EP1845181B1 - Rotationsschaftmaschine, eine solche Schaftmaschine umfassende Webmaschine und Verfahren zur Steuerung einer solchen Schaftmaschine - Google Patents

Rotationsschaftmaschine, eine solche Schaftmaschine umfassende Webmaschine und Verfahren zur Steuerung einer solchen Schaftmaschine Download PDF

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Publication number
EP1845181B1
EP1845181B1 EP20070356044 EP07356044A EP1845181B1 EP 1845181 B1 EP1845181 B1 EP 1845181B1 EP 20070356044 EP20070356044 EP 20070356044 EP 07356044 A EP07356044 A EP 07356044A EP 1845181 B1 EP1845181 B1 EP 1845181B1
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Prior art keywords
bolt
spring
dobby
driving member
force
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EP20070356044
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English (en)
French (fr)
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EP1845181A1 (de
Inventor
Jean Pierre Pages
Robert Nocenti
Willy Galinaitis
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Staubli Faverges SCA
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Staubli Faverges SCA
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D03C1/14—Features common to dobbies of different types
    • D03C1/16—Arrangements of dobby in relation to loom
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D03C1/14—Features common to dobbies of different types
    • 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
    • Y10T292/00—Closure fasteners
    • Y10T292/08—Bolts
    • Y10T292/1043—Swinging
    • Y10T292/1075—Operating means
    • Y10T292/1082—Motor

Definitions

  • the invention relates to a rotating dobby for a loom, and to a loom equipped with such a dobby.
  • the invention also relates to a subassembly belonging to such a dobby and a method of controlling such a dobby.
  • a lock transmits the driving force of the drive blade, while the other undergoes the receiving force which corresponds to the energy returned by the blade to the main shaft.
  • the motor lock works during the driving phase of the movement of the main shaft, that is to say when the acceleration and the speed of the connected frame are of the same sign.
  • the receiver lock is biased during the reception phase of the movement of the main shaft, that is to say when the acceleration and speed of the frame are of different signs.
  • a connected frame moves back and forth in a full rotation of the main shaft. It is possible to decouple it from the movement of the main shaft when it reaches a selection range, around its two extreme positions. These selection ranges correspond to a transfer of effort between the latches working respectively during the driving and receiving phases.
  • the latches When a blade is moving, the latches are engaged in a notch of the drive disk and in support against a corresponding surface of this disc.
  • the selection device When it is appropriate to stop a blade, the selection device must therefore actuate the locks to release them from this notch, while the latch that works during the receiving phase is heavily loaded.
  • the arm must therefore act powerfully and quickly on the lock, which requires sizing the means of action on the locks taking into account the intense efforts to provide.
  • the control elements of the locks have a high inertia, which can limit the operating speeds of known dobbies.
  • This dobby is characterized in that the first elastic load means act directly on the first lock and indirectly on the second lock, while the control means are able to move the first lock against the action of the first means. resilient load, while the second latch remains in engagement configuration of its bearing surface with the second surface of the drive member.
  • the invention it is possible to actuate directly, thanks to the control means, only the first lock by which the motor force of the main shaft is transmitted to the actuating element and the heald frame, while the second latch, which is under load can remain in place, while the dobby is in a receiving phase of the movement of the main shaft, until it goes into the driving phase.
  • the second latch can then be easily disengaged from the corresponding surface of the driving element.
  • the invention also relates to a loom equipped with a dobby as described above. Such a craft can operate at higher speeds than those of the state of the art.
  • the invention relates to a subassembly, sometimes referred to as "dobby blade", which belongs to a dobby as mentioned above and which comprises an eccentric forming an actuating element, a connecting rod mounted on this eccentric and a pivoting arm for connecting the connecting rod to a heald frame.
  • a subassembly can be mounted, as a functional unit provided with the aforementioned locks, as a replacement member in a dobby.
  • the rotational disconnection of the driving element and the actuating element can be initiated while the main shaft of the dobby and the driving element are still in motion at the end of an angular stroke of 180 °.
  • the release of the second lock takes place automatically under the effect of the auxiliary means.
  • the dobby R represented at figure 1 comprises a main shaft 1 animated with an intermittent rotational movement with stopping every half-turn.
  • This shaft 1 receives a series of rolling 2 in number equal to that of the healds frames or blades 3 of the trade M.
  • On each bearing 2 is mounted crazy an eccentric 4 on which is mounted crazy the opening of an oscillating rod 5 around a second bearing 2 '.
  • the free end 51 of the connecting rod 5 is coupled to a pivoting arm 6 which ensures, thanks to a rod connection 61, the vertical displacement of a heald frame 3 shown very schematically for the clarity of the drawing, according to a movement of vertical oscillations represented by the double arrow F 1 to the figure 1 .
  • X 1 the geometric axis of rotation of the shaft 1.
  • the shaft 1 is integral in rotation with a drive disc 8 whose central opening is substantially circular and provided with two teeth 81 engaged in longitudinal grooves of corresponding shapes 1a formed at the periphery of the shaft 1.
  • the peripheral edge 82 of the disk 8 is provided with four notches 83 which define four shoulders 84A, 84B, 84C, 84D arranged in the thickness or slice of the disk 8.
  • Two latches 10 and 11 are respectively hinged around two shafts 12A and 12B fixed on the eccentric 4 and each defining a geometric axis of rotation X 10 , X 11 of the latches 10 and 11.
  • the X axes 10 and X 11 are parallel to the X axis 1 .
  • the latch 10 comprises a first arm 101 which extends generally in a radial direction relative to the axis X 10 and the end 102 can be engaged in two of the notches 83, so that its end surface 103 can then bear against one of the shoulders 84A and 84C.
  • the latch 10 also comprises a second radial arm 104 whose end 105 is engaged in a fork formed at the end 131 of a pusher or slider 13 mounted on the eccentric 4 being movable in translation in both directions according to a direction D 1 radial to the axis X 1 , as represented by the double arrow F 2 .
  • the second latch 11 has the same geometry as the first latch 10 and comprises two arms 111 and 114 which extend radially with respect to the X axis 11 and whose respective ends 112 and 115 are intended to cooperate respectively with the shoulders 84B and 84D and with the pusher 13.
  • the end surface 113 of the arm 111 is intended to selectively bear against the shoulders 84B and 84D.
  • the receiving force F 4 corresponding to the braking energy restored by the blade, in particular at the end of a 180 ° rotation of the shaft 1 about the axis X 1 , is transmitted to the eccentric 4 by the support of the surface 113 on the shoulder 84B. It is the same, respectively at the interfaces between the surfaces 103 and 84C, on the one hand, 113 and 84D, on the other hand, when the locks are engaged in the other two notches 83.
  • the pusher or slider 13 is intended to be actuated by the end nozzle 141 or 151 of an oscillating lever 14 or 15 controlled by a reading device represented by two arrows 16 at the figure 1 .
  • the levers 14 and 15 are subjected to the action of two return springs 17 which tend to bring the spouts 141 and 151 in engagement with the pusher 13, against the action of the reading device 16.
  • the eccentric 4 carries two tabs 41 provided with teeth 42 intended to engage with corresponding teeth 52 formed at the free end of an arm 53 pivotally mounted about an axis X 53 on the rod 5 and subjected to action F 5 unrepresented elastic means tending to engage the teeth 42 and 52.
  • the elements 41 and 53 form two fixed point devices, one of which automatically engages when the shaft 1 reaches one of its two diametrically opposite stop positions and which is automatically released when the eccentric 4 leaves its stop position being driven by the disk 8 by means of the bolts 10 and 11.
  • a cover 18 is mounted on the eccentric 4 away from the face 43 of this eccentric visible at the figure 1 .
  • the elements 10 to 13 are received between the cover 18 and the face 43.
  • a compression spring 19 is disposed between the face 43 and the cover 18. This spring 19 bears against a stop 44 mounted on the eccentric 4. The spring 19 exerts on the arm 101 of the latch 10, by means of a pushbutton 19 ', an elastic force F 19 which tends to engage the end 102 of the arm 101 in a notch 83 when such a notch is opposite the end 102.
  • the force F 19 induces on the latch 10 a torque C 19 about the axis X 10 in a direction such that the arm 104 exerts on a lateral lug 132 of the pusher 13 a force F 104 which tends to move the pusher away from the X axis 1 .
  • the force F 104 is transmitted to the arm 114 of the lever 11 in the form of a force F 131 which tends to rotate the lock 11 around the axis X 11 in a direction opposite to the rotation of the lock 10 under the effect of the torque C 19 .
  • a torque C '19 due to the force F 131 causes the lever 111 clockwise to figure 2 , which has the effect of bringing or holding the end 112 in position in a notch 83.
  • the spring 19 and the pusher 19 ' act directly on the latch 10 and indirectly on the latch 11, through the latch 10 and the pusher 13, to bring the surfaces 103 and 113 respectively in engagement with the shoulders 84A and 84B in the configuration of the figure 2 or with the shoulders 84C and 84D when the latches cooperate with the notches 83 visible in the lower part of the figure 1 .
  • This maneuver can be performed quickly because, in the deceleration phase of the shaft 1, the lock 10 is discharged. In other words, the contact pressure between the surfaces 103 and 84A is then substantially zero. The movement of the lock 10 under the effect of the torque C 14 takes place against the elastic force F 19 .
  • the contact pressure between surfaces 113 and 84B is high.
  • the lock 11 is in simple support on the end 131 of the pusher 13. There is not, on the side of the end 115, tab equivalent to the tab 132 of the pusher 13, so that it is not transmitted to the arm 114 an effort equivalent to the effort F 132 . This allows the latch 11 to remain in an engagement configuration of its surface 113 with the shoulder 84B during the movement of the latch 10 under the effect of the force F 14 .
  • a tab 133 is disposed on the side of the pusher 13 opposite the tab 132.
  • the compression spring exerts on the end 115 and thanks to the pusher 20, an elastic force F 20 which induces on the latch 11 a torque C 20 around the axis X 11 tending to pivot this latch about the axis X 11 in a direction of clearance of its surface 113 relative to the shoulder 84B.
  • the stiffness constant of the spring 20 is chosen such that the torque C 20 does not overcome the friction force F o existing at the interface between the surfaces 113 and 84B as long as the shaft 1 is in progress. deceleration.
  • the intensity of the receiver force transmitted by the disk 8 to the eccentric 4 induces that the friction force F o is intense.
  • the torque C 20 is sufficient to clear the end 112 with respect to the notch 83 in which it was previously received. This induces, by the successive clearances of the locks 10 and 11, a complete uncoupling of the drive element, formed by the disc 8, relative to the actuating element of the connecting rod 5, which is formed by the eccentric 4.
  • the number of parts to be moved to uncouple the disk 8 and the eccentric 4 is reduced, which also allows to achieve high operating speeds and to obtain increased reliability of the dobby.
  • the constituent parts of the dobby are in the configuration of the figure 4 where, if the eccentric 4 is not to be driven, the disk 8 can follow the shaft 1 on a rotation of 180 ° in the direction of the arrow F 8 , in order to bring the shoulder 84C and 84D respectively into the configuration shoulders 84A and 84B at the figure 3 . If the force F 14 is then removed, because of the action of the reading device 16, the latches 10 and 11 engage in the notches 83 under the effect of the action F 19 of the spring 19 when the notches 83 bordered by the shoulders 84C and 84D arrive opposite ends 102 and 112.
  • a location 191 is provided in the vicinity of the latch 11 for receiving a spring and a pusher similar to the elements 19 and 19 '.
  • the shaft 1 and the disk 8 turn forward in the opposite direction of the arrows F 8 , it is possible to reverse the roles and the release order of the locks 10 and 11 which are, moreover, structurally identical. In this case it suffices to mount the spring and the pusher in the location 191 and to turn the pusher 13 so that the spring 20 is on the side of the lock 10.
  • a spring 19 and a pusher 19 'exert on the latch 10 an elastic force F 19 for engaging the end 102 of its arm in a notch 83.
  • This force is transmitted to the latch 11 by a contact between the ends 105 and 115 their arms 104 and 114.
  • the disc 8 rotates with the shaft 1 in the direction of the arrow F 8 .
  • the latch 10 is used to transmit to the eccentric 4 a motor force.
  • the latch 11 is used to transmit a receiving force.
  • This embodiment differs from the previous one in that the auxiliary spring 20 and the associated pusher 20 'are not inserted between a portion of the pusher or slider 13 and the lock 11 but between a fixed stop 45, carried by the disc 4, and the arm 114 of the latch 11.
  • the end 131 of the pusher 13 transmits this force to the arm 104 of the latch 10, in the form of a force F 132 .
  • This induces a corresponding torque C 14 which is transmitted only to the lock 10 and which releases the arm 101 relative to the notch 83 in which it was previously engaged.
  • Additional locations 191 and 201 allow mounting of the springs 19 and 20 and their pushers 19 'and 20' in a position compatible with a rotation of the disc 8 in the forward direction in the opposite direction of the arrow F 8 .
  • a spring 19 and a pusher 19 'exert on the latch 10 an elastic force F 19 engagement in a notch 83.
  • This embodiment differs from the previous ones in that the connection between the first latch 10 and the second latch 11 is made by a generally C-shaped leaf spring 20 which is fixed by a staple 21 on the arm 114 of the latch 11. The end 105 of the arm 104 of the latch 10 bears against a curved end 202 of the spring 20.
  • the spring 20 transmits the torque C 19 to the latch 11 while being in a configuration where his branches are closer than on the figure 7 .
  • the pusher or slider 13 is mounted on the eccentric 4 with the possibility of movement in translation in a direction D 1 radial to the axis of rotation of the main shaft 1.
  • the force F 20 induces a torque C 20 around the axis X 11 which tends to rotate the latch in a direction of disengagement of its end 112 relative to the notch 83.
  • the torque C 20 may be of low intensity, so that the latch 11 remains engaged by its surface. this 113 against the shoulder 84B as the friction force F 0 is greater than the elastic force F 20 .
  • a spring 19 exerts, thanks to a pusher 19 'and on an arm 101 of the lock 10, a main force F 19 which tends to bring back the end surfaces 103 and 113 of the arms 101 and 111 of the locks 10 and 11 in engagement with the shoulders 84A and 84B or equivalent of the disc 8.
  • the spring 19 and the pusher 19 ' act directly on the latch 10. They act on the latch 11 via the end 107 of a third arm 106 radial latch 10 which can bear against the end 115 of the arm 114 of the latch 11.
  • the force F 14 is transmitted to the arm 104 directly and to the arm 114 via the spring 20.
  • the mechanical decoupling between, on the one hand, the control means 13 and / or 14 of the first latch 10 during its release and, on the other hand, the second latch 11 allows the second latch to remain engaged in the notch 83 correspondingly, even as the first lock is being released. This makes it possible to disengage the first lock, while the driving element formed by the disc 8 is still being decelerated, before its total stop.
  • the invention makes it possible to use a main shaft which does not stop every half-turn, but slows down when it reaches the angular selection zones. This makes it possible to increase the operating speed of the loom.

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

Claims (12)

  1. Rotationsschaftmaschine (R) für eine Webmaschine (M), die für jedes ihrer Messer umfasst:
    - ein schwingendes Teil (5), das an einen Schaftrahmen (3) angekoppelt ist und einem Betätigungselement (4) zugeordnet ist, das beweglich auf einer Hauptwelle (1) der Schaftmaschine montiert ist,
    - ein Antriebselement (8), das drehfest mit der Hauptwelle verbunden ist,
    - zwei gesteuerte Klinken (10, 11) zur Drehkopplung des Antriebselementes (8) und des Betätigungselementes (4), wobei jede Klinke auf einem Antriebselement befestigt ist und eine erste Klinke (10) mit einer ersten Fläche (103) zur selektiven Abstützung gegen mindestens eine erste korrespondierende Fläche (84A, 84C) des Antriebselementes versehen ist, wobei diese ersten Flächen eine Grenzfläche (113/84A, 103/84C) zur Übertragung einer Antriebskraft (F3) des Antriebselementes (8) auf das Betätigungselement (4) bilden, während eine zweite Klinke (11) mit einer zweiten Fläche (113) zur selektiven Abstützung gegen mindestens eine zweite korrespondierende Fläche (84A, 84C) des Antriebselementes versehen ist, wobei diese zweiten Flächen eine Grenzfläche (113/84B, 103/84D) zur Übertragung einer Empfangskraft (F4) des Betätigungselementes auf das Antriebselement bilden,
    - erste Mittel (19, 19') zur elastischen Vorspannung (F19) der Klinken (10, 11), jede in Richtung einer Eingriffsanordnung ihrer jeweiligen Abstützflächen (103, 113) mit den korrespondierenden Flächen (84A-84D) des Antriebselementes (8), und
    - Mittel (13-15) zur Steuerung, die vorgesehen sind, um die Klinken gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') zu verschieben,
    dadurch gekennzeichnet, dass die ersten Mittel zur elastischen Vorspannung (19, 19') direkt (F19) auf die erste Klinke (10) und indirekt (F104, F131) auf die zweite Klinke (11) wirken und dass die Mittel zur Steuerung geeignet sind, die erste Klinke gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') zu verschieben (C14), während die zweite Klinke im Eingriffszustand seiner Abstützfläche (113) mit der zweiten Fläche (84B, 84D) des Antriebselementes (8) verbleibt.
  2. Schaftmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die ersten Mittel zur elastischen Vorspannung (19, 19') auf die zweite Klinke (11) über die erste Klinke (10) wirken.
  3. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie zweite Mittel zur elastischen Vorspannung (20, 20') umfasst, die auf die zweite Klinke (11), aber nicht auf die erste Klinke (10), eine Kraft zur Freisetzung (F20) der Abstützfläche (113) der zweiten Klinke in Bezug auf die zweite korrespondierende Fläche (84B, 84D) des Antriebselementes (8) ausüben.
  4. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Mittel zur Steuerung umfassen:
    - ein bewegliches Organ (13, 14), das direkt auf die erste Klinke (10) eine Verschiebungskraft (F132, F14) gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') ausübt und
    - elastische Mittel (20, 20') zur Übertragung einer Kraft zwischen einerseits dem beweglichen Organ (13) oder der ersten Klinke (10) und andererseits der zweiten Klinke (11).
  5. Schaftmaschine nach Anspruch 4, dadurch gekennzeichnet, dass die elastischen Mittel zur Übertragung einer Kraft eine Kompressionsfeder (20) oder eine Blattfeder (20) umfassen.
  6. Schaftmaschine nach einem der Ansprüche 4 oder 5, dadurch gekennzeichnet, dass die elastischen Mittel zur Kraftübertragung (20, 20') zwischen dem beweglichen Organ (13) und der zweiten Klinke (11) angeordnet sind.
  7. Schaftmaschine nach einem der Ansprüche 4 oder 5, dadurch gekennzeichnet, dass die elastischen Mittel zur Kraftübertragung (20) zwischen der ersten Klinke (10) und der zweiten Klinke (11) angeordnet sind.
  8. Schaftmaschine nach einem der Ansprüche 1 bis 3,
    dadurch gekennzeichnet, dass die Mittel zur Steuerung umfassen:
    - ein bewegliches Organ (13), das direkt auf die erste Klinke (10) eine Kraft zur Verschiebung gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') ausübt,
    - Hilfsmittel (20, 20') zur elastischen Vorspannung (F20), die auf die zweite Klinke (11) in die Richtung der Freisetzung der Abstützfläche (113) in Bezug auf die korrespondierende zweite Fläche (84B, 84D) des Antriebselementes (8) wirken, wobei diese Vorspannungshilfsmittel geeignet sind, die Abstützfläche der zweiten Klinke in Bezug auf die korrespondierende zweite Fläche des Antriebselementes nur dann freizusetzen, wenn die zweite Klinke nicht der Wirkung der ersten Mittel zur elastischen Vorspannung unterliegt, aufgrund einer Verschiebung (C14) der ersten Klinke (10) durch die Kraft (F14), die von dem beweglichen Organ (13) ausgeübt wird.
  9. Schaftmaschine nach Anspruch 8, dadurch gekennzeichnet, dass das bewegliche Organ von einem Drücker (13) gebildet wird, der an dem Betätigungselement (4) montiert ist, wobei er translatorisch gemäß einer radialen Richtung (D1) in Bezug auf die Rotationsachse (X1) der Hauptwelle (1) beweglich ist.
  10. Webmaschine (M), ausgerüstet mit einer Schaftmaschine (R) nach einem der vorhergehenden Ansprüche.
  11. Untergruppe, gehörend zu einer und passend für eine Schaftmaschine nach einem der Ansprüche 1 bis 9, wobei die Untergruppe einen Exzenter (4), der das Betätigungselement bildet, eine Pleuelstange (5), die an dem Exzenter befestigt ist, und einen Schwingarm (6) aufweist, der vorgesehen ist, die Verbindung zwischen der Pleuelstange und einem Schaftrahmen (3) sicherzustellen.
  12. Verfahren zur Steuerung einer Rotationsschaftmaschine (R), für jedes ihrer Messer umfassend:
    -
    - ein schwingendes Teil (5), das an einen Schaftrahmen (3) angekoppelt ist und einem Betätigungselement (4) zugeordnet ist, das beweglich auf einer Hauptwelle (1) der Schaftmaschine montiert ist,
    - ein Antriebselement (8), das drehfest mit der Hauptwelle verbunden ist,
    - zwei gesteuerte Klinken (10, 11) zur Drehkopplung des Antriebselementes (8) und des Betätigungselementes (4), wobei jede Klinke auf einem Antriebselement befestigt ist und eine erste Klinke (10) mit einer ersten Fläche (103) zur selektiven Abstützung gegen mindestens eine erste korrespondierende Fläche (84A, 84C) des Antriebselementes versehen ist, wobei diese ersten Flächen eine Grenzfläche (113/84A, 103/84C) zur Übertragung einer Antriebskraft (F3) des Antriebselementes (8) auf das Betätigungselement (4) bilden, während eine zweite Klinke (11) mit einer zweiten Fläche (113) zur selektiven Abstützung gegen mindestens eine zweite korrespondierende Fläche (84A, 84C) des Antriebselementes versehen ist, wobei diese zweiten Flächen eine Grenzfläche (113/84B, 103/84D) zur Übertragung einer Empfangskraft (F4) des Betätigungselementes auf das Antriebselement bilden,
    - erste Mittel (19, 19') zur elastischen Vorspannung (F19) der Klinken (10, 11), jede in Richtung einer Eingriffsanordnung ihrer jeweiligen Abstützflächen (103, 113) mit den korrespondierenden Flächen (84A-84D) des Antriebselementes (8), und
    - Mittel (13-15) zur Steuerung, die vorgesehen sind, um die Klinken gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') zu verschieben,
    dadurch gekennzeichnet, dass bei der Entkopplung des Antriebselementes (8) von dem Betätigungselement (4)
    - a) man auf die erste Klinke (10) gegen die Wirkung (F19) der ersten Mittel zur elastischen Vorspannung (19, 19') und in einer Richtung der Freisetzung ihrer Abstützfläche (103) in Bezug auf die korrespondierende erste Fläche (84A, 84C) des Antriebselementes (8) wirkt (F14), ohne direkt auf die zweite Klinke (11) zu wirken und
    - b) man Hilfsmittel (20, 20') auf die zweite Klinke (11) wirken lässt, die ihre Abstützfläche (113) in Bezug auf die korrespondierende zweite Fläche (84B, 84D) des Antriebselementes (8) freisetzen.
EP20070356044 2006-04-11 2007-04-10 Rotationsschaftmaschine, eine solche Schaftmaschine umfassende Webmaschine und Verfahren zur Steuerung einer solchen Schaftmaschine Active EP1845181B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0603203A FR2899602B1 (fr) 2006-04-11 2006-04-11 Ratiere rotative, metier a tisser comprenant une telle ratiere et procede de commande d'une telle ratiere

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EP1845181A1 EP1845181A1 (de) 2007-10-17
EP1845181B1 true EP1845181B1 (de) 2009-11-11

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US (1) US7980274B2 (de)
EP (1) EP1845181B1 (de)
JP (1) JP4922811B2 (de)
KR (1) KR101431647B1 (de)
CN (1) CN101054748B (de)
AT (1) ATE448339T1 (de)
BR (1) BRPI0702003B8 (de)
DE (1) DE602007003130D1 (de)
FR (1) FR2899602B1 (de)
RU (1) RU2419693C2 (de)

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FR2944297B1 (fr) 2009-04-10 2011-04-08 Staubli Sa Ets Dispositif d'assemblage, ensemble de deux pieces assemblees par un tel dispositif et lame de machine de formation de la foule comprenant un tel ensemble
CN101709525B (zh) * 2009-11-19 2011-04-13 常熟纺织机械厂有限公司 旋转式电子多臂机的三开口开口机构
FR2957366B1 (fr) * 2010-03-12 2012-04-13 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
FR2968317A1 (fr) 2010-12-06 2012-06-08 Staubli Sa Ets Dispositif de selection pour le controle d'une ratiere, ensemble de selection et ratiere controlee par un tel dispositif de selection
FR3080118B1 (fr) * 2018-04-16 2020-05-01 Staubli Faverges Ratiere rotative et metier a tisser

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DE2909131A1 (de) * 1979-03-08 1980-09-11 Johann Kaiser Gmbh & Co Kg Mas Schaftmaschine fuer webmaschinen
DE3476900D1 (en) * 1984-12-18 1989-04-06 Staeubli Ag Rotary dobby
US5214834A (en) * 1990-05-18 1993-06-01 S.A. Des Etablissments Staubli Process for assembling the actuation elements of a rotating dobby
FR2662710B1 (fr) * 1990-05-31 1992-08-28 Staubli Sa Ets Unite electro-magnetique pour la commande des ratieres et autres mecaniques de tissage.
IT1254219B (it) * 1992-02-25 1995-09-14 Eccentrico perfezionato per ratiera rotativa
IT1260291B (it) * 1992-12-18 1996-04-03 Lucio Burigana Ratiera rotativa
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
FR2802218B1 (fr) * 1999-12-14 2002-01-11 Staubli Sa Ets Ratiere rotative pour metier a tisser 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
ITMI20022695A1 (it) * 2002-12-19 2004-06-20 Fimtextile Spa Dispositivo per attuare la programmazione di ratiere rotative in macchine di tessitura
DE10343377B3 (de) * 2003-09-17 2005-04-28 Groz Beckert Kg Schaftantrieb für Webmaschinenschäfte

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KR20070101138A (ko) 2007-10-16
JP4922811B2 (ja) 2012-04-25
RU2007113375A (ru) 2008-11-10
DE602007003130D1 (de) 2009-12-24
BRPI0702003B1 (pt) 2016-11-21
FR2899602A1 (fr) 2007-10-12
BRPI0702003B8 (pt) 2017-05-16
US7980274B2 (en) 2011-07-19
CN101054748A (zh) 2007-10-17
US20070246950A1 (en) 2007-10-25
KR101431647B1 (ko) 2014-08-20
ATE448339T1 (de) 2009-11-15
BRPI0702003A (pt) 2007-12-11
RU2419693C2 (ru) 2011-05-27
JP2007277799A (ja) 2007-10-25
EP1845181A1 (de) 2007-10-17
CN101054748B (zh) 2011-10-05
FR2899602B1 (fr) 2008-05-23

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