EP2365116B1 - Rotary dobby and loom provided with such a dobby - Google Patents

Rotary dobby and loom provided with such a dobby Download PDF

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Publication number
EP2365116B1
EP2365116B1 EP11157534.6A EP11157534A EP2365116B1 EP 2365116 B1 EP2365116 B1 EP 2365116B1 EP 11157534 A EP11157534 A EP 11157534A EP 2365116 B1 EP2365116 B1 EP 2365116B1
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EP
European Patent Office
Prior art keywords
driving element
dobby
driving
latch
engaged
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Active
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EP11157534.6A
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German (de)
French (fr)
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EP2365116A1 (en
Inventor
Robert Nocenti
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Staubli Faverges SCA
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Staubli Faverges SCA
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Publication of EP2365116A1 publication Critical patent/EP2365116A1/en
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D—TEXTILES; PAPER
    • D10—INDEXING SCHEME ASSOCIATED WITH SUBLASSES OF SECTION D, RELATING TO TEXTILES
    • D10B—INDEXING SCHEME ASSOCIATED WITH SUBLASSES OF SECTION D, RELATING TO TEXTILES
    • D10B2331/00—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products
    • D10B2331/02—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products polyamides
    • D10B2331/021—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products polyamides aromatic polyamides, e.g. aramides

Definitions

  • the invention relates to a rotating dobby for the control of heald frames mounted on a loom, and to a loom equipped with such a dobby.
  • each disk has a very low axial thickness which reduces their interaction zone with a rocker which must also be provided in the thickness of the disk.
  • the motion transmission efforts to a heald frame pass through the contact interface between one of these disks and the rocker. This interface being narrow, the contact pressures are very high, which induces premature wear of the dobby and the breakage of certain parts.
  • the drive mechanism of the oscillating disk must be built in the division, which decreases the volume available for the aforementioned disks.
  • the invention intends to remedy more particularly by proposing a new rotary dobby that makes it possible to give a movement to the frames of the loom, including when these must not be moved from an upper position to a lower one. lower position or vice versa, while being more reliable and simpler to manufacture than those of the state of the art.
  • the invention relates to a rotary dobby for a loom, this dobby comprising, for each of its blades, an oscillating piece coupled to a heddle frame and associated with an actuating element mounted loosely on a central shaft , a first driving element of the actuating element, integral in rotation with the central shaft, a second driving element of the actuating element and at least one latch mounted on the operating element and capable of securing in rotation this actuating element with either the first driving element or with the second driving element, while one of the two driving elements is driven in a rotational movement in a only in one direction and that the other drive element is reciprocated.
  • This dobby is characterized in that the second driving element is arranged around the first driving element and in that the latch is disposed in a space defined radially between the first driving element and the second driving element.
  • the first and second drive elements can be arranged in the same width of the division, which allows them to be given a thickness, taken parallel to the axis of rotation of the central shaft, greater than that of the disks of the known dobby of EP-A-1,516,947 . It is thus possible to increase the contact surfaces between these drive elements and the lock or locks, this or these latches not increasing the axial size of the force transmission mechanism since they are located radially between the first driving element and the second driving element.
  • the invention relates to a loom equipped with a dobby as mentioned above.
  • the dobby R represented at Figures 1 to 5 comprises a central shaft 1 driven, in normal operation of the dobby, a continuous rotation movement in one direction, at a constant speed, about its longitudinal axis X 1 , this movement being represented by the arrow F 1 in the figures .
  • This shaft 1 receives a series of bearings 2, in number equal to that of the heald frames 3 of the loom M to which belongs the dobby R.
  • On each bearing 2 is mounted fou 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 rod 5 is coupled to a pivoting arm 6 by means of a connecting plate 7.
  • the pivoting arm 6 is hinged about an axis X 6 parallel to the axis X 1 and defined by a shaft 61 fixed relative to the frame of the dobby R.
  • the movement of the pivoting arm 6 ensures, thanks to a connection rods 62, the vertical displacement of a heald frame 3, which is represented very schematically for the clarity of the drawing, according to a vertical oscillations movement represented by the double arrow F 2 at the figure 1 .
  • Each dobby blade R comprises a drive disc 8 whose central opening is substantially circular and provided with two teeth 81 engaged in longitudinal grooves of corresponding shape 1a formed at the periphery of the shaft 1.
  • the disc 8 being secured in rotation of the shaft 1, it has a rotary motion at a constant speed represented by the arrow F 8.
  • the outer peripheral edge 82 of the disk 8 is provided with four notches 83a, 83b, 83c and 83d which are formed in the thickness or the edge of the disk 8.
  • Each notch 83a to 83d has a generally triangular shape.
  • Two latches 10 and 11 are respectively articulated around two shafts 12a and 12b fixed on the eccentric 4 and each defining a geometric axis X 10 , X 11 of rotation a lock 10 or 11 with respect to the eccentric 4.
  • the axes X 10 and X 11 are parallel to the axis X 1.
  • a drive ring 13 is disposed around each drive disk 8 at the same level along the axis X 1 .
  • each drive ring 13 radially surrounds a drive disk 8 extending around its outer radial edge 82 and each blade of the dobby comprises both a drive disk 8 and a crown Training 13.
  • the ring 13 and the disk 8 may have the same axial thickness, or comparable axial thicknesses, substantially equal to the difference between the division, of the order of 12 mm, and the thickness of the eccentric 4, with the clearance .
  • each ring 13 is provided with four notches 133a, 133b, 133c and 133d which are intended to cooperate selectively with the bolts 10 and 11 and are formed in the thickness or the edge of the ring 13.
  • Each notch 133a to 133d has a generally triangular shape.
  • the notches 83a and 83c are diametrically opposed, as are the notches 83b and 83d, the notches 133a and 133c and the notches 133b and 133d.
  • the various drive rings 13, which are flat and extend parallel to each other along the shaft 1, are separated by spacers 14 and assembled by tie rods 14a, so that they constitute a rigid assembly or cradle which can be rotated alternately about the axis X 1 by a suitable mechanism, mechanical or electrical type which is disposed outside the area where the blades are formed, for example in the vicinity of one end of the 1.
  • Each ring 13 thus has an alternating rotation movement about the axis X 1 , this movement being represented by the arrows F 13 , in the same direction as the arrow F 8 , and F '13 , in a direction opposite to the arrow F 8 , and having an angular amplitude of 60 °.
  • the locks 10 and 11 are arranged in an annular space E defined between the respective peripheral edges 82 and 132 of the drive disk 8 and the drive ring 13.
  • This annular space opens at the two axial faces of the disk 8 and of the two axial faces of the crown 13.
  • the space E is identified as a shaded area at the figure 2 only.
  • the latch 10 comprises two lugs 101 and 102 which extend from an annular body 103 mounted around the shaft 12a.
  • the end 104 of the tab 101 is intended to be selectively engaged in one of the openings 83a and 83c, while the end 105 of the tab 102 is intended to be selectively engaged in one of the notches 133a and 133c.
  • the latch 10 also comprises a control lug 106 intended to cooperate with one of two identical rockers 15 and 16 hinged to the drive ring 13.
  • the constituent parts of the latch 11 bear the same references as those of the latch 10 increased by 10.
  • the latch 11 thus comprises two lugs 111 and 112 which extend from a body 113 and end with ends 114 and 115 intended to be respectively selectively engaged in the notches 83b and 83d, 133b and 133d, then a control lug 116 allows it to interact with one of the rockers 15 and 16.
  • the bolts 10 and 11 are identical except at the level of the control lugs 106 and 116 which are provided to be superimposed in the thickness axial of the space E.
  • Each of the latches 10 and 11 is designed to be engaged with either the drive disk 8 or with the drive ring 13, the two latches 10 and 11 being simultaneously engaged with the same drive element.
  • the rocker 15 is articulated on a shaft 17a passing right through the ring 13.
  • the rocker 15 is formed by the assembly of two plates 15a and 15b interconnected by two spacers 15c and 15d.
  • the spacer 15c is located radially outside the ring 13, that is to say connects the plates 15a and 15b beyond the peripheral outer radial edge 137 of the ring 13 with respect to the X axis. 1 .
  • the spacer 15d connects the plates 15a and 15b to the inside of the ring 13, that is to say in the vicinity of its internal radial edge 132.
  • a notch 135 is provided in the internal radial edge 132 to accommodate spacer 15d.
  • the plates 15a and 15b are each provided with a hook 15e, these hooks being folded towards each other so as to define together a bridge 15f which extends between the plates 15a and 15b.
  • the rocker 15 is mounted as a yoke around a portion of the ring 13, the plates 15a and 15b being disposed on the two opposite axial faces of the drive ring 13. This allows each of the spacers 15c and 15d to have a thickness axial e 15 substantially equal to that of the ring 13.
  • the rocker 16 is identical to the rocker 15 and articulated on the drive ring 13 around a second shaft 17b.
  • 16c and 16d are the spacers of the rocker 16 which are respectively similar to the spacers 15c and 15d.
  • the tilters 15 and 16 are mounted on the ring 13 so that the spacers 15c and 16c, on the one hand, 15d and 16d, on the other hand, are diametrically opposed.
  • Two stops 18 and 19 are mounted on the eccentric 4 on the same side as the shafts 12a and 12b.
  • two return levers 20 and 21 are respectively mounted on the eccentric 4, on the same side as the shafts 12a and 12b and housed in the space E, respectively close to the bolts 10 and 11.
  • the levers 20 and 21 are respectively articulated around two shafts 22a and 22b parallel to the shafts 12a and 12b.
  • X 20 and X 21 respectively denote the axes of articulation of the levers 20 and 21 with respect to the eccentric 4.
  • the lever 20 comprises a first arm 201 resting against the lug 101 of the latch 10, on the side of this lug opposite the drive disk 8.
  • the lever 20 also comprises a second arm 202 subjected to an elastic force E 23 exerted by a spring 23 bearing against the stop 18.
  • the force E 23 is transmitted to the latch 10 in the form of a force E 20 exerted by the arm 201 of the lever 20, the force E 20 having the effect of pressing the arm 201 against the external radial edge 82 of the drive disk 8.
  • a spring 24 bearing on the stop 19 exerts on the lever 21 an elastic force E 24 that the lever 21 transmits to the latch 11 in the form of a E 2 force , which plate the tab 111 of the latch 11 closest to the drive disc 8 against the outer radial edge 82 of the drive disc 8.
  • rocker 15 is subjected to the action of a spring 25 disposed in a housing 136 constituted by a hole formed through the drive ring 13.
  • the bridge 15f is also engaged in the housing 136 and is under a stress elastic E 25 exerted by the spring 25, this elastic force tending to press the spacer 15d against the bottom of the notch 135, that is to say to move this spacer 15d control tabs 106 and 116 locks 10 and 11.
  • the rocker 16 is also mounted on the drive ring 13 with the interposition of a spring 26 which exerts a force E 26 tending to press its inner spacer 16d in the bottom of the notch provided for this purpose on the internal radial edge 132 of the drive gear 13.
  • the dobby R also comprises two oscillating levers 30 and 31 each articulated around a shaft 32a or 32b which is fixed relative to the frame of the dobby.
  • X 30 and X 31 respectively denote the axes of articulation of the oscillating levers 30 and 31 which are defined by the shafts 32a and 32b.
  • the oscillating lever 30 is equipped with a roller 33 designed to roll on a portion 137a of the outer radial peripheral edge 137 of the drive ring 13, as well as on the spacer 15c of the rocker 15, depending on the weave.
  • the oscillating lever 31 is equipped with a roller 34 designed to roll on a portion 137b of the edge 137 and on the outer spacer 16c of the rocker 16, depending on the armor.
  • a selection device 35 which comprises an electromagnet 36 and a selection finger 37, is provided to come into selective engagement with the end 30a of the lever 30 opposite the roller 33 and the end 31a of the lever 31 opposite the roller 34.
  • the selection device 35 makes it possible to hold one or the other of the levers 30 and 31 in position and to hold the roller 33 or 34 of the lever 30 or 31 on which it acts away from the rocker 15 or 16 adjacent.
  • Unrepresented springs exert on the levers 30 and 31 elastic forces E 30 , E 31 which tend to rotate these oscillating levers about the axes X 30 and X 31 in a direction such that the rollers 33 and 34 are moved in the direction of the axis X 1 and that the ends 30a and 31a are remote from this axis.
  • the drive disc 8 constitutes a first element for rotating the eccentric 4, with a rotation movement F 8 in one direction, at a constant speed.
  • the driving ring 13 constitutes a second drive element of the eccentric 4, with an alternating rotational movement F 13 and F '13 .
  • the rotation of the elements 4, 8 and 13 takes place around the axis X 1 .
  • each of the frames 3 is defined for each pick, that is to say each insertion of a weft yarn.
  • a frame can be made to change from an upper position P SUP to a lower position P INF through an intermediate or median position P MED , or vice versa, which is considered a movement basic, or main movement.
  • the frame maintains a higher position, with a low amplitude movement, it performs a secondary movement between the upper position P SUP and a position P ' SUP located above the median position P MED and close to the upper position.
  • the frame When the frame maintains a lower position, it performs a secondary movement between the lower position P INF and a position P ' INF located below the median position P MED and close to the lower position.
  • the difference in height between the positions P INF and P ' INF is less than half the difference in height between the positions P SUP and P INF.
  • the secondary movement takes place over more than 360 ° of craft angle.
  • the basic movement of a heald frame 3 is a portion of sinusoidal motion with a period equal to 720 ° of working angle, between the position P INF and the position P su p or vice versa.
  • This movement is obtained by the conversion of a driving movement of the eccentric 4 by the drive disc 8 which is driven by a uniform rotational movement in one direction, with a period equal to 720 ° of work angle .
  • This is represented by the portion of curve in solid line extending between 720 ° and 1800 ° of angle of the trade ⁇ to the figure 5 and which represents the position P of a frame according to the angle of the craft, during its movements according to the arrow F 2 -
  • N 1 to N 8 are shown.
  • a secondary movement of the heald frame 3 can be obtained when the eccentric 4 is driven by the ring 13, with an alternating rotational movement, which corresponds to the curve portion shown in solid lines between the angles of occupation 360 and 720 to the figure 5 .
  • This secondary movement also corresponds to the curve portion shown in solid line between the angles 1800 ° and 2160 ° in this figure.
  • the portion of the curve between the angles 360 ° and 720 ° corresponds to a secondary movement occurring near the upper position P SUP of a frame that the frame reaches at the pick N 2 and retains the pick N 3 , then that the portion of the curve between the angles of occupation 1800 and 2160 corresponds to the secondary movement occurring near the lower position P INF than the frame reached at the pick N 6 and kept at the pick N 7 .
  • the secondary movement between the 360 ° and 720 ° occupation angles takes place between the positions P SUP and P ' SUP , with an amplitude equal to the difference in height of these positions.
  • the secondary movement between the angles 1800 ° and 2160 ° takes place between the positions P INF and P ' INF , with an amplitude equal to the difference in height between these positions.
  • the assembly or cradle constituted by the various driving rings 13 secured to each other is controlled so that the secondary movement of a frame 3 driven by one of these rings 13 is a portion of sinusoidal frequency movement four times as much. high than the base movement and amplitude equal to 1/16 th of the base movement amplitude, which corresponds to an oscillation of the set of crowns 13 of amplitude equal to 60 °.
  • the angular amplitude of the movement of the rings 13 is between 30 ° and 120 °, preferably between 45 ° and 90 °, the value of 60 ° proving very advantageous.
  • the movement of the ring 13 has a reduced angular amplitude with respect to the complete rotational movement of the disk 8. This has the consequence that the amplitude of movement according to the arrow F 2 of the frame 3 driven by the ring 13 is reduced with respect to the amplitude of this movement when the frame is driven by the disk 8.
  • the frame 3 when it is driven by the ring 13, the frame 3 remains at near its upper end position, that is to say its upper position P SUP , or in the vicinity of its lower end position P INF , that is to say, its lower position.
  • the difference in height between P SUP and P ' SUP or between P INF and P' INF is equal to 1/16 of the difference in height between P SUP and P INF
  • the frequency of the secondary movement of the frames 3 may be another multiple of four times the frequency of the basic movement of the frames 3, for example equal to eight times or twelve times this frequency.
  • the figure 5 shows in dotted lines the instantaneous velocity curve V of an animated frame of the movement represented by the solid line curve and in axial lines the instantaneous acceleration curve A of this frame.
  • the movement represented by the position curve P is a non-stop movement, the acceleration of a frame being non-zero when its speed is zero.
  • the elements 8 and 13 have the same instantaneous angular velocities and the same instantaneous angular accelerations with respect to the axis X 1 .
  • the driving elements 8 and 13 are driven in a rotation movement in the same direction, thanks to the secondary frequency movement 4 times greater than that of the base movement. There is therefore no discontinuity of movement, speed and acceleration of the frame 3 at the transfer points, even if there has been switching.
  • the rollers 33 and 34 roll against the portions 137a and 137b of the outer edge 137, or a portion of these portions, which makes it possible to obtain a leveling of the levers 30 and 31 by rotating them against the efforts E 30 and E 31 .
  • the selection device 35 can retain the end 30a or 31a of one of them depending on the power supply of the electromagnet 36 which depends on the armor, to cause or not switching locks 10 and 11.
  • the levers 30 and 31 are leveled and the selection device 35 blocks the lever 31 without interacting with the lever 30.
  • This action of the rocker 15 on the bolts 10 and 11 has the effect of pivoting respectively about the axes X 10 and X 11 in a direction of release of the ends 104 and 114 relative to the notches 83c and 83b, while engaging the ends 105 and 115 respectively in the notches 133c and 133b.
  • the action of the lever 30 on the rocker 15 makes it possible to separate the eccentric 4 with respect to the drive disc 8 and to secure it to the drive ring 13, so that the frame 3 is then animated secondary movement.
  • the action of the rocker 15 on the bolts 10 and 11 takes place against the forces E 23 and E 24 .
  • the latches 10 and 11 work in compression to transmit the movement of one of the driving elements 8 or 13 to the eccentric 4, which ensures a duration
  • the fact that the rollers 33 and 34 roll on the portions 137a and 137b of the outer edge 137 allows this edge to provide a leveling function, as envisaged in FIG. EP-A-1,382,725 , so that the selection device 35 is dimensioned only to withstand the forces E 30 and E 31 , without having to positively move the levers 30 and 31.
  • the two latches 10 and 11 In operation, depending on whether the frame 3 accelerates or decelerates, the two latches 10 and 11 alternately join the eccentric 4 with the drive element, whether this element is the disk 8 or the ring 13. In a phase of movement of the 3, a single latch 10 or 11 secures the eccentric 4 with one of the driving elements 8 or 13, while in another phase of movement, it is the other latch 11 or 10 which provides this function of solidarity.
  • the driving elements 8 and 13 have the same axial thickness. Alternatively, they may have different thicknesses.
  • the rockers 15 and 16 may not act directly on the control tabs 106 and 116 of the locks 10 and 11 but on a slide movable in translation in a radial direction relative to the axis X 1 and received in a housing of the eccentric 4, the ends of the tabs 106 and 116 being articulated on the slide.
  • the lock 10 is provided with a head 108 having two teeth 108a and 108b which can be selectively engaged in one of the two notches 83a and equivalent of the drive disk 8 and in one of the two notches 133a and equivalent of the drive ring 13.
  • the notches 83a, 133a and equivalent are respectively formed on the outer radial edge 82 of the disk 8 and on the inner radial edge 132 of the ring 13.
  • the latch 10 is disposed radially in a space E which extends between the disk 8 and the ring 13 and it allows to mechanically couple the eccentric 4 is to disc 8 to crown 13.
  • a stop 18, a lever 20 and a spring 23 operate as those of the first embodiment.
  • the lock 10 is unique and comprises a piston 109 loaded elastically by two springs 23 and 24 which each exert a force centrifugal E 23 or E 24 tending to engage an outer radial portion 109a of the piston 109 in one of two notches 133a and equivalent formed on the inner radial edge 132 of the drive ring 133.
  • the drive is provided with two notches 83a and an equivalent selective receiving of an inner radial portion 109b of the piston 109.
  • a slider 15 and its equivalent, not shown and diametrically opposed with respect to the slider 15, are arranged in the ring 13 with a possibility of translation in a radial direction and allow to exercise selectively on the piston 109 a force of engagement of the portion 109b in the notch 83a or the equivalent notch.
  • the latch 10 is clutched on the drive ring 13 and, when it is desired to lock the latch 10 in rotation with the disk 8, it suffices to leave the roller 33 or equivalent of the one of the oscillating levers 30 and equivalent acting on the slider 15 or equivalent near which the lock 10 is located.
  • the latch 10 is disposed in a space E which extends radially between the outer and inner edges 82 and 132 of the drive elements 8 and 13 and the drive ring 13 is arranged radially around the drive disc 8 .
  • the oscillating levers 30 and 31 can act directly on the locks mounted on the eccentric.
  • the invention is described above in the case where the shaft 1 and the discs 8 are driven in a rotary motion in one direction, while the rings 13 are moved in a reciprocating motion.
  • the invention also relates to the opposite case where the central shaft and the disks 8 are driven by an alternating rotational movement, whereas the set of rings 13 is driven by a continuous rotational movement in one direction only. preferably at constant speed.
  • a heald frame when a heald frame is driven from a ring 13, the amplitude of its movement of vertical oscillations is reduced with respect to its amplitude when it is driven by a disk 8 and the switching of the locks 10 and the equivalent, a securing position with the disk 8 to a position of attachment to the ring 13, or conversely, occurs when the frame is in the vicinity of its position higher or near its lower position.

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

Description

L'invention a trait à une ratière rotative pour la commande des cadres de lisses montés sur un métier à tisser, ainsi qu'à un métier à tisser équipé d'une telle ratière.The invention relates to a rotating dobby for the control of heald frames mounted on a loom, and to a loom equipped with such a dobby.

Dans le domaine des ratières rotatives, il est connu, par exemple de FR-A-2 663 347 , d'entraîner avec un mouvement secondaire les cadres d'un métier à tisser, y compris lorsque ceux-ci conservent une position supérieure ou une position inférieure, par rapport à une positon intermédiaire où les oeillets de leurs lisses sont alignés avec le plan d'insertion des fils de trames. Dans ce genre de matériels, il est connu de EP-A-1 516 947 d'utiliser, pour chaque lame d'une ratière, deux disques dont l'un est animé d'un mouvement de rotation continu dans un seul sens, alors que l'autre est animé d'un mouvement oscillant, ces deux disques étant montés côte à côte et au voisinage d'un excentrique, dans la division de la lame. Ceci impose que chaque disque a une épaisseur axiale très faible qui réduit leur zone d'interaction avec une bascule qui doit également être prévue dans l'épaisseur du disque. Or, les efforts de transmission de mouvement à un cadre de lisses passent par l'interface de contact entre l'un de ces disques et la bascule. Cette interface étant étroite, les pressions de contact sont très élevées, ce qui induit une usure prématurée de la ratière et la casse de certaines pièces. En outre, le mécanisme d'entraînement du disque à mouvement oscillant doit être construit dans la division, ce qui diminue d'autant le volume disponible pour les disques précités.In the field of rotary dobbies, it is known, for example FR-A-2,663,347 to drive with a secondary movement the frames of a loom, including when they maintain a higher position or a lower position, relative to an intermediate position where the eyelets of their healds are aligned with the plane of insertion of the frame wires. In this kind of material, it is known to EP-A-1,516,947 to use, for each blade of a dobby, two disks, one of which is driven in a continuous rotational movement in one direction, while the other is animated by an oscillating movement, these two disks being mounted side by side and in the vicinity of an eccentric, in the division of the blade. This requires that each disk has a very low axial thickness which reduces their interaction zone with a rocker which must also be provided in the thickness of the disk. However, the motion transmission efforts to a heald frame pass through the contact interface between one of these disks and the rocker. This interface being narrow, the contact pressures are very high, which induces premature wear of the dobby and the breakage of certain parts. In addition, the drive mechanism of the oscillating disk must be built in the division, which decreases the volume available for the aforementioned disks.

C'est à ces inconvénients qu'entend plus particulièrement remédier l'invention en proposant une nouvelle ratière rotative qui permet de conférer un mouvement aux cadres du métier, y compris lorsque ceux-ci ne doivent pas être déplacés d'une position supérieure vers une position inférieure ou réciproquement, tout en étant plus fiable et plus simple à fabriquer que celles de l'état de la technique.It is these drawbacks that the invention intends to remedy more particularly by proposing a new rotary dobby that makes it possible to give a movement to the frames of the loom, including when these must not be moved from an upper position to a lower one. lower position or vice versa, while being more reliable and simpler to manufacture than those of the state of the art.

A cet effet, l'invention concerne une ratière rotative pour un métier à tisser, cette ratière comportant, pour chacune de ses lames, une pièce oscillante attelée à un cadre de lisses et associée à un élément d'actionnement monté fou sur un arbre central, un premier élément d'entraînement de l'élément d'actionnement, solidaire en rotation de l'arbre central, un deuxième élément d'entraînement de l'élément d'actionnement et au moins un verrou monté sur l'élément d'actionnement et apte à solidariser en rotation cet élément d'actionnement soit avec le premier élément d'entraînement, soit avec le deuxième élément d'entraînement, alors que l'un des deux éléments d'entraînement est animé d'un mouvement de rotation dans un seul sens et que l'autre élément d'entraînement est animé d'un mouvement de rotation alternatif. Cette ratière est caractérisée en ce que le deuxième élément d'entraînement est disposé autour du premier élément d'entraînement et en ce que le verrou est disposé dans un espace défini radialement entre le premier élément d'entraînement et le deuxième élément d'entraînement.For this purpose, the invention relates to a rotary dobby for a loom, this dobby comprising, for each of its blades, an oscillating piece coupled to a heddle frame and associated with an actuating element mounted loosely on a central shaft , a first driving element of the actuating element, integral in rotation with the central shaft, a second driving element of the actuating element and at least one latch mounted on the operating element and capable of securing in rotation this actuating element with either the first driving element or with the second driving element, while one of the two driving elements is driven in a rotational movement in a only in one direction and that the other drive element is reciprocated. This dobby is characterized in that the second driving element is arranged around the first driving element and in that the latch is disposed in a space defined radially between the first driving element and the second driving element.

Grâce à l'invention, les premier et deuxième éléments d'entraînement peuvent être disposés dans la même largeur de la division, ce qui permet de leur conférer une épaisseur, prise parallèlement à l'axe de rotation de l'arbre central, supérieure à celle des disques de la ratière connue de EP-A-1 516 947 . Il est ainsi possible d'augmenter les surfaces de contact entre ces éléments d'entraînement et le ou les verrous, ce ou ces verrous n'augmentant pas l'encombrement axial du mécanisme de transmission d'effort puisqu'ils sont situés radialement entre le premier élément d'entraînement et le deuxième élément d'entraînement.Thanks to the invention, the first and second drive elements can be arranged in the same width of the division, which allows them to be given a thickness, taken parallel to the axis of rotation of the central shaft, greater than that of the disks of the known dobby of EP-A-1,516,947 . It is thus possible to increase the contact surfaces between these drive elements and the lock or locks, this or these latches not increasing the axial size of the force transmission mechanism since they are located radially between the first driving element and the second driving element.

Selon des aspects avantageux mais non obligatoires de l'invention, une telle ratière peut incorporer une ou plusieurs des caractéristiques suivantes prises dans toute combinaison techniquement admissible :

  • Le premier élément d'entraînement est animé d'un mouvement de rotation dans un seul sens, alors que le deuxième élément d'entraînement est animé d'un mouvement de rotation alternatif.
  • Chaque verrou est pourvu d'une première partie adaptée pour s'engager sélectivement dans au moins une encoche ménagée sur un bord radial externe du premier élément d'entraînement et d'une deuxième partie adaptée pour s'engager sélectivement dans au moins une encoche ménagée sur un bord radial interne du deuxième élément d'entraînement. Dans ce cas, la ratière comprend avantageusement des moyens de charge élastique de chaque verrou vers une position d'engagement de sa première partie ou de sa deuxième partie dans une encoche ménagée sur le bord radial externe du premier élément d'entraînement ou dans une encoche ménagée sur le bord radial interne du deuxième élément d'entraînement. On peut en outre prévoir que, lorsqu'un verrou est en prise avec un élément d'entraînement, parmi le premier et le deuxième élément d'entraînement, une partie de ce verrou, qui est adaptée pour d'engager sélectivement dans une encoche de l'autre élément d'entraînement, est en appui glissant contre le bord adjacent de l'autre élément d'entraînement.
  • Deux verrous sont disposés dans l'espace défini radialement entre les éléments d'entraînement et le bord radial externe du premier élément d'entraînement et le bord radial interne du deuxième élément d'entraînement sont chacun pourvus de quatre encoches de réception d'une partie d'un verrou.
  • Les deuxièmes éléments d'entraînement appartenant aux différentes lames de la ratière sont solidaires en rotation autour de l'axe de l'arbre central et forment ensemble un berceau, lui-même entraîné en rotation autour de cet axe.
  • La ratière comprend, pour chaque lame, deux leviers oscillants, aptes à être maintenus en position par un dispositif de sélection, et au moins un organe, monté sur le deuxième élément d'entraînement et apte à transmettre un effort de l'un des leviers oscillants vers un verrou. Chaque organe de transmission d'effort peut être un basculeur, monté pivotant autour d'un axe fixe par rapport au deuxième élément d'entraînement et chargé élastiquement vers une position où il n'interagit pas avec le ou les verrous. En variante, chaque organe de transmission d'effort est un coulisseau mobile, en translation selon une direction radiale, sur le deuxième élément d'entraînement.
  • La ratière comprend, pour chaque lame, deux leviers oscillants, aptes à être maintenus en position par un dispositif de sélection et au moins une portion d'un bord radial externe du deuxième élément d'entraînement est apte à coopérer avec un levier oscillant et à placer ce levier dans une position où il peut être retenu par le dispositif de sélection.
  • Lorsque la ratière est dans une configuration où le verrou peut être basculé entre une première position, en prise avec l'un des éléments d'entraînement, et une deuxième position, en prise avec l'autre élément d'entraînement, les deux éléments d'entraînement sont animés d'un mouvement de rotation dans le même sens. Dans cette configuration de basculement, les deux éléments d'entraînement ont avantageusement les mêmes vitesses angulaires et les mêmes accélérations angulaires instantanées par rapport à l'axe de rotation de l'arbre central.
According to advantageous but non-compulsory aspects of the invention, such a dobby may incorporate one or more of the following features taken in any technically permissible combination:
  • The first drive member is rotated in one direction, while the second drive member is rotated alternately.
  • Each latch is provided with a first portion adapted to engage selectively in at least one notch provided on an outer radial edge of the first drive member and a second portion adapted to engage selectively in at least one notched slot. on an inner radial edge of the second drive member. In this case, the dobby preferably comprises means for resiliently loading each latch towards an engagement position of its first portion or of its second portion in a notch provided on the outer radial edge of the first driving element or in a notch formed on the inner radial edge of the second drive element. It can further be provided that, when a latch is engaged with a drive member, among the first and second drive members, a portion of the latch, which is adapted to selectively engage a notch of the other drive element is in sliding abutment against the adjacent edge of the other drive element.
  • Two latches are provided in the radially defined space between the drive members and the outer radial edge of the first driving member and the inner radial edge of the second driving member are each provided with four receiving notches of a portion a lock.
  • The second drive elements belonging to the different blades of the dobby are integral in rotation about the axis of the central shaft and together form a cradle, itself driven in rotation about this axis.
  • The dobby comprises, for each blade, two oscillating levers, able to be held in position by a selection device, and at least one member, mounted on the second drive element and adapted to transmit a force of one of the levers oscillating towards a lock. Each force transmission member may be a rocker, pivotally mounted about a fixed axis relative to the second drive member and resiliently loaded to a position where it does not interact with the locks. In a variant, each force transmission member is a sliding slider, in translation in a radial direction, on the second driving element.
  • The dobby comprises, for each blade, two oscillating levers, able to be held in position by a selection device and at least a portion of an outer radial edge of the second driving element is adapted to cooperate with an oscillating lever and to place this lever in a position where it can be retained by the selection device.
  • When the dobby is in a configuration where the lock can be tilted between a first position, engaged with one of the driving elements, and a second position, engaged with the other driving element, the two elements of The drive is rotated in the same direction. In this tilting configuration, the two drive elements advantageously have the same angular velocities and the same instantaneous angular accelerations with respect to the axis of rotation of the central shaft.

En outre, l'invention concerne un métier à tisser équipé d'une ratière telle que mentionnée ci-dessus.In addition, the invention relates to a loom equipped with a dobby as mentioned above.

L'invention sera mieux comprise et d'autres avantages de celle-ci apparaîtront plus clairement à la lumière de la description qui va suivre d'un mode de réalisation d'une ratière et d'un métier à tisser conformes à son principe, donnée uniquement à titre d'exemple et faite en référence aux dessins annexés dans lesquels :

  • la figure 1 est une représentation schématique de principe d'un métier à tisser conforme à l'invention comprenant une ratière conforme à l'invention, cette ratière étant représenté en coupe transversale, dans une première configuration,
  • la figure 2 est une vue analogue au détail II à la figure 1 lorsque la ratière est dans une deuxième configuration,
  • la figure 3 est une vue à plus grande échelle du détail III à la figure 2,
  • la figure 4 est une vue analogue à la figure 2 lorsque la ratière est dans une troisième configuration,
  • la figure 5 est une représentation schématique de principe de la position d'un cadre, de sa vitesse et de son accélération en fonction de l'angle métier,
  • la figure 6 est une vue en perspective d'un basculeur utilisé dans la ratière des figures 1 à 4,
  • la figure 7 est une vue analogue à la figure 3 pour une ratière conforme à un deuxième mode de réalisation de l'invention et
  • la figure 8 est une vue analogue à la figure 3 pour une ratière conforme à un troisième mode de réalisation de l'invention.
The invention will be better understood and other advantages thereof will appear more clearly in the light of the following description of an embodiment of a dobby and a loom according to its principle, given only by way of example and with reference to the appended drawings in which:
  • the figure 1 is a schematic representation of a loom according to the invention comprising a dobby according to the invention, this dobby being shown in cross section, in a first configuration,
  • the figure 2 is a view similar to detail II at the figure 1 when the dobby is in a second configuration,
  • the figure 3 is a larger-scale view of detail III to the figure 2 ,
  • the figure 4 is a view similar to the figure 2 when the dobby is in a third configuration,
  • the figure 5 is a schematic representation of the position of a frame, its speed and its acceleration according to the angle of the craft,
  • the figure 6 is a perspective view of a rocker used in the dobby of Figures 1 to 4 ,
  • the figure 7 is a view similar to the figure 3 for a dobby according to a second embodiment of the invention and
  • the figure 8 is a view similar to the figure 3 for a dobby according to a third embodiment of the invention.

La ratière R représentée aux figures 1 à 5 comprend un arbre central 1 animé, en fonctionnement normal de la ratière, d'un mouvement de rotation continu dans un seul sens, à vitesse constante, autour de son axe longitudinal X1, ce mouvement étant représenté par la flèche F1 sur les figures. Cet arbre 1 reçoit une série de roulements 2, en nombre égal à celui des cadres de lisses 3 du métier à tisser M auquel appartient la ratière R. Sur chaque roulement 2 est monté fou un excentrique 4 sur lequel est montée folle l'ouverture d'une bielle 5 oscillante, autour d'un second roulement 2'. L'extrémité libre 51 de la bielle 5 est attelée à un bras pivotant 6 au moyen d'une plaque de liaison 7. Pour chaque lame ou cadre de lisses 3, le bras pivotant 6 est articulé autour d'un axe X6 parallèle à l'axe X1 et défini par un arbre 61 fixe par rapport au bâti de la ratière R. Le mouvement du bras pivotant 6 assure, grâce à une liaison par biellettes 62, le déplacement vertical d'un cadre de lisses 3, ce qui est représenté de façon très schématique pour la clarté du dessin, selon un mouvement d'oscillations verticales représenté par la double flèche F2 à la figure 1.The dobby R represented at Figures 1 to 5 comprises a central shaft 1 driven, in normal operation of the dobby, a continuous rotation movement in one direction, at a constant speed, about its longitudinal axis X 1 , this movement being represented by the arrow F 1 in the figures . This shaft 1 receives a series of bearings 2, in number equal to that of the heald frames 3 of the loom M to which belongs the dobby R. On each bearing 2 is mounted fou 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 rod 5 is coupled to a pivoting arm 6 by means of a connecting plate 7. For each blade or heald frame 3, the pivoting arm 6 is hinged about an axis X 6 parallel to the axis X 1 and defined by a shaft 61 fixed relative to the frame of the dobby R. The movement of the pivoting arm 6 ensures, thanks to a connection rods 62, the vertical displacement of a heald frame 3, which is represented very schematically for the clarity of the drawing, according to a vertical oscillations movement represented by the double arrow F 2 at the figure 1 .

Chaque lame de ratière R comprend un disque d'entraînement 8 dont l'ouverture centrale est sensiblement circulaire et pourvue de deux dents 81 engagés dans des rainures longitudinales de forme correspondante 1a ménagées à la périphérie de l'arbre 1. Le disque 8 étant solidaire en rotation de l'arbre 1, il a un mouvement rotatif à vitesse constante représenté par la flèche F8. Each dobby blade R comprises a drive disc 8 whose central opening is substantially circular and provided with two teeth 81 engaged in longitudinal grooves of corresponding shape 1a formed at the periphery of the shaft 1. The disc 8 being secured in rotation of the shaft 1, it has a rotary motion at a constant speed represented by the arrow F 8.

Le bord périphérique externe 82 du disque 8 est pourvu de quatre encoches 83a, 83b, 83c et 83d qui sont ménagées dans l'épaisseur ou la tranche du disque 8. Chaque encoche 83a à 83d a une forme globalement triangulaire.The outer peripheral edge 82 of the disk 8 is provided with four notches 83a, 83b, 83c and 83d which are formed in the thickness or the edge of the disk 8. Each notch 83a to 83d has a generally triangular shape.

Deux verrous 10 et 11 sont respectivement articulés autour de deux arbres 12a et 12b fixés sur l'excentrique 4 et définissant chacun un axe géométrique X10, X11 de rotation d'un verrou 10 ou 11 par rapport à l'excentrique 4. Les axes X10 et X11 sont parallèles à l'axe X1.Two latches 10 and 11 are respectively articulated around two shafts 12a and 12b fixed on the eccentric 4 and each defining a geometric axis X 10 , X 11 of rotation a lock 10 or 11 with respect to the eccentric 4. The axes X 10 and X 11 are parallel to the axis X 1.

Une couronne d'entraînement 13 est disposée autour de chaque disque d'entraînement 8, au même niveau le long de l'axe X1. En d'autres termes, chaque couronne d'entraînement 13 entoure radialement un disque d'entraînement 8 en s'étendant autour de son bord radial externe 82 et chaque lame de la ratière comprend à la fois un disque d'entraînement 8 et une couronne d'entraînement 13.A drive ring 13 is disposed around each drive disk 8 at the same level along the axis X 1 . In other words, each drive ring 13 radially surrounds a drive disk 8 extending around its outer radial edge 82 and each blade of the dobby comprises both a drive disk 8 and a crown Training 13.

Dans la présente description, les adjectifs « axial », « radial », « centripète » et « centrifuge » et les adverbes « axialement », « radialement » et « diamétralement » s'entendent par rapport à l'axe X1, à moins qu'il en soit précisé autrement. En particulier, une direction radiale est perpendiculaire à l'axe X1.In the present description, the adjectives "axial", "radial", "centripetal" and "centrifugal" and the adverbs "axially", "radially" and "diametrically" refer to the axis X 1 , unless that it be stated otherwise. In particular, a radial direction is perpendicular to the axis X 1 .

La couronne 13 et le disque 8 peuvent avoir la même épaisseur axiale, ou des épaisseurs axiales comparables, sensiblement égale à la différence entre la division, de l'ordre de 12 mm, et l'épaisseur de l'excentrique 4, au jeu près.The ring 13 and the disk 8 may have the same axial thickness, or comparable axial thicknesses, substantially equal to the difference between the division, of the order of 12 mm, and the thickness of the eccentric 4, with the clearance .

Le bord périphérique et radial interne 132 de chaque couronne 13 est pourvu de quatre encoches 133a, 133b, 133c et 133d qui sont destinées à coopérer sélectivement avec les verrous 10 et 11 et sont ménagées dans l'épaisseur ou la tranche de la couronne 13. Chaque encoche 133a à 133d a une forme globalement triangulaire.The peripheral and internal radial edge 132 of each ring 13 is provided with four notches 133a, 133b, 133c and 133d which are intended to cooperate selectively with the bolts 10 and 11 and are formed in the thickness or the edge of the ring 13. Each notch 133a to 133d has a generally triangular shape.

Les encoches 83a et 83c sont diamétralement opposées, de même que les encoches 83b et 83d, les encoches 133a et 133c et les encoches 133b et 133d.The notches 83a and 83c are diametrically opposed, as are the notches 83b and 83d, the notches 133a and 133c and the notches 133b and 133d.

Les différentes couronnes d'entraînement 13, qui sont planes et s'étendent parallèlement les unes aux autres le long de l'arbre 1, sont sépares par des entretoises 14 et assemblées par des tirants 14a, de sorte qu'elles constituent un ensemble rigide ou berceau qui peut être entraîné en rotation alternée autour de l'axe X1 par un mécanisme approprié, de type mécanique ou électrique qui est disposé hors de la zone où sont constituées les lames, par exemple au voisinage d'une extrémité de l'arbre 1. Chaque couronne 13 a donc un mouvement de rotation alternative autour de l'axe X1, ce mouvement étant représenté par les flèches F13, de même sens que la flèche F8, et F'13, de sens contraire à la flèche F8, et ayant une amplitude angulaire de 60°.The various drive rings 13, which are flat and extend parallel to each other along the shaft 1, are separated by spacers 14 and assembled by tie rods 14a, so that they constitute a rigid assembly or cradle which can be rotated alternately about the axis X 1 by a suitable mechanism, mechanical or electrical type which is disposed outside the area where the blades are formed, for example in the vicinity of one end of the 1. Each ring 13 thus has an alternating rotation movement about the axis X 1 , this movement being represented by the arrows F 13 , in the same direction as the arrow F 8 , and F '13 , in a direction opposite to the arrow F 8 , and having an angular amplitude of 60 °.

Les verrous 10 et 11 sont disposés dans un espace annulaire E défini entre les bords périphériques respectifs 82 et 132 du disque d'entraînement 8 et de la couronne d'entraînement 13. Cet espace annulaire débouche au niveau des deux faces axiales du disque 8 et des deux faces axiales de la couronne 13. A titre illustratif, l'espace E est identifié comme une zone ombrée à la figure 2 uniquement.The locks 10 and 11 are arranged in an annular space E defined between the respective peripheral edges 82 and 132 of the drive disk 8 and the drive ring 13. This annular space opens at the two axial faces of the disk 8 and of the two axial faces of the crown 13. By way of illustration, the space E is identified as a shaded area at the figure 2 only.

Le verrou 10 comprend deux pattes 101 et 102 qui s'étendent à partir d'un corps annulaire 103 monté autour de l'arbre 12a. L'extrémité 104 de la patte 101 est destinée à être sélectivement engagée dans l'une des ouvertures 83a et 83c, alors que l'extrémité 105 de la patte 102 est destinée à être sélectivement engagée dans l'une des encoches 133a et 133c. Le verrou 10 comprend également une patte de commande 106 destinée à coopérer avec l'un de deux basculeurs identiques 15 et 16 articulés sur la couronne d'entraînement 13. Les parties constitutives du verrou 11 portent les mêmes références que celles du verrou 10 augmentées de 10. Le verrou 11 comprend ainsi deux pattes 111 et 112 qui s'étendent à partir d'un corps 113 et se terminent par des extrémités 114 et 115 prévues pour être respectivement sélectivement engagées dans les encoches 83b et 83d, 133b et 133d, alors qu'une patte de commande 116 lui permet d'interagir avec l'un des basculeurs 15 et 16. Les verrous 10 et 11 sont identiques, sauf au niveau des pattes de commande 106 et 116 qui sont prévues pour se superposer dans l'épaisseur axiale de l'espace E.The latch 10 comprises two lugs 101 and 102 which extend from an annular body 103 mounted around the shaft 12a. The end 104 of the tab 101 is intended to be selectively engaged in one of the openings 83a and 83c, while the end 105 of the tab 102 is intended to be selectively engaged in one of the notches 133a and 133c. The latch 10 also comprises a control lug 106 intended to cooperate with one of two identical rockers 15 and 16 hinged to the drive ring 13. The constituent parts of the latch 11 bear the same references as those of the latch 10 increased by 10. The latch 11 thus comprises two lugs 111 and 112 which extend from a body 113 and end with ends 114 and 115 intended to be respectively selectively engaged in the notches 83b and 83d, 133b and 133d, then a control lug 116 allows it to interact with one of the rockers 15 and 16. The bolts 10 and 11 are identical except at the level of the control lugs 106 and 116 which are provided to be superimposed in the thickness axial of the space E.

Chacun des verrous 10 et 11 est prévu pour être en prise soit avec le disque d'entraînement 8, soit avec la couronne d'entraînement 13, les deux verrous 10 et 11 étant simultanément en prise avec le même élément d'entraînement.Each of the latches 10 and 11 is designed to be engaged with either the drive disk 8 or with the drive ring 13, the two latches 10 and 11 being simultaneously engaged with the same drive element.

Le basculeur 15 est articulé sur un arbre 17a traversant de part en part la couronne 13. Le basculeur 15 est formé par l'assemblage de deux plaques 15a et 15b reliées entre elles par deux entretoises 15c et 15d. L'entretoise 15c est située radialement à l'extérieur de la couronne 13, c'est-à-dire relie les plaques 15a et 15b au-delà du bord périphérique et radial externe 137 de la couronne 13 par rapport à l'axe X1. L'entretoise 15d relie les plaques 15a et 15b sur l'intérieur de la couronne 13, c'est-à-dire au voisinage de son bord radial interne 132. Une encoche 135 est prévue dans le bord radial interne 132 pour y loger l'entretoise 15d. Par ailleurs, les plaques 15a et 15b sont chacune pourvue d'un crochet 15e, ces crochets étant pliés l'un vers l'autre de façon à définir ensemble un pontet 15f qui s'étend entre les plaques 15a et 15b.The rocker 15 is articulated on a shaft 17a passing right through the ring 13. The rocker 15 is formed by the assembly of two plates 15a and 15b interconnected by two spacers 15c and 15d. The spacer 15c is located radially outside the ring 13, that is to say connects the plates 15a and 15b beyond the peripheral outer radial edge 137 of the ring 13 with respect to the X axis. 1 . The spacer 15d connects the plates 15a and 15b to the inside of the ring 13, that is to say in the vicinity of its internal radial edge 132. A notch 135 is provided in the internal radial edge 132 to accommodate spacer 15d. Furthermore, the plates 15a and 15b are each provided with a hook 15e, these hooks being folded towards each other so as to define together a bridge 15f which extends between the plates 15a and 15b.

Le basculeur 15 est monté en chape autour d'une partie de la couronne 13, les plaques 15a et 15b étant disposées sur les deux faces axiales opposées de la couronne d'entraînement 13. Ceci permet que chacune des entretoises 15c et 15d ait une épaisseur axiale e15 sensiblement égale à celle de la couronne 13.The rocker 15 is mounted as a yoke around a portion of the ring 13, the plates 15a and 15b being disposed on the two opposite axial faces of the drive ring 13. This allows each of the spacers 15c and 15d to have a thickness axial e 15 substantially equal to that of the ring 13.

Le basculeur 16 est identique au basculeur 15 et articulé sur la couronne d'entraînement 13 autour d'un deuxième arbre 17b. On note 16c et 16d les entretoises du basculeur 16 qui sont respectivement analogues aux entretoises 15c et 15d. Les basculeurs 15 et 16 sont montés sur la couronne 13 de façon que les entretoises 15c et 16c, d'une part, 15d et 16d, d'autre part, sont diamétralement opposées.The rocker 16 is identical to the rocker 15 and articulated on the drive ring 13 around a second shaft 17b. 16c and 16d are the spacers of the rocker 16 which are respectively similar to the spacers 15c and 15d. The tilters 15 and 16 are mounted on the ring 13 so that the spacers 15c and 16c, on the one hand, 15d and 16d, on the other hand, are diametrically opposed.

Deux butées 18 et 19 sont montées sur l'excentrique 4, du même côté que les arbres 12a et 12b. Par ailleurs, deux leviers de renvoi 20 et 21 sont respectivement montés sur l'excentrique 4, du même côté que les arbres 12a et 12b et logés dans l'espace E, respectivement à proximité des verrous 10 et 11. En pratique, les leviers de renvoi 20 et 21 sont respectivement articulés autour de deux arbres 22a et 22b parallèles aux arbres 12a et 12b. On note respectivement X20 et X21 les axes d'articulation des leviers 20 et 21 par rapport à l'excentrique 4.Two stops 18 and 19 are mounted on the eccentric 4 on the same side as the shafts 12a and 12b. Moreover, two return levers 20 and 21 are respectively mounted on the eccentric 4, on the same side as the shafts 12a and 12b and housed in the space E, respectively close to the bolts 10 and 11. In practice, the levers 20 and 21 are respectively articulated around two shafts 22a and 22b parallel to the shafts 12a and 12b. X 20 and X 21 respectively denote the axes of articulation of the levers 20 and 21 with respect to the eccentric 4.

Le levier 20 comprend un premier bras 201 en appui contre la patte 101 du verrou 10, du côté de cette patte opposée au disque d'entraînement 8. Le levier 20 comprend également un deuxième bras 202 soumis à un effort élastique E23 exercé par un ressort 23 en appui contre la butée 18. L'effort E23 est transmis au verrou 10 sous la forme d'un effort E20 exercé par le bras 201 du levier 20, cet effort E20 ayant pour effet de plaquer le bras 201 contre le bord radial externe 82 du disque d'entraînement 8. De la même façon, un ressort 24 en appui sur la butée 19 exerce sur le levier 21 un effort élastique E24 que le levier 21 transmet au verrou 11 sous la forme d'un effort E2, qui plaque la patte 111 du verrou 11 la plus proche du disque d'entraînement 8 contre le bord radial externe 82 du disque d'entraînement 8.The lever 20 comprises a first arm 201 resting against the lug 101 of the latch 10, on the side of this lug opposite the drive disk 8. The lever 20 also comprises a second arm 202 subjected to an elastic force E 23 exerted by a spring 23 bearing against the stop 18. The force E 23 is transmitted to the latch 10 in the form of a force E 20 exerted by the arm 201 of the lever 20, the force E 20 having the effect of pressing the arm 201 against the external radial edge 82 of the drive disk 8. In the same way, a spring 24 bearing on the stop 19 exerts on the lever 21 an elastic force E 24 that the lever 21 transmits to the latch 11 in the form of a E 2 force , which plate the tab 111 of the latch 11 closest to the drive disc 8 against the outer radial edge 82 of the drive disc 8.

Par ailleurs, le basculeur 15 est soumis à l'action d'un ressort 25 disposé dans un logement 136 constitué par un orifice ménagé à travers la couronne d'entraînement 13. Le pontet 15f est également engagé dans le logement 136 et subit un effort élastique E25 exercé par le ressort 25, cet effort élastique ayant tendance à plaquer l'entretoise 15d contre le fond de l'encoche 135, c'est-à-dire à éloigner cette entretoise 15d des pattes de commande 106 et 116 des verrous 10 et 11.Furthermore, the rocker 15 is subjected to the action of a spring 25 disposed in a housing 136 constituted by a hole formed through the drive ring 13. The bridge 15f is also engaged in the housing 136 and is under a stress elastic E 25 exerted by the spring 25, this elastic force tending to press the spacer 15d against the bottom of the notch 135, that is to say to move this spacer 15d control tabs 106 and 116 locks 10 and 11.

Le basculeur 16 est également monté sur la couronne d'entraînement 13 avec interposition d'un ressort 26 qui exerce un effort E26 tendant à plaquer son entretoise interne 16d dans le fond de l'encoche prévue à cet effet sur le bord radial interne 132 de la couronne d'entraînement 13.The rocker 16 is also mounted on the drive ring 13 with the interposition of a spring 26 which exerts a force E 26 tending to press its inner spacer 16d in the bottom of the notch provided for this purpose on the internal radial edge 132 of the drive gear 13.

La ratière R comprend également deux leviers oscillants 30 et 31 articulés chacun autour d'un arbre 32a ou 32b qui est fixe par rapport au bâti de la ratière. On note respectivement X30 et X31 les axes d'articulation des leviers oscillants 30 et 31 qui sont définis par les arbres 32a et 32b. Le levier oscillant 30 est équipé d'un galet 33 prévu pour rouler sur une portion 137a du bord périphérique radial externe 137 de la couronne d'entraînement 13, ainsi que sur l'entretoise 15c du basculeur 15, en fonction de l'armure. De la même façon, le levier oscillant 31 est équipé d'un galet 34 prévu pour rouler sur une portion 137b du bord 137 et sur l'entretoise externe 16c du basculeur 16, en fonction de l'armure.The dobby R also comprises two oscillating levers 30 and 31 each articulated around a shaft 32a or 32b which is fixed relative to the frame of the dobby. X 30 and X 31 respectively denote the axes of articulation of the oscillating levers 30 and 31 which are defined by the shafts 32a and 32b. The oscillating lever 30 is equipped with a roller 33 designed to roll on a portion 137a of the outer radial peripheral edge 137 of the drive ring 13, as well as on the spacer 15c of the rocker 15, depending on the weave. In the same way, the oscillating lever 31 is equipped with a roller 34 designed to roll on a portion 137b of the edge 137 and on the outer spacer 16c of the rocker 16, depending on the armor.

Un dispositif de sélection 35, qui comprend un électroaimant 36 et un doigt de sélection 37, est prévu pour venir sélectivement en engagement avec l'extrémité 30a du levier 30 opposée au galet 33 et l'extrémité 31 a du levier 31 opposée au galet 34. Le dispositif de sélection 35 permet de maintenir en position l'un ou l'autre des leviers 30 et 31 et de maintenir le galet 33 ou 34 du levier 30 ou 31 sur lequel il agit éloigné du basculeur 15 ou 16 adjacent.A selection device 35, which comprises an electromagnet 36 and a selection finger 37, is provided to come into selective engagement with the end 30a of the lever 30 opposite the roller 33 and the end 31a of the lever 31 opposite the roller 34. The selection device 35 makes it possible to hold one or the other of the levers 30 and 31 in position and to hold the roller 33 or 34 of the lever 30 or 31 on which it acts away from the rocker 15 or 16 adjacent.

Des ressorts non représentés exercent sur les leviers 30 et 31 des efforts élastiques E30, E31 qui tendent à faire tourner ces leviers oscillants autour des axes X30 et X31 dans un sens tel que les galets 33 et 34 sont déplacés en direction de l'axe X1 et que les extrémités 30a et 31 a sont éloignées de cet axe.Unrepresented springs exert on the levers 30 and 31 elastic forces E 30 , E 31 which tend to rotate these oscillating levers about the axes X 30 and X 31 in a direction such that the rollers 33 and 34 are moved in the direction of the axis X 1 and that the ends 30a and 31a are remote from this axis.

Le disque d'entraînement 8 constitue un premier élément d'entraînement en rotation de l'excentrique 4, avec un mouvement de rotation F8 dans un seul sens, à vitesse constante. La couronne d'entraînement 13 constitue un deuxième élément d'entraînement de l'excentrique 4, avec un mouvement de rotation alternée F13 et F'13. La rotation des éléments 4, 8 et 13 a lieu autour de l'axe X1.The drive disc 8 constitutes a first element for rotating the eccentric 4, with a rotation movement F 8 in one direction, at a constant speed. The driving ring 13 constitutes a second drive element of the eccentric 4, with an alternating rotational movement F 13 and F '13 . The rotation of the elements 4, 8 and 13 takes place around the axis X 1 .

Le fonctionnement de la ratière R est le suivant : En fonction de l'armure, la position de chacun des cadres 3 est définie pour chaque duite, c'est-à-dire chaque insertion d'un fil de trame. D'une duite à la suivante, un cadre peut être amené à changer d'une position supérieure PSUP à une position inférieure PINF en passant par une position intermédiaire ou médiane PMED, ou réciproquement, ce qu'on considère comme un mouvement de base, ou mouvement principal. Lorsque le cadre conserve une position supérieure, avec un mouvement de faible amplitude, il effectue un mouvement secondaire entre la position supérieure PSUP et une position P'SUP située au dessus de la position médiane PMED et proche de la position supérieure. Lorsque le cadre conserve une position inférieure, il effectue un mouvement secondaire entre la position inférieure PINF et une position P'INF située au dessous de la position médiane PMED et proche de la position inférieure. La différence de hauteur entre les positions PINF et P'INF est inférieure à la moitié de la différence de hauteur entre les positions PSUP et PINF. The operation of the dobby R is as follows: Depending on the armor, the position of each of the frames 3 is defined for each pick, that is to say each insertion of a weft yarn. From one pick to the next, a frame can be made to change from an upper position P SUP to a lower position P INF through an intermediate or median position P MED , or vice versa, which is considered a movement basic, or main movement. When the frame maintains a higher position, with a low amplitude movement, it performs a secondary movement between the upper position P SUP and a position P ' SUP located above the median position P MED and close to the upper position. When the frame maintains a lower position, it performs a secondary movement between the lower position P INF and a position P ' INF located below the median position P MED and close to the lower position. The difference in height between the positions P INF and P ' INF is less than half the difference in height between the positions P SUP and P INF.

Si le cadre 3 doit conserver une position supérieure ou une position inférieure sur au moins trois duites, le mouvement secondaire a lieu sur plus de 360° d'angle métier.If the frame 3 must maintain a higher position or a lower position on at least three picks, the secondary movement takes place over more than 360 ° of craft angle.

Le mouvement de base d'un cadre de lisses 3est une portion de mouvement sinusoïdal de période égale à 720 ° d'angle métier, entre la position PINF et la position Psup ou réciproquement. Ce mouvement est obtenu par la conversion d'un mouvement d'entraînement de l'excentrique 4 par le disque d'entraînement 8 qui est animé d'un mouvement de rotation uniforme dans un sens, de période égale à 720° d'angle métier. Ceci est représenté par la portion de courbe en trait plein s'étendant entre 720 ° et 1800 ° d'angle métier θ à la figure 5 et qui représente la position P d'un cadre en fonction de l'angle métier, lors de ses mouvements selon la flèche F2- Sur cette figure huit duites N1 à N8 sont représentées.The basic movement of a heald frame 3is a portion of sinusoidal motion with a period equal to 720 ° of working angle, between the position P INF and the position P su p or vice versa. This movement is obtained by the conversion of a driving movement of the eccentric 4 by the drive disc 8 which is driven by a uniform rotational movement in one direction, with a period equal to 720 ° of work angle . This is represented by the portion of curve in solid line extending between 720 ° and 1800 ° of angle of the trade θ to the figure 5 and which represents the position P of a frame according to the angle of the craft, during its movements according to the arrow F 2 - In this figure eight picks N 1 to N 8 are shown.

Un mouvement secondaire du cadre de lisses 3 peut être obtenu lorsque l'excentrique 4 est entraîné par la couronne 13, avec un mouvement de rotation alternative, ce qui correspond à la portion de courbe représentée en trait plein entre les angles métier 360 et 720 à la figure 5. Ce mouvement secondaire correspond également à la portion de courbe représentée en trait plein entre les angles métier 1800° et 2160° sur cette figure. La portion de courbe entre les angles métiers 360° et 720° correspond à un mouvement secondaire se produisant à proximité de la position supérieure PSUP d'un cadre que le cadre atteint à la duite N2 et conserve à la duite N3, alors que la portion de courbe entre les angles métier 1800 et 2160 correspond au mouvement secondaire se produisant à proximité de la position inférieure PINF que la cadre atteint à la duite N6 et conserve à la duite N7 . Le mouvement secondaire entre les angles métier 360° et 720° a lieu entre les positions PSUP et P'SUP, avec une amplitude égale à la différence de hauteur de ces positions. Le mouvement secondaire entre les angles 1800° et 2160° a lieu entre les positions PINF et P'INF, avec une amplitude égale à la différence de hauteur entre ces positions. Ces deux mouvements secondaires sont obtenus selon que les verrous 10 et 11 sont en prise avec les encoches 133a et 133d, d'une part, ou avec les encoches 133b et 133c, d'autre part.A secondary movement of the heald frame 3 can be obtained when the eccentric 4 is driven by the ring 13, with an alternating rotational movement, which corresponds to the curve portion shown in solid lines between the angles of occupation 360 and 720 to the figure 5 . This secondary movement also corresponds to the curve portion shown in solid line between the angles 1800 ° and 2160 ° in this figure. The portion of the curve between the angles 360 ° and 720 ° corresponds to a secondary movement occurring near the upper position P SUP of a frame that the frame reaches at the pick N 2 and retains the pick N 3 , then that the portion of the curve between the angles of occupation 1800 and 2160 corresponds to the secondary movement occurring near the lower position P INF than the frame reached at the pick N 6 and kept at the pick N 7 . The secondary movement between the 360 ° and 720 ° occupation angles takes place between the positions P SUP and P ' SUP , with an amplitude equal to the difference in height of these positions. The secondary movement between the angles 1800 ° and 2160 ° takes place between the positions P INF and P ' INF , with an amplitude equal to the difference in height between these positions. These two secondary movements are obtained according to whether the locks 10 and 11 are engaged with the notches 133a and 133d, on the one hand, or with the notches 133b and 133c, on the other hand.

L'ensemble ou berceau constitué des différentes couronnes d'entraînement 13 solidarisées entre elles est commandé de telle sorte que le mouvement secondaire d'un cadre 3 entraîné par l'une de ces couronnes 13 est une portion de mouvement sinusoïdal de fréquence quatre fois plus élevée que le mouvement de base et d'amplitude égale à 1/16ème de l'amplitude de mouvement de base, ce qui correspond à une oscillation de l'ensemble des couronnes 13 d'amplitude égale à 60°.The assembly or cradle constituted by the various driving rings 13 secured to each other is controlled so that the secondary movement of a frame 3 driven by one of these rings 13 is a portion of sinusoidal frequency movement four times as much. high than the base movement and amplitude equal to 1/16 th of the base movement amplitude, which corresponds to an oscillation of the set of crowns 13 of amplitude equal to 60 °.

Selon des variantes de l'invention, l'amplitude angulaire du mouvement des couronnes 13 est comprise entre 30° et 120°, de préférence entre 45° et 90°, la valeur de 60° s'avérant très avantageuse. Ainsi, sur 360° d'angle métier, le mouvement de la couronne 13 a une amplitude angulaire réduite par rapport au mouvement de rotation complète du disque 8. Ceci a pour conséquence que l'amplitude de mouvement selon la flèche F2 du cadre 3 entraîné par la couronne 13 est réduite par rapport à l'amplitude de ce mouvement lorsque le cadre est entraîné par le disque 8. En particulier, lorsqu'il est entraîné par la couronne 13, le cadre 3 reste au voisinage de sa position de fin de course haute, c'est-à-dire sa position supérieure PSUP, ou au voisinage de sa position de fin de course basse PINF, c'est-à-dire sa position inférieure. Ainsi, dans l'exemple des figures, la différence de hauteur entre PSUP et P'SUP ou entre PINF et P'INF est égale à 1/l6eme de la différence de hauteur entre PSUP et PINF According to variants of the invention, the angular amplitude of the movement of the rings 13 is between 30 ° and 120 °, preferably between 45 ° and 90 °, the value of 60 ° proving very advantageous. Thus, over 360 ° of the craft angle, the movement of the ring 13 has a reduced angular amplitude with respect to the complete rotational movement of the disk 8. This has the consequence that the amplitude of movement according to the arrow F 2 of the frame 3 driven by the ring 13 is reduced with respect to the amplitude of this movement when the frame is driven by the disk 8. In particular, when it is driven by the ring 13, the frame 3 remains at near its upper end position, that is to say its upper position P SUP , or in the vicinity of its lower end position P INF , that is to say, its lower position. Thus, in the example of the figures, the difference in height between P SUP and P ' SUP or between P INF and P' INF is equal to 1/16 of the difference in height between P SUP and P INF

En variante, la fréquence du mouvement secondaire des cadres 3 peut être un autre multiple de quatre fois la fréquence du mouvement de base des cadres 3, par exemple égal à huit fois ou douze fois cette fréquence.As a variant, the frequency of the secondary movement of the frames 3 may be another multiple of four times the frequency of the basic movement of the frames 3, for example equal to eight times or twelve times this frequency.

La figure 5 montre en traits pointillés la courbe de vitesse instantanée V d'un cadre animé du mouvement représenté par la courbe en trait plein et en traits d'axe la courbe d'accélération instantanée A de ce cadre. Le mouvement représenté par la courbe de position P est un mouvement sans arrêt, l'accélération d'un cadre étant non nulle lorsque sa vitesse est nulle.The figure 5 shows in dotted lines the instantaneous velocity curve V of an animated frame of the movement represented by the solid line curve and in axial lines the instantaneous acceleration curve A of this frame. The movement represented by the position curve P is a non-stop movement, the acceleration of a frame being non-zero when its speed is zero.

Tous les 360° d'angle métier, il existe une position de la lame de la ratière où le cadre 3 est dans l'une des positions supérieure PSUP ou inférieure PINF de sa course selon le mouvement de base, et où deux encoches du disque 8 et deux encoches de la couronne 13 se trouvent en regard des verrous 10 et 11, alors que le basculeur 15 ou 16 est en regard des pattes 106, 116. Cette position de la lame, qui correspond à un point de transfert, est dite position de transfert. Il existe également une zone de transfert, définie sur une amplitude angulaire de plus ou moins 15° d'angle métier autour de la position de transfert, zone dans laquelle la commutation de mouvement de l'excentrique 4 peut avoir lieu entre un mouvement entraîné par le disque 8 et un mouvement entraîné par la couronne 13, ou réciproquement. On note que, dans les positions de la lame où le transfert de mouvement peut avoir lieu, les éléments 8 et 13 ont les mêmes vitesses angulaires instantanées et les mêmes accélérations angulaires instantanées par rapport à l'axe X1. Dans les positions de transferts, les éléments d'entraînement 8 et 13 sont animés d'un mouvement de rotation dans le même sens, grâce au mouvement secondaire de fréquence 4 fois supérieure à celle du mouvement de base. Il n'existe donc pas de discontinuité de mouvement, de vitesse et d'accélération du cadre 3 aux points de transferts, même s'il y a eu commutation.All 360 ° of the craft angle, there is a position of the dobby blade where the frame 3 is in one of the upper positions P SUP or lower P INF of its stroke according to the basic movement, and where two notches of the disc 8 and two notches of the crown 13 are opposite the latches 10 and 11, while the rocker 15 or 16 is opposite the tabs 106, 116. This position of the blade, which corresponds to a transfer point, is called transfer position. There is also a transfer zone, defined on an angular amplitude of plus or minus 15 ° of the angle around the transfer position, in which zone the movement switching of the eccentric 4 can take place between a movement driven by the disk 8 and a movement driven by the ring 13, or vice versa. Note that in the positions of the blade where the transfer of motion can take place, the elements 8 and 13 have the same instantaneous angular velocities and the same instantaneous angular accelerations with respect to the axis X 1 . In the transfer positions, the driving elements 8 and 13 are driven in a rotation movement in the same direction, thanks to the secondary frequency movement 4 times greater than that of the base movement. There is therefore no discontinuity of movement, speed and acceleration of the frame 3 at the transfer points, even if there has been switching.

Dans la configuration de la figure 1, les extrémités 104 et 114 des branches 101 et 111 des verrous 10 et 11 sont engagées respectivement dans les encoches 83c et 83b du disque d'entraînement 8, de sorte que l'excentrique 4 tourne avec l'arbre 1, dans le sens de la flèche F8, et le cadre 3 est animé d'un mouvement de base. Les extrémités 104 et 114 des pattes 101 et 102 reposent par leurs tranches respectives sur les bords les plus courts des encoches 83c et 83d.In the configuration of the figure 1 the ends 104 and 114 of the branches 101 and 111 of the latches 10 and 11 are respectively engaged in the notches 83c and 83b of the drive disc 8, so that the eccentric 4 rotates with the shaft 1, in the direction of the arrow F 8 , and the frame 3 is animated by a basic movement. The ends 104 and 114 of the tabs 101 and 102 rest at their respective edges on the shorter edges of the notches 83c and 83d.

Par ailleurs, du fait du mouvement alternatif de la couronne d'entraînement 13, les galets 33 et 34 roulent contre les portions 137a et 137b du bord externe 137, ou une partie de ces portions, ce qui permet d'obtenir un nivelage des leviers 30 et 31 en les faisant pivoter à l'encontre des efforts E30 et E31. Dans cette position des leviers le dispositif de sélection 35 peut retenir l'extrémité 30a ou 31 a de l'un d'entre eux en fonction de l'alimentation électrique de l'électroaimant 36 qui dépend de l'armure, pour provoquer ou non la commutation des verrous 10 et 11. Dans l'exemple de la figure 1, les leviers 30 et 31 sont nivelés et le dispositif de sélection 35 bloque le levier 31, sans interagir avec le levier 30.Moreover, because of the reciprocating movement of the driving ring 13, the rollers 33 and 34 roll against the portions 137a and 137b of the outer edge 137, or a portion of these portions, which makes it possible to obtain a leveling of the levers 30 and 31 by rotating them against the efforts E 30 and E 31 . In this position of the levers the selection device 35 can retain the end 30a or 31a of one of them depending on the power supply of the electromagnet 36 which depends on the armor, to cause or not switching locks 10 and 11. In the example of the figure 1 the levers 30 and 31 are leveled and the selection device 35 blocks the lever 31 without interacting with the lever 30.

La poursuite des mouvements de rotation des éléments 8 et 13, respectivement dans le sens des flèches F8 et F13, permet d'atteindre une configuration où le galet 33 du levier 30, qui n'est pas soumis à l'action du doigt de sélection 37 mais soumis à l'effort E30, vient rouler sur l'entretoise extérieure 15c du basculeur 15 et exerce sur celui-ci un effort centripète E33 qui fait pivoter le basculeur 15 autour de l'axe 17a dans le sens de la flèche F15. Ceci a pour effet de déplacer l'entretoise 15d du basculeur 15 qui exerce alors, dans la position de transfert de la lame et sur les pattes de commande 106 et 116, un effort centripète E15 qui correspond à la transmission de l'effort E33. Cette action du basculeur 15 sur les verrous 10 et 11 a pour effet de les faire pivoter respectivement autour des axes X10 et X11 dans un sens de dégagement des extrémités 104 et 114 par rapport aux encoches 83c et 83b, tout en engageant les extrémités 105 et 115 respectivement dans les encoches 133c et 133b. En d'autres termes, l'action du levier 30 sur le basculeur 15 permet de désolidariser l'excentrique 4 par rapport au disque d'entraînement 8 et de le solidariser à la couronne d'entraînement 13, de sorte que le cadre 3 est ensuite animé du mouvement secondaire. L'action du basculeur 15 sur les verrous 10 et 11 a lieu à l'encontre des efforts E23 et E24.Continuing the rotational movements of the elements 8 and 13, respectively in the direction of the arrows F 8 and F 13 , makes it possible to reach a configuration where the roller 33 of the lever 30, which is not subjected to the action of the finger 37 but subject to the force E 30 , is rolled on the outer spacer 15c of the rocker 15 and exerts on it a centripetal force E 33 which pivots the rocker 15 about the axis 17a in the direction of the arrow F 15 . This has the effect of moving the spacer 15d of the rocker 15 which then exerts, in the transfer position of the blade and on the control lugs 106 and 116, a centripetal force E 15 which corresponds to the transmission of the force E 33 . This action of the rocker 15 on the bolts 10 and 11 has the effect of pivoting respectively about the axes X 10 and X 11 in a direction of release of the ends 104 and 114 relative to the notches 83c and 83b, while engaging the ends 105 and 115 respectively in the notches 133c and 133b. In other words, the action of the lever 30 on the rocker 15 makes it possible to separate the eccentric 4 with respect to the drive disc 8 and to secure it to the drive ring 13, so that the frame 3 is then animated secondary movement. The action of the rocker 15 on the bolts 10 and 11 takes place against the forces E 23 and E 24 .

Cette configuration où la ratière se trouve à un point de transfert est représentée aux figures 2 et 3.This configuration where the dobby is at a transfer point is shown in figures 2 and 3 .

L'action du levier 30 sur le basculeur 15, c'est-à-dire l'application de l'effort E33, est maintenue dans toute la zone de transfert, soit plus ou moins 15° autour du point de transfert. Les efforts E33 et E15 sont ainsi maintenus, ce qui garantit un dégagement efficace des extrémités 104 et 114 hors des encoches du disque 8 lors de la mise en prise ou le maintien en prise des verrous 10 et 11 dans les encoches 133c et 133d.The action of the lever 30 on the rocker 15, that is to say the application of the force E 33 , is maintained throughout the transfer zone, more or less 15 ° around the transfer point. Efforts E 33 and E 15 are thus maintained, which ensures effective clearance of the ends 104 and 114 out of the notches of the disc 8 when engaging or maintaining the latches 10 and 11 in the notches 133c and 133d .

On parvient alors dans la configuration de la figure 4 où l'excentrique 4 est entraîné par la couronne 4, à travers les verrous 10 et 11.We then arrive in the configuration of the figure 4 where the eccentric 4 is driven by the ring 4, through the locks 10 and 11.

Lorsque le métier parcourt 360° d'angle métier par rapport à la configuration des figures 2 et 3, la couronne 13 poursuit son mouvement de rotation dans le sens de la flèche F13, puis elle adopte un mouvement de rotation inversé dans le sens de la flèche F'13 et à nouveau le mouvement de rotation dans le sens de la flèche F13. Ainsi, après 360° d'angle métier, on retrouve une position de transfert de la lame et il existe une nouvelle possibilité de commutation des verrous 10 et 11, grâce aux leviers oscillants 30 et 31 et à leur action sur l'un ou l'autre des basculeurs 15 et 16. Si le galet 33 ou 34 du levier 30 ou 31 à proximité duquel se trouvent les verrous 10 et 11 exerce sur le basculeur adjacent 15 ou 16 un effort centripète E33, les verrous 10 et 11 restent en prise avec la couronne d'entraînement 13 et le cadre de lisses 3 conserve un mouvement secondaire de faible amplitude. Au contraire, si le levier oscillant n'agit pas sur le basculeur adjacent, les verrous 10 et 11 viennent automatiquement en prise avec le disque d'entraînement 8 sous l'effet des efforts élastiques E23 et E24 et le cadre 3 est à nouveau entraîné par le disque 8 pour passer d'une position supérieure à une position inférieure, ou réciproquement.When the trade travels 360 ° of business angle with respect to the configuration of figures 2 and 3 , the ring 13 continues its rotational movement in the direction of the arrow F 13 , then it adopts an inverted rotational movement in the direction of the arrow F '13 and again the rotational movement in the direction of the arrow F 13 . Thus, after 360 ° of the working angle, there is a transfer position of the blade and there is a new possibility of switching locks 10 and 11, thanks to the oscillating levers 30 and 31 and their action on one or the other. other of the rockers 15 and 16. If the roller 33 or 34 of the lever 30 or 31 near which are the locks 10 and 11 exerts on the adjacent rocker 15 or 16 a centripetal force E 33 , the latches 10 and 11 remain in position. taken with the drive ring 13 and the heald frame 3 maintains a secondary motion of low amplitude. On the contrary, if the oscillating lever does not act on the adjacent rocker, the bolts 10 and 11 automatically engage with the drive disk 8 under the effect of the elastic forces E 23 and E 24 and the frame 3 is at again driven by the disc 8 to move from a higher position to a lower position, or vice versa.

On note que, dans les configurations d'entraînement mentionnées ci-dessus, les verrous 10 et 11 travaillent en compression pour transmettre le mouvement de l'un des éléments d'entraînement 8 ou 13 vers l'excentrique 4, ce qui assure une durée de vie importante pour la ratière R. Le fait que les galets 33 et 34 roulent sur les portions 137a et 137b du bord externe 137 permet à ce bord d'assurer une fonction de nivelage, comme envisagé dans EP-A-1 382 725 , de sorte que le dispositif de sélection 35 est dimensionné uniquement pour résister aux efforts E30 et E31, sans avoir à déplacer positivement les leviers 30 et 31.Note that, in the drive configurations mentioned above, the latches 10 and 11 work in compression to transmit the movement of one of the driving elements 8 or 13 to the eccentric 4, which ensures a duration The fact that the rollers 33 and 34 roll on the portions 137a and 137b of the outer edge 137 allows this edge to provide a leveling function, as envisaged in FIG. EP-A-1,382,725 , so that the selection device 35 is dimensioned only to withstand the forces E 30 and E 31 , without having to positively move the levers 30 and 31.

En fonctionnement, selon que le cadre 3 accélère ou décélère, les deux verrous 10 et 11 solidarisent alternativement l'excentrique 4 avec l'élément d'entraînement, que cet élément soit le disque 8 ou la couronne 13. Dans une phase de mouvement du cadre 3, un seul verrou 10 ou 11 solidarise l'excentrique 4 avec l'un des éléments d'entraînement 8 ou 13, alors que dans une autre phase de mouvement, c'est l'autre verrou 11 ou 10 qui assure cette fonction de solidarisation.In operation, depending on whether the frame 3 accelerates or decelerates, the two latches 10 and 11 alternately join the eccentric 4 with the drive element, whether this element is the disk 8 or the ring 13. In a phase of movement of the 3, a single latch 10 or 11 secures the eccentric 4 with one of the driving elements 8 or 13, while in another phase of movement, it is the other latch 11 or 10 which provides this function of solidarity.

Dans la configuration de la figure 1, les extrémités 105 et 115 des verrous 10 et 11 sont en appui glissant sur le bord adjacent 132 de la couronne d'entraînement 13. Inversement, dans la configuration de la figure 4, lorsque les verrous 10 et 11 sont en prise avec la couronne 13, les extrémités 104 et 105 sont en appui glissant sur le bord adjacent 82 du disque 8. Ceci a pour effet de faciliter l'engagement des extrémités des pattes des verrous 10 et 11 dans les encoches du bord 82 ou 132 aux points de transfert, en cas de commutation, et de bloquer les verrous en prise avec l'un ou l'autre des éléments d'entraînement 8 ou 13 en dehors des points de transfert.In the configuration of the figure 1 , the ends 105 and 115 of the locks 10 and 11 are slidingly abutting on the adjacent edge 132 of the driving ring 13. Conversely, in the configuration of the figure 4 when the locks 10 and 11 are engaged with the ring 13, the ends 104 and 105 are in sliding abutment on the edge 8. This has the effect of facilitating the engagement of the ends of the tabs of the locks 10 and 11 in the notches of the edge 82 or 132 at the transfer points, in case of switching, and to lock the locks engaged with one or the other of the driving elements 8 or 13 outside the transfer points.

On comprend que la construction des deux éléments d'entraînement que sont le disque 8 et la couronne 13 radialement l'un autour de l'autre, de part et d'autre des verrous 10 et 11 et de l'espace E, permet d'augmenter l'épaisseur axiale des surfaces de contact entre ces verrous et ces éléments d'entraînement, ce qui augmente la résistance mécanique de ces pièces.It is understood that the construction of the two drive elements that are the disk 8 and the ring 13 radially around each other, on both sides of the locks 10 and 11 and the space E, allows to increase the axial thickness of the contact surfaces between these locks and these drive elements, which increases the mechanical strength of these parts.

Les éléments d'entraînement 8 et 13 ont la même épaisseur axiale. En variante, ils peuvent avoir des épaisseurs différentes.The driving elements 8 and 13 have the same axial thickness. Alternatively, they may have different thicknesses.

Selon une variante non représentée de l'invention, les basculeurs 15 et 16 peuvent ne pas agir directement sur les pattes de commande 106 et 116 des verrous 10 et 11 mais sur un coulisseau mobile en translation selon une direction radiale par rapport à l'axe X1 et reçu dans un logement de l'excentrique 4, les extrémités des pattes 106 et 116 étant articulées sur ce coulisseau.According to a not shown variant of the invention, the rockers 15 and 16 may not act directly on the control tabs 106 and 116 of the locks 10 and 11 but on a slide movable in translation in a radial direction relative to the axis X 1 and received in a housing of the eccentric 4, the ends of the tabs 106 and 116 being articulated on the slide.

Dans les deuxième et troisième modes de réalisation représentés respectivement aux figures 7 et 8, les éléments analogues à ceux du premier mode de réalisation portent les mêmes références. Dans ce qui suit, on décrit principalement ce qui distingue ces modes de réalisation du précédent.In the second and third embodiments shown respectively in figures 7 and 8 elements similar to those of the first embodiment bear the same references. In what follows, we mainly describe what distinguishes these embodiments from the previous one.

Dans le mode de réalisation de la figure 7, un seul verrou 10 est utilisé. Il peut être actionné par un basculeur 15 ou son équivalent, non représenté et disposé diamétralement à l'opposé du basculeur 15, sur la couronne d'entraînement 13. Le verrou 10 est pourvu d'une tête 108 présentant deux dents 108a et 108b qui peuvent être sélectivement engagées dans une des deux encoches 83a et équivalente du disque d'entraînement 8 et dans une des deux encoches 133a et équivalente de la couronne d'entraînement 13. Les encoches 83a, 133a et équivalentes sont respectivement ménagées sur le bord radial externe 82 du disque 8 et sur le bord radial interne 132 de la couronne 13. Le verrou 10 est disposé radialement dans un espace E qui s'étend entre le disque 8 et la couronne 13 et il permet de coupler mécaniquement l'excentrique 4 soit au disque 8 soit à la couronne 13.In the embodiment of the figure 7 only one lock 10 is used. It can be actuated by a rocker 15 or its equivalent, not shown and arranged diametrically opposite the rocker 15, on the drive ring 13. The lock 10 is provided with a head 108 having two teeth 108a and 108b which can be selectively engaged in one of the two notches 83a and equivalent of the drive disk 8 and in one of the two notches 133a and equivalent of the drive ring 13. The notches 83a, 133a and equivalent are respectively formed on the outer radial edge 82 of the disk 8 and on the inner radial edge 132 of the ring 13. The latch 10 is disposed radially in a space E which extends between the disk 8 and the ring 13 and it allows to mechanically couple the eccentric 4 is to disc 8 to crown 13.

Une butée 18, un levier 20 et un ressort 23 fonctionnent comme ceux du premier mode de réalisation.A stop 18, a lever 20 and a spring 23 operate as those of the first embodiment.

Dans le mode de réalisation de la figure 8, le verrou 10 est unique et comprend un piston 109 chargé élastiquement par deux ressorts 23 et 24 qui exercent chacun un effort centrifuge E23 ou E24 tendant à engager une portion radiale externe 109a du piston 109 dans l'une de deux encoches 133a et équivalente ménagées sur le bord radial interne 132 de la couronne d'entraînement 133. Le bord radial externe 82 du disque d'entraînement est pourvu de deux encoches 83a et équivalente de réception sélective d'une portion radiale interne 1 09b du piston 109. Un coulisseau 15 et son équivalent, non représenté et diamétralement opposé par rapport au coulisseau 15, sont disposés dans la couronne 13 avec une possibilité de translation selon une direction radiale et permettent d'exercer sélectivement sur le piston 109 un effort d'engagement de la portion 109b dans l'encoche 83a ou l'encoche équivalente.In the embodiment of the figure 8 the lock 10 is unique and comprises a piston 109 loaded elastically by two springs 23 and 24 which each exert a force centrifugal E 23 or E 24 tending to engage an outer radial portion 109a of the piston 109 in one of two notches 133a and equivalent formed on the inner radial edge 132 of the drive ring 133. The outer radial edge 82 of the disc The drive is provided with two notches 83a and an equivalent selective receiving of an inner radial portion 109b of the piston 109. A slider 15 and its equivalent, not shown and diametrically opposed with respect to the slider 15, are arranged in the ring 13 with a possibility of translation in a radial direction and allow to exercise selectively on the piston 109 a force of engagement of the portion 109b in the notch 83a or the equivalent notch.

Ainsi, sans action sur le coulisseau 15, le verrou 10 est craboté sur la couronne d'entraînement 13 et, lorsqu'on souhaite solidariser en rotation le verrou 10 avec le disque 8, il suffit de laisser le galet 33 ou équivalent de l'un des leviers oscillants 30 et équivalent agir sur le coulisseau 15 ou équivalent à proximité duquel se trouve le verrou 10.Thus, without action on the slider 15, the latch 10 is clutched on the drive ring 13 and, when it is desired to lock the latch 10 in rotation with the disk 8, it suffices to leave the roller 33 or equivalent of the one of the oscillating levers 30 and equivalent acting on the slider 15 or equivalent near which the lock 10 is located.

Comme précédemment, le verrou 10 est disposé dans un espace E qui s'étend radialement entre les bords externe 82 et interne 132 des éléments d'entraînement 8 et 13 et la couronne d'entraînement 13 est disposée radialement autour du disque d'entraînement 8.As previously, the latch 10 is disposed in a space E which extends radially between the outer and inner edges 82 and 132 of the drive elements 8 and 13 and the drive ring 13 is arranged radially around the drive disc 8 .

Selon une variante non représentée de l'invention, les leviers oscillants 30 et 31 peuvent agir directement sur le ou les verrous montés sur l'excentrique.According to a variant not shown of the invention, the oscillating levers 30 and 31 can act directly on the locks mounted on the eccentric.

L'invention est décrite ci-dessus dans le cas ou l'arbre 1 et les disques 8 sont animés d'un mouvement rotatif dans un seul sens, alors que les couronnes 13 sont animées d'un mouvement alternatif. L'invention concerne également le cas inverse où l'arbre central et les disques 8 sont animés d'un mouvement de rotation alternatif, alors que l'ensemble des couronnes 13 est animé d'un mouvement de rotation continu dans un seul sens, de préférence à vitesse constante.The invention is described above in the case where the shaft 1 and the discs 8 are driven in a rotary motion in one direction, while the rings 13 are moved in a reciprocating motion. The invention also relates to the opposite case where the central shaft and the disks 8 are driven by an alternating rotational movement, whereas the set of rings 13 is driven by a continuous rotational movement in one direction only. preferably at constant speed.

Quel que soit le mode de réalisation, sur 360° d'angle métier, lorsque un cadre de lisses est entraîné à partir d'une couronne 13, l'amplitude de son mouvement d'oscillations verticales est réduite par rapport à son amplitude lorsqu'il est entraîné par un disque 8 et la commutation des verrous 10 et équivalent, d'une position de solidarisation avec le disque 8 vers une position de solidarisation avec la couronne 13, ou réciproquement, a lieu lorsque le cadre est au voisinage de sa position supérieure ou au voisinage de sa position inférieure.Regardless of the embodiment, over 360 ° of the working angle, when a heald frame is driven from a ring 13, the amplitude of its movement of vertical oscillations is reduced with respect to its amplitude when it is driven by a disk 8 and the switching of the locks 10 and the equivalent, a securing position with the disk 8 to a position of attachment to the ring 13, or conversely, occurs when the frame is in the vicinity of its position higher or near its lower position.

Les caractéristiques techniques des modes de réalisation et variantes de l'invention peuvent être combinées entre elles.The technical features of the embodiments and variants of the invention can be combined with each other.

Claims (14)

  1. Rotary dobby (R) for a loom (M), this dobby comprising, for each of its blades:
    - an oscillating part (5) coupled to a heddle frame (3) and associated with an actuating element (4) mounted loose on a central shaft (1),
    - a first driving element (8) for driving the actuation element, secured in rotation to the central shaft,
    - a second driving element (13) for driving the actuation element, and
    - at least one latch (10, 11) mounted on the actuation element and capable of securing this actuation element in rotation either with the first driving element (8), or with the second driving element (13),
    one of the two driving elements being driven in a rotary movement in only one direction, while the other driving element is driven in an alternating rotary movement,
    characterized in that the second driving element (13) is placed around the first driving element (8) and in that the latch (10, 11) is placed in a space (E) defined radially between the first driving element and the second driving element.
  2. Dobby according to claim 1, characterized in that the first driving element (8) is driven in a rotary movement (F8) in only one direction and in that the second driving element (13) is driven in an alternating rotary movement (F13, F'13).
  3. Dobby according to one of the preceding claims, characterized in that each latch (10, 11) is provided with a first portion (104, 114; 109b) suitable for being engaged selectively in at least one notch (83a-83d) arranged on an outer radial edge (82) of the first driving element (8) and with a second portion (105, 115; 109a) suitable for being engaged selectively in at least one notch (133a-133d) arranged on an inner radial edge (132) of the second driving element (13).
  4. Dobby according to claim 3, characterized in that it comprises means (23, 24) for elastically loading each latch (10, 11) to a position of engagement of its first portion (104, 114) or of its second portion (109a) in a notch (83a-83d) arranged on the outer radial edge (82) of the first driving element (8) or in a notch (133a) arranged on the inner radial edge (132) of the second driving element (13).
  5. Dobby according to one of claims 3 or 4, characterized in that, when a latch (10, 11) is engaged with a driving element (8), amongst the first and the second driving elements, a portion (105, 115) of this latch, which is suitable for being engaged selectively in a notch (133a-133d) of the other driving element (13), is in sliding contact with the adjacent edge (132) of the other driving element (13).
  6. Dobby according to one of the preceding claims, characterized in that two latches (10, 11) are placed in the space (E) defined radially between the first driving element (8) and the second driving element (13) and in that the outer radial edge (82) of the first driving element (8) and the inner radial edge (132) of the second driving element (13) are each provided with four notches (83a-83d, 133a-133d) for receiving a portion (104, 105, 114, 115) of a latch (10, 11).
  7. Dobby according to one of the preceding claims, characterized in that the second driving elements (13) belonging to the various blades of the dobby (R) are secured in rotation about the axis (X1) of the central shaft (1) and together form a cradle, itself rotated (F13, F'13) about this axis.
  8. Dobby according to one of the preceding claims, characterized in that it comprises, for each blade, two oscillating levers (30, 31), capable of being held in position by a selection device (35), and at least one member (15, 16), mounted on the second driving element (13) and capable of transmitting a force (E33, E15) from one of the oscillating levers to a latch (10, 11).
  9. Dobby according to claim 8, characterized in that each force-transmitting member is a rocker (15, 16), mounted so as to pivot (F15) about an axis (17a, 17b) that is fixed relative to the second driving element (13).
  10. Dobby according to claim 8, characterized in that each force-transmitting member is a movable slide (15) that can move in translation in a radial direction, on the second driving element (13).
  11. Dobby according to one of the preceding claims, characterized in that it comprises, for each blade, two oscillating levers (30, 31) capable of being held in position by a selection device (35) and in that at least one portion (137a, 137b) of an outer radial edge (137) of the second driving member (13) is capable of interacting with an oscillating lever (30, 31) and of placing this lever in a position in which it can be retained by the selection device.
  12. Dobby according to one of the preceding claims, characterized in that, when it is in a configuration (Fig. 2) in which the latch (10, 11) can be tipped between a first position, engaged with one of the driving elements (8), and a second position, engaged with the other driving element (13), both driving elements (8, 13) are driven in a rotary movement (F8, F13) in the same direction.
  13. Dobby according to one of the preceding claims, characterized in that, when it is in a configuration (Fig. 2) in which the latch (10, 11) can be tipped between a first position, engaged with one of the driving elements (8), and a second position, engaged with the other driving element (13), both driving elements (8, 13) have the same instantaneous angular speeds (V) and the same instantaneous angular accelerations (A) relative to the axis (X1) of rotation of the central shaft (1).
  14. Loom (M) fitted with a rotary dobby (R) according to one of the preceding claims.
EP11157534.6A 2010-03-12 2011-03-09 Rotary dobby and loom provided with such a dobby Active EP2365116B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1051794A FR2957366B1 (en) 2010-03-12 2010-03-12 ROTARY RATIERE AND WEAVING EQUIPPED WITH SUCH A RETIRE

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EP2365116A1 EP2365116A1 (en) 2011-09-14
EP2365116B1 true EP2365116B1 (en) 2015-07-08

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CN (1) CN102191605B (en)
FR (1) FR2957366B1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110117859B (en) * 2018-02-06 2021-08-17 郑川田 Dobby capable of forming double-fell
CN108588950A (en) * 2018-04-03 2018-09-28 西安工程大学 A kind of multipage heald frame shedding mechanism of three dimensional separation loom

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH671782A5 (en) * 1987-01-05 1989-09-29 Ernst Kleiner
FR2662186B1 (en) * 1990-05-18 1992-08-28 Staubli Sa Ets PROCESS FOR THE ASSEMBLY OF THE ROTARY DRIVES FOR ACTIVATING ROTATORS FOR WEAVING MATERIALS, AND DRIVES OBTAINED.
FR2663347A1 (en) 1990-06-15 1991-12-20 Staubli Trumpelt Gmbh Maschine CLOSED CROWD RAIL FOR WEAVING MATERIALS.
JPH07166444A (en) * 1993-12-15 1995-06-27 Murata Mach Ltd Rotary dobby
JPH101842A (en) * 1996-06-14 1998-01-06 Murata Mach Ltd Rotary dobby
FR2757883B1 (en) * 1996-12-31 1999-02-19 Staubli Sa Ets ROTARY RATIERE AND WEAVING MACHINE EQUIPPED WITH SUCH A RATIERE
FR2757882B1 (en) * 1996-12-31 1999-02-19 Staubli Sa Ets ROTARY RATIERE AND WEAVING MACHINE EQUIPPED WITH SUCH A RATIERE
FR2842538B1 (en) * 2002-07-16 2004-10-29 Staubli Sa Ets ROTARY RATIERE FOR WEAVING, AND WEAVING EQUIPMENT PROVIDED WITH SUCH A RAIL
ITMI20022151A1 (en) * 2002-10-10 2004-04-11 Fimtextile Spa DEVICE FOR IMPLEMENTING THE PROGRAMMING OF ROTARY DOBBIES FOR WEAVING MACHINES CONTAINING PERFECTED ELECTRIC ROTARY MOTOR CONTROL VEHICLES
ITMI20022695A1 (en) * 2002-12-19 2004-06-20 Fimtextile Spa DEVICE FOR IMPLEMENTING ROTARY DOBBY PROGRAMMING IN WEAVING MACHINES
DE10343377B3 (en) * 2003-09-17 2005-04-28 Groz Beckert Kg Shaft drive for weaving shafts
FR2899244B1 (en) * 2006-03-31 2008-06-13 Staubli Faverges Sca ROTARY RATIERE, WEAVING EQUIPPED WITH SUCH REAL ESTATE AND TRAINING ELEMENT FOR SUCH REAL ESTATE
FR2899602B1 (en) * 2006-04-11 2008-05-23 Staubli Faverges Sca ROTARY RATIERE, WEAVING COMPRISING SUCH A REAL ESTATE AND METHOD OF CONTROLLING SUCH REAL ESTATE

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CN102191605A (en) 2011-09-21
FR2957366B1 (en) 2012-04-13
CN102191605B (en) 2014-08-20
FR2957366A1 (en) 2011-09-16
EP2365116A1 (en) 2011-09-14

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