EP1700939B1 - Système d'entraînement de lames pour métiers à tisser - Google Patents

Système d'entraînement de lames pour métiers à tisser Download PDF

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Publication number
EP1700939B1
EP1700939B1 EP20060002238 EP06002238A EP1700939B1 EP 1700939 B1 EP1700939 B1 EP 1700939B1 EP 20060002238 EP20060002238 EP 20060002238 EP 06002238 A EP06002238 A EP 06002238A EP 1700939 B1 EP1700939 B1 EP 1700939B1
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EP
European Patent Office
Prior art keywords
heald frame
movement
pawl
drive
drive according
Prior art date
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EP20060002238
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German (de)
English (en)
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EP1700939A2 (fr
EP1700939A3 (fr
Inventor
Joannes Dr. Bruske
Bernhard Münster
Armin FÄLLER
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Groz Beckert KG
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Groz Beckert KG
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Publication of EP1700939A3 publication Critical patent/EP1700939A3/fr
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies

Definitions

  • the invention relates to a shaft drive for at least one heald of a loom.
  • a plurality of healds are generally provided on looms, each having a plurality of mutually parallel strands are passed through the thread eyes the warp threads.
  • the healds are moved up and down very quickly.
  • Serve this shaft drives which are referred to as dobby or eccentric machines.
  • Eccentric machines generate from the rotating movement of a drive shaft up and Movement of the heald frames, whereby high weaving speeds can be achieved.
  • Such eccentric machines are inflexible. The creation of patterns or different bindings is limited. Therefore, shaft drives are widely used, in which a pawl clutch is provided between a drive shaft and the eccentric for generating the shaft movement.
  • Such a dobby is for example from the DE 697 02 039 T2 known.
  • the latching mechanism arranged between the eccentric and the driving shaft is here switched on for each shaft movement, ie for an upward movement of the shaft or for a downward movement of the shaft in each case for half a shaft rotation.
  • Such dobby machines are very flexible. However, it is necessary for the function of the pawl mechanism of such a dobby, that the entire transmission, including all input and output elements and the shaft, during the switching phase stand still. Dobby according to DE 697 02 039 switch in the rest.
  • At least one drive pulley that performs a predetermined, for example, uniform rotational movement belongs to the clutch device. It may be provided a second drive pulley, which is a rotary oscillation movement performs, which is briefly or completely synchronous to the rotational movement of the first drive pulley in selected angular ranges. These short phases of synchronous movement between the two drive pulleys can be used to switch the drive connection to the driven pulley from the first pulley to the second or vice versa. Serve one or more pawls.
  • the pawl is engaged and disengaged by an actuator.
  • This is e.g. a slider which is adjustable between two positions and past which the pawl, whereby it is actuated according to its position.
  • the actuating device may also be formed by at least one, but preferably two, shifters, past which the pawl passes and thereby actuates, i. e.g. is engaged.
  • For temporary connection of the actuator with the pawl is preferably a link guide. This allows the moving, e.g. with the driven pulley rotating pawl a free movement in the circumferential direction and transmits the directed in the radial direction switching movement to the pawl.
  • the slide can be actuated by a rotary driven cam, with which it is in contact with a cam follower.
  • the shift levers can be operated directly electrically or pneumatically. However, it is preferred to drive them via a control clutch from a cam drive ago.
  • the control clutch can then be operated with very low power, on the other hand, sufficiently large forces are generated to move the shifter.
  • the clutch can eg via stationary or movable Control magnets are controlled and formed by a swing-driven selection finger. This results in a precisely responsive and with low energy controllable control arrangement for the clutch assembly.
  • the pawl can be biased by a biasing means to its on or Auskuppelposition out and, if desired, be moved by the actuating device in each case in the off or Einkuppelposition.
  • a particularly responsive and stable latching mechanism is obtained when the biasing means is a bi-stable device having two stable switching positions. Between these positions, a dead center can be formed. The actuator then has to move the pawl to toggle only over the dead center, after which the pawl switches. This can be ensured even at very high operating speeds, in spite of the impacts acting on the entire mechanism, the resulting vibrations and the centrifugal forces that occur.
  • the pawl may be constructed in the manner of a rocker and have two switching lugs, one of which is assigned to a first drive pulley and the second of a second drive pulley.
  • the pawl can serve to selectively produce the drive connection between the first drive pulley and the driven pulley or the second drive pulley and the driven pulley.
  • the pawl can be designed as a rigid rocker, the pivot axis is connected to the driven pulley.
  • the rocker may be formed in two parts with a spring-mounted arm.
  • an embodiment of the invention is considered to be particularly advantageous, in which two mutually separate pawls are provided.
  • a pawl of the first drive pulley and the second pawl of the second drive pulley be assigned.
  • the pawls are then preferably arranged on diametrically opposite sides of the driven pulley. They may be resiliently biased toward their engaged positions, or may also be connected to a bistable biasing means as described above and with the advantages described above.
  • the embodiment with two pawls has the advantage that the switching movements of a respective pawl can each be determined independently of the switching movement of the other pawl. Again, this is advantageous in terms of reliably achieving high operating and switching speeds.
  • the shaft When the driven pulley is coupled to the first drive pulley, the shaft makes its reciprocating motion.
  • the driven pulley is attached to the second, only by a limited angle back and forth Coupled drive pulley, the shaft is in its resting phase in which he performs only a slight oscillation movement about its upper and lower reversal point.
  • this oscillation movement it can be engaged during the short synchronizing phases, with the acceleration forces occurring on the shaft and the gear elements involved and the resulting loads hardly being greater than during uninterrupted operation of the shaft. At least no noticeable sudden changes in the acceleration forces occur.
  • the oscillating movement of the second drive pulley can be generated by a cam drive or by electrical, hydraulic or pneumatic drives.
  • FIG. 1 a heald 1 with associated shaft drive 2 is illustrated.
  • the heald 1 is formed by a provided with strands 95 frame, which is in operation as indicated by an arrow 3 moves up and down.
  • a linkage 4 which attaches to the weaving shank 1 at two or more points 5, 6 and forms the output of the shaft drive 2.
  • To the linkage 4 include angle lever 7, 8, which are connected on the one hand with the weaving shank 1 and on the other hand directly or indirectly with the pull and push rod 9.
  • This is connected to the shaft drive 2, the output side of a rocker 11, which follows a pivoting movement has.
  • the shaft drive 2 generates from the uniform rotational movement of an input shaft 12 in FIG. 1 by an arrow 13 illustrated reciprocating motion, wherein this movement on the heald 1 as a largely harmonic oscillatory motion in appearance.
  • the curve I describes in FIG. 2 the shaft movement of the heald shaft 1 with its X-coordinate (direction of the arrow 3 in FIG. 1 ) over time t. For example, it follows a sine function. As soon as the heald 1 has reached its upper reversal position TO, in which it could, as seen by weaving technology, persist, the curve I changes into a vibration with reduced amplitude and acceleration (curve branch II). The heald 1 thus performs oscillation in a turning point area BTO instead of resting. Near the top of the vertex, the shaft movement changes from curve I to curve II ( FIG. 2 ).
  • FIG. 3 illustrates that the reverse point oscillation in the rest phase R can be maintained over several cycles.
  • a plurality of heald frames 1, 1a, 1b can be arranged at a small distance one behind the other, which are driven by the common shaft drive 2 and thus by the common input shaft 12.
  • This is connected to a rotary drive device 14, which is formed by a servo motor, another electric motor or an output shaft of a central drive device, which drives other organs of the loom.
  • the said movements of the heald shaft 1 in the movement phases B and the resting phases R are determined by the mechanical shaft drive 2 according to FIG Figure 5 to 7 generated.
  • the shaft drive 2 comprises for each weaving shank 1, 1a, 1b respectively a gear arrangement 15 (15a, 15b) for converting the rotational movement of the input shaft 12 into the reciprocating movement of the respective output side lever 11 (11a, 11b) in the form of a rocker, and a clutch assembly 16 (16a, 16b) via which the transmission assembly 15 is to be selectively connected to or disconnected from the input shaft 12.
  • the clutch assembly 16 and the gear assembly 15 are in the Figures 5 and 7 schematized illustrated.
  • the coupling arrangement serves to control the movement of the heald and is in this respect the mechanically designed here control device C.
  • the structure ( FIG. 7 ) is as follows:
  • the gear assembly 15 is formed by an eccentric 17 which drives the lever 11 via a connecting rod 18 swinging.
  • the gear assembly 15 thus serves to convert the rotational movement of the eccentric 17 in a reciprocating motion.
  • the clutch assembly 16 includes a first pulley 21 and a second pulley 22 (both referred to as "pulleys" because they form the inputs of the clutch assembly 16).
  • Both discs 21, 22 preferably have the same diameter. However, they can also have different diameters and are designed to improve clarity FIG. 7 also illustrated with different diameters.
  • the first disc 21 is connected to the input shaft 12 and via this to the rotary drive device 14. The disc 21 thus rotates uniformly at a substantially constant speed. This symbolizes in FIG. 7 an arrow 23.
  • the second disc 22 is rotatably supported about the same axis of rotation 24 as the first disc 21. However, it is not constantly rotating but reciprocating, ie driven rotationally oscillating or mospendelnd. This is illustrated by arrow 25.
  • To the clutch assembly 16 also includes a switching member 26 in the form of a pawl 27 which is pivotally mounted about a pin 28 on the eccentric 17 (which is also referred to as "driven pulley" because it forms the output of the clutch assembly).
  • the pawl has a first switching lug 29 and a second switching lug 30, wherein the switching lugs 29, 30 are arranged on different sides of the pin 28.
  • the switching lug 29 are assigned to each other by 180 ° opposite recesses 31, 32 in the disc 21.
  • the switching lug 30 are assigned to each other by 180 ° opposite recesses 33, 34 in the disc 22.
  • the pawl 27 is eg according to FIG. 6 or 8th designed as a rigid rocker. The movements of the switching lug 29, 30 are then rigidly coupled to each other.
  • the switching nose 29 carrying arm 27 a and the switching nose 30 supporting arm 27 b can rotate independently of each other about the pin 28.
  • the arm 27b may also be provided with an attachment for the arm 27a.
  • a spring can bias the arm 27a against this projection.
  • the pawl 27 are two levers 36, 37 assigned ( FIG. 5 ), each having a for actuating the control roller 35 serving cylindrically curved shift gates 38, 39.
  • the shift gates 38, 39 are approximately concentric to the rotation axis 24 and are each formed by approximately circular arc-shaped grooves (see FIG. 6 ). They have arcuate groove flanks, between which the control roller 35 runs.
  • the shift levers 36, 37 can according to FIG. 5 be pivoted radially inwardly and outwardly about pivot axes 41, 42.
  • the inner pivot position is chosen so that the switching lug 29 of the pawl 27 according to FIG. 8 is lifted out of its respective latching recess 31, 32 when the control roller 35 runs along the outer groove flank of the shift gate 38, 39. Accordingly, the switching nose 30 is engaged in the recess 33, 34.
  • the control roller runs on the inner groove flank of the control link 38, 39.
  • a cam drive 43 ( FIG. 5 ), which is connected to the input shaft 12 and, for example, has two cams.
  • This is associated with a trained as an angle lever cam follower lever 44 which actuates the shift lever 36, 37 via a selection finger 45 which serves as a control clutch 46.
  • the selection finger 45 is vertically oscillated by the cam follower lever 44 and thus actuates depending on the pivot position either the free end 47 of the shift lever 36 or the free end 48 of the shift lever 37 by the respective end 47, 48 for the time of the deflection of the cam follower lever 44 is pressed down.
  • stops 51, 52 are arranged on both sides thereof, which limit the selection finger 45 in its position.
  • the selection finger 45 is attracted and held against the spring force of the compression spring 52B against the stopper 52 by a control magnet 52A, when released for control. Otherwise a compression spring 52 B presses the selection finger 45 against the stop 51 and holds it in position.
  • While the disc 21 is constantly driven to rotate, the disc 22, as mentioned, driven rotationally oscillating or nadopendelnd.
  • the purpose of a connected to the disc 22 cam follower 53 ( FIG. 5 ), for example in the form of a roller, which is mounted at the end of a rigidly connected to the disc 22 lever.
  • the cam follower 53 is actuated by a cam 54, for example, rotates at twice the speed of the input shaft 12 and has only a single survey.
  • the disc 22 receives twice per revolution of the input shaft 12 a reciprocating motion.
  • the shaft drive 2 described so far operates as follows:
  • the eccentric 17 is to rotate constantly.
  • the pawl 27 must constantly connect the disc 21 with the eccentric 17.
  • each of the shift lever 36 and the shift lever 37 must always escape to the outside when the pawl 27 passes as a result of rotation of the disc 21 to the respective shift lever.
  • the control solenoid 52A is energized so that the select finger 45 pushes the end 47 downward as the pawl 27 passes the shift lever 36 and the select finger 45 pushes the end 48 downward as the pawl 27 passes the shift lever 37.
  • the buttons 38, 39 of the shift levers 36, 37 extend over an angular range, which serves as a switching range can be viewed.
  • the cam follower 53 forms, together with the cam 54, a pendulum drive 55. This imparts to the disc 22 to a rotary pendulum motion, which is always synchronous with the movement of the disc 21 when the pawl 27 passes through the switching areas.
  • These movement phases are characterized in that the cams of the cam drive 43 urge the end of the cam follower lever 44 to the outside.
  • the clutch assembly 16 can be switched by the respective shift lever 36 or 37 does not escape to the outside.
  • the switching lug 29 is pushed out of the latching recess 31 and the switching lug 30 is engaged in the latching recess 33.
  • the relevant shift lever 36 or 37 then remains activated by the relevant shift lever 36, 37, for example by springs 56, 57 (FIG. FIG. 5 ) is held in its inner position and is not moved outwardly by the selection finger 45.
  • the eccentric 17 performs only a reciprocating motion in this state, because he is bound to the disc 22.
  • the movement oscillating back and forth by a few degrees, for example 10 °, causes only a slight upward and downward movement of the same in the upper or lower reversal point of the heald, at most only a few millimeters. This does not disturb the shedding and weaving process. However, it allows a synchronous reconnection, by only the relevant shift lever 36, 37, in which the pawl 27 is, is pivoted outwardly.
  • the cam drive 43 causes this at the moment of synchronization of the two discs 21, 22, so that a soft shock-free restart of the eccentric 17 takes place.
  • FIG. 8 illustrates an exemplary embodiment.
  • a push rod 60 which is supported on an abutment 61. This is rotatably and fixedly connected to the bearing of the pin 28 and thus for example attached to the eccentric 17.
  • a spring 62 On the push rod 60 sits a spring 62, for example a compression spring which is supported at one end to the abutment 61 and at its other end to a provided on the push rod 60 disc 63.
  • the push rod 60 is connected to the pawl 27 at a hinge 64.
  • the abutment 61, the joint 64 and the pin 28 are arranged so that the switching rocker 27 and the push rod 60 when passing through a pivoting range of the rocker switch 27 through an extended position. This forms a dead center.
  • On both sides of the pawl has stable Einkuppellagen on.
  • the switching nose 29 is engaged in the recess 31 while in the other stable position, the switching nose 30 is engaged in the recess 33.
  • the pawl 27 securely retains the coupling position given to it by the control roller 35.
  • the pawl 27 may, as in FIG. 8 and 9 illustrated, rigid or, according to FIG. 7 be formed in two parts. In both cases, it is switched by the switching levers 36, 37 in the respective stable switching positions, which dictates the bistable biasing means 35a.
  • FIG. 10 illustrates another modification.
  • the illustrated there shaft drive uses pawls 27a, 27b, which, similar to the above-described pawl 27, each with a pin 28a, 28b are pivotally mounted on the eccentric 17. Both pawls 27a, 27b wear each only one switching lug 29, 30.
  • the peel pawls 27a, 27b are by springs, such as the FIG. 11 apparent wrap spring 35b biased toward their latching position.
  • the pawl 27a is engaged with the disk 21.
  • the pawl 27b is disengaged from the disc 22.
  • To disengage the pawls 27a, 27b serve the shift lever 36, 37 and their preferably cylindrically curved buttons 38a, 39a, the shift gates 38, 39 of the switching device according to FIG. 6 replace.
  • the embodiment with separate pawls 27a, 27b allows the engagement of the respective desired pawl 27a or 27b, regardless of how quickly the other pawl reaches the disengaging position.
  • the pawls 27a, 27b can be actuated via shift gates 38, 39.
  • the pawls 27a, 27b according to FIG. 11 as well as pawls according to FIG. 13 Find application.
  • the pawls 27a, 27b according to FIG. 13 are each provided with a bistable biasing means 35a, as already associated with FIG. 8 has been described. The too FIG. 8 Applicable description applies accordingly.
  • the pawls 27a, 27b can be actuated both by the switching levers 36, 37 and by a slide 65 on which the two links 38, 39 are formed.
  • the slider 65 for example, slidably mounted with respect to the axis of rotation 24 in a selected radial direction be and how FIG. 14 illustrated by a control cam 66 are actuated.
  • the slider 65 guarantees a synchronous switching of the two pawls 27a, 27b, so that even at high switching speeds faulty circuits are avoided.
  • the slider 65 may be associated with a holding magnet 67 in order to hold the slider 65 in an end position.
  • a novel shaft gearbox allows the switching on and off of individual heald frames, even at high working speeds.
  • pawls are provided which couple an eccentric with permanently rotating and / or reciprocating sheaves. Measures to improve the controllability of such a clutch assembly are each for themselves control of the pawls on shift gates, assignment of bistable biasing means to the pawls and / or distribution of the switching function on individual pawls 27a, 27b, each of which different discs 21, 22 are assigned individually.
  • one of the two discs performs a continuous rotational movement and the other disc only a pendulum movement, which dictates the shaft movement during the sheep rest phases.

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

Claims (21)

  1. Système d'entraînement de lame pour au moins une lame (1) d'un métier à tisser,
    comprenant au moins un mécanisme de sortie (4) qui est associé à la lame (1) et est relié à celle-ci afin de la maintenir dans des phases de repos (R) et de lui communiquer un mouvement pendant des phases de mouvement (B),
    comprenant un dispositif de commande (C,) pour contrôler la vitesse momentanée du mécanisme de sortie (4) et donc de la lame (1),
    comprenant un dispositif d'accouplement (16) qui fait partie du système d'entraînement (2) et est placé entre un dispositif d'entraînement (14) et un dispositif de transmission (15) destiné à transmettre le mouvement d'entraînement à la lame (1),
    le dispositif d'accouplement (16) présentant un premier disque d'entraînement (21), relié au dispositif d'entraînement (14), et un deuxième disque d'entraînement (22) ainsi qu'un disque de sortie (17) qui est relié, par l'intermédiaire d'au moins un cliquet de manoeuvre (27), au choix au premier ou au deuxième disque d'entraînement (21, 22),
    le cliquet de manoeuvre (27) étant maintenu par un dispositif de précontrainte (35a) bistable, avec possibilité de déplacement en va-et-vient entre deux positions stables.
  2. Système d'entraînement de lame pour au moins une lame (1) d'un métier à tisser,
    comprenant au moins un mécanisme de sortie (4) qui est associé à la lame (1) et est relié à celle-ci afin de la maintenir dans des phases de repos (R) et de lui communiquer un mouvement pendant des phases de mouvement (B),
    comprenant un dispositif de commande (C,) pour contrôler la vitesse momentanée du mécanisme de sortie (4) et donc de la lame (1),
    comprenant un dispositif d'accouplement (16) qui fait partie du système d'entraînement (2) et est placé entre un dispositif d'entraînement (14) et un dispositif de transmission (15) destiné à transmettre le mouvement d'entraînement à la lame (1),
    le dispositif d'accouplement (16) présentant un premier disque d'entraînement (21), relié au dispositif d'entraînement (14), et un deuxième disque d'entraînement (22) ainsi qu'un disque de sortie (17) qui peut être relié, par l'intermédiaire d'un premier cliquet de manoeuvre (27) ou d'un deuxième cliquet de manoeuvre (27a) disposé à distance du premier, au choix au premier ou au deuxième disque d'entraînement (21, 22).
  3. Système d'entraînement de lame selon la revendication 2, caractérisé par le fait que le cliquet de manoeuvre (27) est maintenu sous précontrainte en direction d'une position stable, à l'aide d'un dispositif de précontrainte (35a).
  4. Système d'entraînement de lame selon la revendication 2, caractérisé par le fait que le cliquet de manoeuvre (27) est maintenu par un dispositif de précontrainte (35a) bistable, avec possibilité de déplacement en va-et-vient entre deux positions stables.
  5. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le cliquet de manoeuvre (27) peut être déplacé en va-et-vient entre une position d'accouplement et une position de désaccouplement par un élément d'actionnement (36, 65) doté d'un guide-coulisse (38).
  6. Système d'entraînement de lame selon la revendication 3, caractérisé par le fait que le guide-coulisse (38) entre en prise avec le cliquet de manoeuvre (27) uniquement dans des positions angulaires sélectionnées du dispositif d'entraînement (14).
  7. Système d'entraînement de lame selon la revendication 5, caractérisé par le fait que l'élément d'actionnement (65) est un poussoir d'actionnement.
  8. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le dispositif d'entraînement (14) communique au premier disque d'entraînement (21) un mouvement avec un sens constant, un mouvement avec des sens alternés étant imprimé au deuxième disque d'entraînement (22).
  9. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le mécanisme de sortie (4) exécute un mouvement prédéterminé, également pendant les phases de repos (R).
  10. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le mouvement prédéterminé des phases de repos R est défini par le dispositif de commande (C,).
  11. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que, au début d'une phase de repos (R), le mécanisme de sortie (4) présente une accélération qui correspond à son accélération à la fin de la phase de mouvement (B) précédente.
  12. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que, au début d'une phase de mouvement (B), le mécanisme de sortie (4) présente une accélération qui correspond à son accélération à la fin de la phase de repos (R) précédente.
  13. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que pendant les phases de repos (R), le mécanisme de sortie (4) exécute un mouvement oscillatoire.
  14. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le premier disque d'entraînement (21) et le deuxième disque d'entraînement (22) sont entraînés au moins temporairement de façon synchrone, et par le fait que la manoeuvre du dispositif d'accouplement (16) est effectuée durant la phase synchrone.
  15. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le deuxième disque d'entraînement (22) est relié à un moyen d'entraînement pendulaire (55) qui communique un mouvement oscillatoire au deuxième disque d'entraînement (22).
  16. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le cliquet de manoeuvre (27) doit être relié en permanence à l'excentrique (17) et au choix au premier ou au deuxième disque d'entraînement (21, 22).
  17. Système d'entraînement de lame selon la revendication 15, caractérisé par le fait que dans des positions de manoeuvre prédéterminées par l'élément d'actionnement (36, 37), le mouvement de rotation oscillatoire du deuxième disque d'entraînement (22) est synchrone avec le mouvement de rotation du premier élément d'entrée (21).
  18. Système d'entraînement de lame selon la revendication 5, caractérisé par le fait que l'élément d'actionnement (36, 37) est constitué d'au moins un levier de manoeuvre (36, 37) qui est associé au cliquet de manoeuvre (27), afin d'accoupler ou de désaccoupler celui-ci dans au moins une des positions de manoeuvre prédéterminées.
  19. Système d'entraînement de lame selon la revendication 1 ou 2, caractérisé par le fait que le cliquet de manoeuvre (27) est relié au disque de sortie (17) et tourne avec celui-ci.
  20. Système d'entraînement de lame selon la revendication 19, caractérisé par le fait que l'élément d'actionnement (36, 37) est relié par un moyen d'accouplement de commande (46) à un moyen d'entraînement à cames (43).
  21. Système d'entraînement de lame selon la revendication 20, caractérisé par le fait que le moyen d'accouplement de commande (46) présente un doigt de sélection (45) qui est monté de manière à pouvoir être déplacé entre au moins deux positions, afin d'activer et de désactiver l'actionnement du levier de manoeuvre (36, 37) via le moyen d'entraînement à cames (43), et par le fait que le doigt de sélection (45) peut être déplacé par une combinaison formée d'un aimant de commande 52A et d'un ressort de pression 52B.
EP20060002238 2005-03-07 2006-02-03 Système d'entraînement de lames pour métiers à tisser Active EP1700939B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510010807 DE102005010807B3 (de) 2005-03-07 2005-03-07 Schaftantrieb für Webmaschinenschäfte

Publications (3)

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EP1700939A2 EP1700939A2 (fr) 2006-09-13
EP1700939A3 EP1700939A3 (fr) 2008-10-15
EP1700939B1 true EP1700939B1 (fr) 2010-06-16

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JP (1) JP4248554B2 (fr)
CN (1) CN1834318B (fr)
DE (2) DE102005010807B3 (fr)

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DE69126569T2 (de) * 1990-07-20 1997-11-13 Brevtex Sa Steuervorrichtung zum Programmieren von Rotationsschaftmaschinen für Webmaschinen
IT1260291B (it) * 1992-12-18 1996-04-03 Lucio Burigana Ratiera rotativa
JPH07268742A (ja) * 1994-03-28 1995-10-17 Toyota Autom Loom Works Ltd 織機における開口方法及び装置
FR2757883B1 (fr) * 1996-12-31 1999-02-19 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
FR2757882B1 (fr) * 1996-12-31 1999-02-19 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
FR2842538B1 (fr) * 2002-07-16 2004-10-29 Staubli Sa Ets Ratiere rotative pour metier a tisser, et metier a tisser equipe d'une telle ratiere
DE10343377B3 (de) * 2003-09-17 2005-04-28 Groz Beckert Kg Schaftantrieb für Webmaschinenschäfte

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CN1834318B (zh) 2010-12-08
EP1700939A3 (fr) 2008-10-15
CN1834318A (zh) 2006-09-20
JP4248554B2 (ja) 2009-04-02
JP2006249649A (ja) 2006-09-21
DE502006007207D1 (de) 2010-07-29
DE102005010807B3 (de) 2006-04-06

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