.The invention relates to a projectile acceleration device of a weaving machine with a drive shaft, acceleration shaft, impact lever, oil brake and a knee joint on a roller lever. Such devices are known for example from CH-PS 313 155 or US-PS 2,813,549. The impact lever and a torsion bar connected to it are tensioned by a cam on the drive shaft via the roller lever and the knee joint. When firing, the relatively heavy roller lever must now also take part in the entire movement of the striking lever. This requires a great deal of energy and power to accelerate and to slow down the movement again after the projectile has been fired. So this means a considerable expenditure of energy, large mechanical loads and wear and increasing braking problems, with which the performance limits of the weaving machines are reached.

Um die Webmaschinenleistung weiter steigern zu können, wie auch um Energieverbrauch und Abnützung relativ zu senken, wird eine verbesserte Projektilbeschleunigungsvorrichtung gesucht. Deren Aufgabe ist es, obige Probleme zu überwin­den und höhere Webmaschinenleistungen und grössere Effi­zienz zu erreichen.In order to be able to further increase the weaving machine performance as well as to reduce energy consumption and wear relatively, an improved projectile acceleration device is sought. Their task is to overcome the above problems and to achieve higher weaving machine performance and greater efficiency.

Diese Aufgabe wird erfindungsgemäss durch die Merkmale von Anspruch 1 gelöst. Durch die Einführung eines Koppelge­triebes mit zwei Knicklagen wird die Bewegung des relativ schweren Rollenhebels beim Abschuss stark reduziert und durch das Spannorgan zum Spannen des Schlaghebels bzw. des Torsionsstabs über seine Strecklage hinaus kann überdies eine wesentlich günstigere geometrische Anordnung erreicht werden. Insgesamt werden also Energiebedarf, auftretende Kräfte und Abnützung wesentlich reduziert und die Lei­stungsfähigkeit der Webmaschine entsprechend erhöht.According to the invention, this object is achieved by the features of claim 1. The introduction of a coupling gear with two articulated positions greatly reduces the movement of the relatively heavy roller lever when firing it, and the tensioning element for tensioning the impact lever or the torsion bar beyond its extended position also allows a much more favorable geometric arrangement to be achieved. Overall, energy consumption, forces and wear are significantly reduced and the performance of the loom is increased accordingly.

Die abhängigen Ansprüche betreffen vorteilhafte Weiterbil­dungen der Erfindung. Eine besonders einfache Ausführung weist einen Rollenhebel mit zwei Rollen auf, welche beide auf nur einer Kurvenscheibe der Antriebswelle ablaufen. Eine einfache Ausführung des Spannorgans weist eine Exzen­terschwinge auf der Antriebswelle und ein Spannlappen auf der Beschleunigungswelle auf. Besonders hohe Webmaschinen­leistungen können mit einem Schlaghebel erreicht werden, der ein Endstück aufweist, das beim Abschuss direkt auf die Stossfläche des Projektils einwirkt ohne zwischenge­schaltetes Schlagstück. Denn dies erlaubt grössere Be­schleunigungswinkel und damit höhere Leistungen.The dependent claims relate to advantageous developments of the invention. A particularly simple embodiment has a roller lever with two rollers, both of which run on only one cam disk of the drive shaft. A simple version of the tensioning element has an eccentric rocker arm on the drive shaft and a tensioning tab on the acceleration shaft. Particularly high weaving machine performance can be achieved with a striking lever that has an end piece that acts directly on the impact surface of the projectile when shot, without an intermediate striking piece. Because this allows larger acceleration angles and thus higher performance.

Im folgenden wird die Erfindung anhand von Beispielen im Zusammenhang mit den Zeichnungen näher erläutert. Es zeigt:

  • Fig. 1 eine erfindungsgemässe Projektilbeschleunigungs­vorrichtung mit Koppelgetriebe und Spannorgan;
  • Fig. 2 schematisch den Mechanismus einer weiteren Projektilbeschleunigungsvorrichtung;
  • Fig. 3 ein Spannorgan mit Spannlappen und Schwenk­lasche;
  • Fig. 4 ein Spannorgan mit bogenförmiger Führungsnut des Spannlappens und
  • Fig. 5 ein Spannorgan mit Gabelführung an der Exzenter­schwinge.
The invention is explained in more detail below with the aid of examples in connection with the drawings. It shows:
  • 1 shows a projectile acceleration device according to the invention with a coupling gear and tensioning element;
  • 2 schematically shows the mechanism of a further projectile acceleration device;
  • 3 shows a tensioning element with a tensioning flap and swivel bracket;
  • Fig. 4 shows a clamping member with an arcuate guide groove of the clamping tab and
  • Fig. 5 shows a tensioning element with fork guide on the eccentric swing arm.

Bei der erfindungsgemässen Projektilbeschleunigungsvor­richtung von Fig. 1a, b sind ein Schlaghebel 4, ein Spann­lappen 9 mit Lagernut 24 und ein Arm 18 einer Oelbremse 17 fest mit der Beschleunigungswelle 10 verbunden. Eine Schwenklasche 22 läuft drehbar ebenfalls auf Welle 10. Mit der Antriebswelle 12 sind eine Kurvenscheibe 34 mit Arre­tier- und Auslösenocken 2 und Spannnocken 30 sowie eine Exzenterschwinge 20 verbunden. Den Nocken 2 und 30 sind entsprechende Arretier- und Auslöserolle 1 und Spannrolle 31 zugeordnet. Die Rollen 1 und 31 trägt ein Rollenhebel 32 mit Drehachse 33. Eine Lasche 7 ist über ein Kniegelenk 15 mit dem Rollenhebel 32 und über ein weiteres Gelenk 16 mit dem Schlaghebel 4 gekoppelt. Lasche 7 und Gelenke 15 und 16 bilden das Koppelgetriebe 8. Der Schlaghebel 4 mün­det in ein Endstück 5, welches in Direktabschuss auf das Projektil 6 trifft und dieses in Richtung 14 beschleunigt. Das Endstück 5 ist hier unmittelbar fest oder drehbar nur am Schlaghebel 4 fixiert, im Gegensatz zu bisherigen Schlagstücken, welche in einer externen Führung laufen. Die Funktion der erfindungsgemässen Projektilbeschleuni­gungsvorrichtung ist in Fig. 2 schematisch dargestellt.In the projectile acceleration device according to the invention from FIGS. 1 a, b, a striking lever 4, a tensioning flap 9 with a bearing groove 24 and an arm 18 of an oil brake 17 are firmly connected to the acceleration shaft 10. A swivel bracket 22 also rotates on shaft 10. A cam disk 34 with locking and release cams 2 and tensioning cams 30 and an eccentric rocker arm 20 are connected to the drive shaft 12. Corresponding locking and release roller 1 and tension roller 31 are assigned to cams 2 and 30. The rollers 1 and 31 carry a roller lever 32 with an axis of rotation 33. A bracket 7 is coupled to the roller lever 32 via a knee joint 15 and to the striking lever 4 via a further joint 16. Tab 7 and joints 15 and 16 form the coupling gear 8. The striking lever 4 opens into an end piece 5, which strikes the projectile 6 in direct launch and accelerates it in the direction 14. The end piece 5 is here directly fixed or rotatable only on the striking lever 4, in contrast to previous striking pieces which run in an external guide. The function of the projectile acceleration device according to the invention is shown schematically in FIG. 2.

Fig. 1a zeigt die Vorrichtung in ihrer Ausgangslage a mit erster Knicklage 8a des Koppelgetriebes vor Abschuss des Projektils. Die Rolle 1 des Rollenhebels 32a läuft dabei auf dem Arretier- und Auslösenocken 2 bis zu dessen Aus­lösepunkt 3 und hält dadurch das Kniegelenk 15 und den Schlaghebel 4a gespannt. Durch Ueberschreiten des Auslöse­punktes 3 wird das Kniegelenk 15 geknickt, der Schlaghebel 4 bewegt sich um den Winkel W1 bis zur Stellung 4b und beschleunigt dabei das Projektil 6 in Richtung 14 auf maximale Geschwindigkeit. In dieser Stellung b ist das Koppelgetriebe 8b mit dessen zweitem Gelenk 16 gestreckt und der Rollenhebel 32b erfährt hier eine Bewegungsumkehr, hat also die Geschwindigkeit 0 und damit auch die kineti­sche Energie 0. Im Gegensatz dazu hat bei bisherigen Pro­jektilbeschleunigungsvorrichtungen der schwere Rollenhebel in dieser Stellung eine grosse kinetische Energie aufge­nommen, welche für die Beschleunigung des Projektils ver­loren ist.Fig. 1a shows the device in its starting position a with the first buckling position 8a of the coupling gear before the projectile is fired. The roller 1 of the roller lever 32a runs on the locking and release cam 2 up to its release point 3 and thereby holds the knee joint 15 and the striking lever 4a under tension. When the trigger point 3 is exceeded, the knee joint 15 is bent, the striking lever 4 moves through the angle W1 to position 4b and thereby accelerates the projectile 6 in direction 14 to maximum speed. In this position b, the coupling gear 8b is stretched with its second joint 16 and the roller lever 32b here undergoes a reversal of movement, that is to say it has the speed 0 and thus also the kinetic energy 0. In contrast to this, in previous projectile acceleration devices the heavy roller lever has one in this position large kinetic energy absorbed, which is lost for the acceleration of the projectile.

Der Schlaghebel 4 wird anschliessend über den Winkel W2 von der Oelbremse 17 bis zum Stillstand in seiner Endlage 4c gebremst, wobei das Koppelgetriebe seine zweite Knick­lage 8c erreicht. Während also der Schlaghebel, wie ange­strebt, sehr grosse Winkel W1 und W2 mit hoher Geschwin­digkeit überstreicht, wird die Bewegung des Rollenhebels 32 entsprechend den kleinen Winkeln W3 und W4 sehr stark reduziert. Das anschliessende Spannen des Schlaghebels, bzw. seines Torsionsstabes, erfolgt nun durch das Spann­organ 13 mit der Exzenterschwinge 20, wobei sich das Koppelgetriebe 8 mit Gelenk 16 um den Winkel W6 bis über die Strecklage 8a hinaus bewegt (Fig. 2). Anschliessend wird der schlaghebel durch die Spannrolle 31 des Rollen­hebels über das Koppelgetriebe 8 um den Winkel W7 weiter gespannt bis zur Abschussstellung 4a, 8a und 32a.The striking lever 4 is then braked via the angle W2 by the oil brake 17 to a standstill in its end position 4c, the coupling gear reaching its second articulation position 8c. Thus, while the striking lever, as desired, sweeps very large angles W1 and W2 at high speed, the movement of the roller lever 32 is very greatly reduced in accordance with the small angles W3 and W4. The subsequent tensioning of the striking lever or its torsion bar is now carried out by the tensioning member 13 with the eccentric rocker arm 20, the coupling gear 8 with the joint 16 moving through the angle W6 beyond the extended position 8a (FIG. 2). The impact lever is then tensioned further by the tensioning roller 31 of the roller lever via the coupling gear 8 by the angle W7 until the firing position 4a, 8a and 32a.

In Fig. 1 und 3 besteht das Spannorgan nebst der Exzenter­schwinge 20 aus einer Schwenklasche 22 mit einem Gelenk­bolzen 21, welcher in eine Lagernut 24 des Spannlappens 9 eingreift und dadurch den Schlaghebel 4 spannt.1 and 3, the tensioning element, in addition to the eccentric rocker 20, consists of a swivel bracket 22 with a hinge pin 21 which engages in a bearing groove 24 of the tensioning lug 9 and thereby tensions the striking lever 4.

Fig. 4 zeigt ein Spannorgan mit einem Bolzen 37 an der Exzenterschwinge 20, welcher in eine bogenförmige Führungsnut 36 des Spannlappens 9 eingreift. Bei der umge­kehrten Anordnung von Fig. 5 läuft ein Bolzen 39 des Spannlappens 9 in einer bogenförmigen Gabelführung 38 der Exzenterschwinge 20. Diese erfindungsgemässen Spannorgane ergeben günstige geometrische Bedingungen, d.h. günstige Spannwinkel sowohl für das Spannorgan selber als auch für das restliche Spannen des Schlaghebels um den Winkel W7 mittels Rollenhebel 32 und Koppelgetriebe 8. Sie ermögli­chen damit höhere Spannleistungen bei reduziertem Aufwand und Verschleiss. Der Winkel W7 kann sehr klein gewählt werden, z.B. nur 1 bis 2 Grad, während W1 und W2 z.B. mit 20 bis 30 Grad bei Direktabschuss relativ grosse Werte erreichen können.Fig. 4 shows a clamping member with a bolt 37 on the eccentric rocker 20, which is in an arcuate Guide groove 36 of the flap 9 engages. In the reverse arrangement of FIG. 5, a bolt 39 of the tensioning lug 9 runs in an arcuate fork guide 38 of the eccentric rocker 20. These tensioning members according to the invention result in favorable geometric conditions, ie favorable tensioning angles both for the tensioning member itself and for the remaining tensioning of the striking lever around the Angle W7 by means of roller lever 32 and coupling gear 8. They enable higher clamping capacities with reduced effort and wear. The angle W7 can be chosen to be very small, for example only 1 to 2 degrees, while W1 and W2, for example with 20 to 30 degrees, can reach relatively large values when fired directly.

BezeichnungslisteLabel list

  • 1 Arretier- und Auslöserolle1 locking and release roller
  • 2 Arretier- und Auslösenocken2 locking and release cams
  • 3 Auslösepunkt3 trigger point
  • 4 Schlaghebel4 striking levers
  • 5 Endstück5 end piece
  • 6 Projektil6 projectile
  • 7 Lasche7 tab
  • 8 Koppelgetriebe8 coupling gears
  • 9 Spannlappen9 flaps
  • 10 Beschleunigungswelle10 acceleration shaft
  • 12 Antriebswelle12 drive shaft
  • 13 Spannorgan13 tensioning element
  • 14 Abschussrichtung14 launch direction
  • 15 Kniegelenk15 knee joint
  • 16 weiteres Gelenk16 additional joint
  • 17 Oelbremse17 Oil brake
  • 18 Arm18 arm
  • 20 Exzenterschwinge20 eccentric rockers
  • 21 Gelenkbolzen21 hinge pin
  • 22 Schwenklasche22 swivel bracket
  • 24 Lagernut24 bearing groove
  • 30 Spannnocken30 clamping cams
  • 31 Spannrolle31 tension pulley
  • 32 Rollenhebel32 roller levers
  • 33 Drehachse von 3233 axis of rotation of 32
  • 34 Kurvenscheibe mit 2, 3034 cam with 2, 30
  • 36 bogenförmige Führungsnut36 arcuate guide groove
  • 37 Bolzen37 bolts
  • 38 bogenförmige Gabelführung38 curved fork guide
  • 39 Bolzen39 bolts
  • W1 WinkelW1 angle
  • W2W2
  • W3W3
  • W4W4
  • W6D6
  • W7W7
  • a 1. Knicklagea 1. Kink position
  • b Strecklageb Stretch position
  • c 2. Knicklagec 2. Kink position

Claims (9)

1. Projektilbeschleunigungsvorrichtung einer Webmaschine mit Antriebswelle, Beschleunigungswelle, Schlaghebel, Oelbremse und einem Kniegelenk an einem Rollenhebel, gekennzeichnet durch ein Koppelgetriebe (8) mit einem weiteren Gelenk (16) zwischen Rollenhebel (32) und schlaghebel (4), welches zwei Knicklagen auf­weist, wobei die erste Knicklage (8a) der Abschussposi­tion (4a) und die gegenüberliegende zweite Knicklage (8c) der Endposition (4c) des Schlaghebels entspricht, und durch ein von der Antriebswelle (12) angetriebenes Spannorgan (13), welches das Koppelgetriebe aus der zweiten Knicklage über seine Strecklage (8b) hinaus in Richtung erste Knicklage (8c) spannt.1. projectile acceleration device of a weaving machine with drive shaft, acceleration shaft, impact lever, oil brake and a knee joint on a roller lever, characterized by a coupling gear (8) with a further joint (16) between roller lever (32) and impact lever (4), which has two buckling positions, wherein the first kink position (8a) corresponds to the firing position (4a) and the opposite second kink position (8c) corresponds to the end position (4c) of the striking lever, and by a tensioning element (13) driven by the drive shaft (12) which removes the coupling gear from the second Kink position over its extended position (8b) in the direction of the first kink position (8c). 2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Oelbremse (17) mit dem Schlaghebel (4) gekop­pelt ist.2. Device according to claim 1, characterized in that the oil brake (17) is coupled to the impact lever (4). 3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Beschleunigungsendlage des Schlaghebels im wesentlichen der Strecklage (8b) des Koppelgetriebes entspricht.3. Device according to claim 1, characterized in that the acceleration end position of the striking lever essentially corresponds to the extended position (8b) of the coupling gear. 4. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Rollenhebel (32) zwei Rollen (1, 31) aufweist, welche beide auf einer Kurvenscheibe (34) der Antriebs­welle (12) ablaufen.4. The device according to claim 1, characterized in that the roller lever (32) has two rollers (1, 31), both of which run on a cam (34) of the drive shaft (12). 5. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Spannorgan (13) eine Exzenterschwinge (20) auf der Antriebswelle (12) und einen Spannlappen (9) auf der Beschleunigungswelle (10) aufweist.5. The device according to claim 1, characterized in that the clamping member (13) has an eccentric rocker (20) the drive shaft (12) and a tensioning tab (9) on the acceleration shaft (10). 6. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die Exzenterschwinge (20) über einen Bolzen (21) mit einer Schwenklasche (22) auf der Beschleunigungs­welle (10) verbunden ist und dass der Spannlappen (9) eine Lagernut (24) zur Abstützung des Bolzens (21) auf­weist.6. The device according to claim 5, characterized in that the eccentric rocker (20) via a bolt (21) with a swivel bracket (22) on the acceleration shaft (10) is connected and that the clamping tab (9) has a bearing groove (24) for support of the bolt (21). 7. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Spannlappen (9) eine bogenförmige Führungsnut (36) zur Aufnahme eines Bolzens (37) der Exzenter­schwinge (20) aufweist.7. The device according to claim 5, characterized in that the clamping tab (9) has an arcuate guide groove (36) for receiving a bolt (37) of the eccentric rocker (20). 8. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die Exzenterschwinge (20) eine bogenförmige Gabel­führung (38) zur Aufnahme eines Bolzens (39) des Spann­lappens (9) aufweist.8. The device according to claim 5, characterized in that the eccentric rocker (20) has an arcuate fork guide (38) for receiving a bolt (39) of the clamping tab (9). 9. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Schlaghebel (4) ein Endstück (5) aufweist, dass beim Abschuss direkt auf die Stossfläche des Projektils (6) einwirkt.9. The device according to claim 1, characterized in that the impact lever (4) has an end piece (5) that acts directly on the impact surface of the projectile (6) when fired.
EP90810657A 1989-09-15 1990-08-30 Shuttle picking mechanism for a loom Expired - Lifetime EP0418195B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3364/89 1989-09-15
CH336489 1989-09-15

Publications (2)

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EP0418195A1 true EP0418195A1 (en) 1991-03-20
EP0418195B1 EP0418195B1 (en) 1993-09-29

Family

ID=4254377

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90810657A Expired - Lifetime EP0418195B1 (en) 1989-09-15 1990-08-30 Shuttle picking mechanism for a loom

Country Status (5)

Country Link
US (1) US5063972A (en)
EP (1) EP0418195B1 (en)
CN (1) CN1022938C (en)
DE (1) DE59002911D1 (en)
RU (1) RU1814671C (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0908547A1 (en) * 1997-10-07 1999-04-14 Sulzer Rüti Ag Weft inserting device in a loom and loom with such a device
EP1777329A1 (en) * 2005-10-01 2007-04-25 Markus Farner Dummy shuttle loom

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59206965D1 (en) * 1992-12-10 1996-09-26 Rueti Ag Maschf Accelerator lever, especially for projectile weaving machines
CN1071162C (en) * 1999-01-18 2001-09-19 华中理工大学 Metal type heat-insulation coating
CN1071161C (en) * 1999-01-18 2001-09-19 华中理工大学 Metal-type top heat-conductive coating

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Publication number Priority date Publication date Assignee Title
DE678468C (en) * 1937-01-31 1939-07-15 Tefag Textil Finanz A G Shooter striking device for looms
CH313155A (en) * 1952-11-03 1956-03-31 Sulzer Ag Shuttle hitting device on a weaving machine, in which the hitting force is supplied by an energy storage device
CH332768A (en) * 1953-09-03 1958-09-30 Sulzer Ag Shooting device on a weaving machine, in which a torsion bar spring drives the hammer
CH636656A5 (en) * 1979-06-14 1983-06-15 Sulzer Ag BRAKING DEVICE FOR SUDDENLY MOVING PARTS OF A LOOPPING MACHINE.

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2813549A (en) * 1952-11-03 1957-11-19 Sulzer Ag Shuttle picking mechanism for weaving machines
US4223703A (en) * 1978-08-17 1980-09-23 Sulzer Brothers Limited Picking mechanism for a shuttle of a weaving machine
DE58905202D1 (en) * 1988-03-14 1993-09-16 Sulzer Ag PROJECTILE WEAVING MACHINE AND PROJECTILE FOR THE WEAVING MACHINE.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE678468C (en) * 1937-01-31 1939-07-15 Tefag Textil Finanz A G Shooter striking device for looms
CH313155A (en) * 1952-11-03 1956-03-31 Sulzer Ag Shuttle hitting device on a weaving machine, in which the hitting force is supplied by an energy storage device
CH332768A (en) * 1953-09-03 1958-09-30 Sulzer Ag Shooting device on a weaving machine, in which a torsion bar spring drives the hammer
CH636656A5 (en) * 1979-06-14 1983-06-15 Sulzer Ag BRAKING DEVICE FOR SUDDENLY MOVING PARTS OF A LOOPPING MACHINE.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0908547A1 (en) * 1997-10-07 1999-04-14 Sulzer Rüti Ag Weft inserting device in a loom and loom with such a device
EP1777329A1 (en) * 2005-10-01 2007-04-25 Markus Farner Dummy shuttle loom

Also Published As

Publication number Publication date
US5063972A (en) 1991-11-12
CN1022938C (en) 1993-12-01
CN1050234A (en) 1991-03-27
EP0418195B1 (en) 1993-09-29
RU1814671C (en) 1993-05-07
DE59002911D1 (en) 1993-11-04

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