EP4095296B1 - Shedding machine - Google Patents

Description

The present invention relates to a shed forming machine, of mechanical cam or dobby type, for a loom.

In the field of weaving, it is known to use a shed forming machine to drive, according to a predetermined weave and with a movement parallel to each other, sets of levers and connecting rods forming a pulling mechanism. frames of a loom.

A shedding machine can be formed by a cam mechanism which comprises several cams rotated by a main shaft and each defining two conjugate tracks on which two rollers supported by a lever, most often called a lever, respectively bear. Release. Each output lever includes a lever arm to which one of the connecting rods of the pulling mechanism is coupled. The output levers are provided in a number equivalent to the number of heddle frames of the loom and mounted to have an alternating oscillation movement around a common shaft defined by the mechanical frame.

A shedding machine can also be constituted by a rotating dobby which comprises internal connecting rods belonging to oscillating connecting rod-lever assemblies controlled by eccentric-shaped actuating elements. These actuating elements are mounted on a main shaft of the dobby driven by an intermittent rotational movement. A selection device allows, at the level of each of the dobby blades, and depending on the weave to be obtained on the fabric being weaved, to secure or not the actuating element with the main shaft, which allows you to train or not the pulling mechanism. The part of each actuating element which is connected to the draw constitutes an exit lever for the dobby.

Whatever the type of shedding machine, we consider an exit opening of this machine constituted by a cutout made in a cover of the machine and which is crossed by the exit levers, part of which remains contained between the frame and the cover of the machine, within the internal volume of the machine which contains an oil bath necessary for the lubrication of the moving mechanical components of the machine.

The high speed movement of the output levers which move partially in the oil bath is likely to produce oil splashing out of the machine. However, the oil present in the internal volume of the machine must not escape, in order not to risk staining the fabric during manufacture or contaminating the environment of the machine.

On the other hand, a shed forming machine can be equipped with a variable number of output levers, depending on the number of frames of the loom with which it is associated. Under these conditions, a sealing device intended to close an outlet opening of the shedding machine must be compatible with different distributions of outlet levers.

It is known to limit oil projections outside the internal volume of a shedding machine by means of sealing spacers mounted around a common shaft of the output levers. So, EP-A-3 162 933 teaches to equip adjacent sealing spacers with sealing barriers formed by joints. This solution is generally satisfactory and makes it possible to limit, to a large extent, oil splashes through the outlet opening of the machine. However, the sealing around the cover and the frame of the shedding machine is carried out by means of profiles which must be manufactured and mounted precisely, which is expensive and time-consuming. In addition, it is planned to use seals attached around the spacers, which can also prove expensive and complex to implement.

It is these drawbacks that the invention more particularly intends to remedy by proposing a new shed forming machine in which the sealing at the level of the outlet opening crossed by the oscillating outlet levers is improved, by means of an economical and reliable approach.

• des leviers de sortie oscillant autour d'un arbre commun centré sur un axe longitudinal ;
• un capot définissant une ouverture de sortie traversée par les leviers de sortie ;
• un bâti qui délimite, avec le capot, un volume intérieur de la machine ; et
• un dispositif d'étanchéité destiné à fermer l'ouverture de sortie du capot et comprenant des entretoises d'étanchéité empilées le long de l'arbre commun et disposées de part et d'autre des leviers de sortie, ainsi qu'au moins un joint d'étanchéité.

Chaque entretoise d'étanchéité comprend :

• un bandeau qui s'étend d'une première extrémité, située à proximité du bâti, à une deuxième extrémité, située à proximité du capot, et comprend deux bords longitudinaux, orthogonaux à l'axe longitudinal de l'arbre commun et configurés pour être en appui contre au moins un bord longitudinal du bandeau d'une entretoise d'étanchéité adjacente ; et
• un bord radial interne qui définit une ouverture de passage de l'arbre commun centrée sur un axe primaire confondu avec l'axe longitudinal de l'arbre commun au moins lorsque la machine est en configuration de tissage.

Conformément à l'invention,

• le joint d'étanchéité s'étend selon une direction principale parallèle à l'axe longitudinal de l'arbre commun et est en appui contre une pièce fixe de la machine ;
• chaque entretoise d'étanchéité est pourvue d'au moins une rainure qui s'étend parallèlement à son axe primaire et débouche de chaque côté de l'entretoise d'étanchéité ;
• les rainures des entretoises d'étanchéité du dispositif d'étanchéité définissent ensemble un canal de réception d'un talon du joint d'étanchéité.

To this end, the invention relates to a shed forming machine of the mechanical cam or dobby type, for a weaving loom, this machine comprising:

• output levers oscillating around a common shaft centered on a longitudinal axis;
• a cover defining an outlet opening through which the outlet levers pass;
• a frame which delimits, with the cover, an interior volume of the machine; And
• a sealing device intended to close the outlet opening of the hood and comprising sealing spacers stacked along the common shaft and arranged on either side of the outlet levers, as well as at least one seal sealing.

Each seal spacer includes:

• a strip which extends from a first end, located near the frame, to a second end, located near the cover, and comprises two longitudinal edges, orthogonal to the longitudinal axis of the common shaft and configured to bear against at least one longitudinal edge of the strip of an adjacent sealing spacer; And
• an internal radial edge which defines a passage opening of the common shaft centered on a primary axis coincident with the longitudinal axis of the common shaft at least when the machine is in weaving configuration.

According to the invention,

• the seal extends in a main direction parallel to the longitudinal axis of the common shaft and bears against a fixed part of the machine;
• each sealing spacer is provided with at least one groove which extends parallel to its primary axis and opens out on each side of the sealing spacer;
• the grooves of the sealing spacers of the sealing device together define a channel for receiving a heel of the sealing gasket.

Thanks to the invention, the different grooves of the sealing spacers make it possible to mount the seal as close as possible to the fixed part of the machine, whether it is the frame or the cover. The joint can have a relatively simple shape and its assembly is easy, which is advantageous in economic terms and in terms of speed of manufacture. In addition, the structure envisaged for the sealing spacers and the seal gives the shed forming machine of the invention good compactness and facilitates maintenance operations.

• dans un plan perpendiculaire à l'axe primaire, la rainure de chaque entretoise d'étanchéité est définie par un profil avec un fond dont la largeur est supérieure à la largeur de son embouchure.
• les rainures des entretoises d'étanchéité du dispositif d'étanchéité ont, dans un plan perpendiculaire à leur axe primaire, le même profil.
• le joint d'étanchéité présente une section, perpendiculaire à sa direction principale, qui est constante selon cette direction principale et la longueur du joint d'étanchéité, mesurée parallèlement à sa direction principale, est supérieure ou égale à une largeur de l'ouverture de sortie, mesurée parallèlement à l'axe longitudinal de l'arbre commun.
• au moins une des entretoises d'étanchéité est une entretoise d'étanchéité intercalaire, une largeur du bandeau de cette entretoise, mesurée parallèlement à l'axe primaire entre ses deux bords longitudinaux, présente une première valeur au niveau de ses première et deuxième extrémités et une deuxième valeur dans une zone intermédiaire située entre ses première et deuxième extrémités qui couvre un secteur angulaire de débattement d'un levier de sortie, la première valeur est égale à la division de la machine de formation de la foule et la deuxième valeur est égale à la division de la machine de formation de la foule diminuée de l'épaisseur d'un levier de sortie, mesurée parallèlement à l'axe longitudinal de l'arbre commun.
• le bord radial interne s'étend autour de l'axe primaire sur un secteur angulaire dont l'angle au sommet est strictement inférieur à 180°.
• le dispositif d'étanchéité comprend au moins un organe d'étanchéité complémentaire monté dans l'ouverture de sortie, logé partiellement dans l'entretoise d'étanchéité intercalaire au niveau de la zone intermédiaire et qui coopère de façon étanche avec une face d'un levier de sortie adjacent, cette face étant perpendiculaire à l'axe longitudinal de l'arbre commun.
• au moins une des entretoises d'étanchéité est une entretoise d'étanchéité d'extrémité, une largeur du bandeau de cette entretoise, mesurée parallèlement à l'axe primaire entre ses deux bords longitudinaux, présente une valeur constante, égale à la division de la machine de formation de la foule, de sa première extrémité à sa deuxième extrémité et en ce que l'entretoise d'étanchéité comprend des moyens de centrage par rapport à l'arbre commun.
• la machine de formation de la foule comprend :
  • des butées axiales disposées autour de l'arbre commun, de part et d'autre de chaque levier de sortie ;
  • des organes de fixation axiale montés à chaque extrémité de l'arbre commun et configurés pour retenir les butées axiales et les leviers de sortie sur l'arbre commun ;
  • au moins deux bagues d'appui, chacune interposée entre une butée axiale et un organe de fixation axiale ;
  • alors que des entretoises d'étanchéité d'extrémité sont montées autour des bagues d'appui grâce aux moyens de centrage ; et
  • des entretoises d'étanchéité intercalaires sont chacune montées en périphérie d'une butée axiale et délimitent chacune un volume de passage d'un levier de sortie vers l'extérieur, à travers l'ouverture de sortie, au niveau de la zone intermédiaire de leur bandeau.
• chaque entretoise d'étanchéité comprend un logement qui la traverse selon un axe parallèle à l'axe primaire, qui débouche sur deux côtés opposés de l'entretoise d'étanchéité et qui est configuré pour accueillir un arbre support.
• La machine de formation de la foule comprend un arceau formé d'une corps longitudinal parallèle à l'axe longitudinal de l'arbre commun et de deux pattes perpendiculaires au corps longitudinal et qui définissent chacune un palier d'articulation de l'arbre support.
• la machine de formation de la foule est de type ratière et chaque levier de sortie est entraîné dans un mouvement oscillant par une bielle interne de la machine.
• la machine de formation de la foule est de type mécanique à cames et comprend un arbre à cames parallèle à l'arbre commun et dont la rotation entraîne les leviers de sortie dans un mouvement oscillant et chaque entretoise est configurée pour pivoter entre une position de tissage, dans laquelle les leviers de sortie sont accouplés à l'arbre à cames, et une position de nivelage, dans laquelle les leviers de sortie sont découplés de l'arbre à cames.
• les entretoises d'étanchéité comprennent des organes de solidarisation adaptés pour maintenir les entretoises adjacentes empilées le long de l'arbre commun.
• les entretoises d'étanchéité comprennent des parois qui viennent en recouvrement entre deux entretoises d'étanchéité adjacentes, lorsqu'elles sont empilées le long de l'arbre commun .
• un canal de réception inférieur du dispositif d'étanchéité reçoit un premier joint d'étanchéité qui est en appui contre une partie du bâti tournée vers le capot en configuration de tissage de la machine de formation de la foule et un canal de réception supérieur du dispositif d'étanchéité reçoit un deuxième joint d'étanchéité qui est en appui contre une partie du capot tournée vers le bâti en configuration de tissage de la machine de formation de la foule.

According to advantageous but not obligatory aspects of the invention, such a crowd forming machine can incorporate one or more of the following characteristics:

• in a plane perpendicular to the primary axis, the groove of each sealing spacer is defined by a profile with a bottom whose width is greater than the width of its mouth.
• the grooves of the sealing spacers of the sealing device have, in a plane perpendicular to their primary axis, the same profile.
• the seal has a section, perpendicular to its main direction, which is constant along this main direction and the length of the seal, measured parallel to its main direction, is greater than or equal to a width of the opening of output, measured parallel to the longitudinal axis of the common shaft.
• at least one of the sealing spacers is an intermediate sealing spacer, a width of the strip of this spacer, measured parallel to the primary axis between its two longitudinal edges, has a first value at its first and second ends and a second value in an intermediate zone located between its first and second ends which covers an angular sector of travel of a lever output, the first value is equal to the division of the shedding machine and the second value is equal to the division of the shedding machine minus the thickness of an output lever, measured parallel to the longitudinal axis of the common shaft.
• the internal radial edge extends around the primary axis over an angular sector whose apex angle is strictly less than 180°.
• the sealing device comprises at least one complementary sealing member mounted in the outlet opening, partially housed in the intermediate sealing spacer at the level of the intermediate zone and which cooperates in a sealed manner with one face of a adjacent output lever, this face being perpendicular to the longitudinal axis of the common shaft.
• at least one of the sealing spacers is an end sealing spacer, a width of the strip of this spacer, measured parallel to the primary axis between its two longitudinal edges, has a constant value, equal to the division of the machine for forming the shed, from its first end to its second end and in that the sealing spacer comprises centering means relative to the common shaft.
• The crowd forming machine includes:
  • axial stops arranged around the common shaft, on either side of each output lever;
  • axial fasteners mounted at each end of the common shaft and configured to retain the axial stops and output levers on the common shaft;
  • at least two support rings, each interposed between an axial stop and an axial fixing member;
  • while end sealing spacers are mounted around the support rings using the centering means; And
  • intermediate sealing spacers are each mounted on the periphery of an axial stop and each delimit a volume of passage of an exit lever towards the outside, through the outlet opening, at the level of the intermediate zone of their headband.
• each sealing spacer comprises a housing which passes through it along an axis parallel to the primary axis, which opens onto two opposite sides of the sealing spacer and which is configured to accommodate a support shaft.
• The shed forming machine comprises an arch formed of a longitudinal body parallel to the longitudinal axis of the common shaft and two legs perpendicular to the longitudinal body and which each define an articulation bearing of the support shaft.
• the shedding machine is of the dobby type and each output lever is driven in an oscillating movement by an internal connecting rod of the machine.
• the shedding machine is of mechanical cam type and includes a camshaft parallel to the common shaft and the rotation of which drives the output levers in an oscillating motion and each spacer is configured to pivot between a weaving position , in which the output levers are coupled to the camshaft, and a leveling position, in which the output levers are decoupled from the camshaft.
• the sealing spacers comprise securing members adapted to maintain the adjacent spacers stacked along the common shaft.
• the sealing spacers comprise walls which overlap between two adjacent sealing spacers, when they are stacked along the common shaft.
• a lower receiving channel of the sealing device receives a first seal which bears against a part of the frame facing the cover in weaving configuration of the shed forming machine and an upper receiving channel of the device seal receives a second seal which is supported against a part of the cover facing the frame in the weaving configuration of the shed forming machine.

• [Fig. 1] la figure 1 est une vue en perspective d'une machine de formation de la foule conforme à l'invention ;
• [Fig. 2] la figure 2 est une vue en perspective de la machine de formation de la foule de la figure 1, après retrait de son capot et mise en place d'un outil de nivelage, et alors que les leviers de sortie sont en configuration de tissage ;
• [Fig. 3] la figure 3 est une coupe transversale à un arbre commun de la machine dans la configuration de la figure 2, dans deux plans décalés le long de cet arbre, représentés respectivement aux inserts A et B ;
• [Fig. 4] la figure 4 est une vue à plus grande échelle du détail IV à l'insert B de la figure 3 ;
• [Fig. 5] la figure 5 est une vue analogue à la figure 3, dans les mêmes plans représentés aux inserts A et B, alors que les leviers sont en configuration de nivelage ;
• [Fig. 6] la figure 6 est une coupe partielle à plus grande échelle, selon le plan VI-VI à la figure 3 ;
• [Fig. 7] la figure 7 est une vue en perspective éclatée des éléments représentés en coupe à la figure 6, à l'exception de deux vis d'assemblage ;
• [Fig. 8] la figure 8 est une vue en perspective éclatée d'un empilement d'entretoises d'étanchéité et de deux joints utilisés dans la machine de formation de la foule des figures 1 à 7 ;
• [Fig. 9] la figure 9 est une vue de dessus et en élévation, sur deux côtés opposés, d'une entretoise intercalaire appartenant à la machine des figures 1 à 7 ;
• [Fig. 10] la figure 10 est une vue analogue à la figure 9 pour une entretoise d'extrémité ; et
• [Fig. 11] la figure 11 est une vue analogue à la figure 8 dans le cas où la machine de formation de la foule comprend une répartition de leviers de sortie différents de celle de des figures 1 à 7.

The invention will be better understood and other advantages thereof will appear more clearly in the light of the description which follows of two embodiments of a crowd forming machine conforming to its principle, given solely as a example and made with reference to the appended designs in which:

• [ Fig. 1 ] there figure 1 is a perspective view of a crowd forming machine according to the invention;
• [ Fig. 2 ] there figure 2 is a perspective view of the crowd forming machine of the figure 1 , after removing its cover and installing a leveling tool, and while the output levers are in weaving configuration;
• [ Fig. 3 ] there Figure 3 is a cross section to a common shaft of the machine in the configuration of the figure 2 , in two planes offset along this tree, represented respectively in inserts A and B;
• [ Fig. 4 ] there Figure 4 is a larger scale view of detail IV at insert B of the Figure 3 ;
• [ Fig. 5 ] there Figure 5 is a view analogous to the Figure 3 , in the same planes shown in inserts A and B, while the levers are in leveling configuration;
• [ Fig. 6 ] there Figure 6 is a partial section on a larger scale, according to plan VI-VI at Figure 3 ;
• [ Fig. 7 ] there Figure 7 is an exploded perspective view of the elements shown in section at the Figure 6 , except for two assembly screws;
• [ Fig. 8 ] there figure 8 is an exploded perspective view of a stack of sealing spacers and two seals used in the crowd forming machine of figures 1 to 7 ;
• [ Fig. 9 ] there Figure 9 is a top and elevation view, on two opposite sides, of an intermediate spacer belonging to the machine of figures 1 to 7 ;
• [ Fig. 10 ] there Figure 10 is a view analogous to the Figure 9 for an end spacer; And
• [ Fig. 11 ] there Figure 11 is a view analogous to the figure 8 in the case where the shedding machine includes a distribution of output levers different from that of figures 1 to 7 .

The cam mechanism 2 shown on the figures 1 to 10 is intended to drive connecting rods and levers of a drawing mechanism not shown, this drawing mechanism itself driving the frames of a loom, according to a technique known per se.

As such, the cam mechanism 2 constitutes a crowd forming machine.

The cam mechanism 2 comprises a frame 4 and a cover 6 attached to the frame. The frame 4 and the cover 6 are fixed parts of the cam mechanism 2 and define between them an internal volume V2 of the cam mechanism 2, in which are received a certain number of mechanical members lubricated by an oil bath not shown.

A control shaft 8 is driven in rotation, around its longitudinal axis A8, by a motor not shown. This control shaft 8 itself drives, through an angle gear not shown, a camshaft 10 equipped with cams 12 and supported by the frame 4. We denote A10 the longitudinal axis of the camshaft, around which this shaft rotates when the cam mechanism operates. In the example of the figures, the number of cams 12 is equal to eight. The cams 12 determine the armor produced by the heddle frames driven by the cam mechanism 2.

A set of four output levers 14 is mounted in the volume V2 and partially protrudes from this volume through an outlet opening 16 provided in the cover 6. More precisely, each outlet lever 14 defines a central bore 142 and two tabs 144 on which rollers 18 are mounted held in position by flanges 20. Each output lever 14 also comprises a lever arm 146 which extends generally in a radial direction to a central axis of the bore 142. In the mounted configuration of the cam mechanism 2, the parts 142 and 144 of an output lever 14 as well as the rollers 18 and the flanges 20 which are associated with it are arranged in the volume V2, while its lever arm 146 passes through the opening 16 .

A shaft 22, whose longitudinal axis is denoted A22, is inserted into the different central bores 142 of the levers 14 and constitutes a common shaft around which the levers 14 oscillate when the cam mechanism 2 is operating. Axes A10 and A22 are parallel.

In the example of the figures, the cam mechanism 2 is equipped with four levers 14 and the volume left free by these four levers, along the common shaft 22 which can receive up to eight levers, is occupied by rings catch-up 24 of which there are four.

Between two adjacent levers 14 along the axis A22, there is provided around the shaft 22 a ball bearing, commonly referred to as a "thrust ball", which allows differentiated oscillation movements of the levers 14 around the oscillation. axis A22, depending on the profile of the cams 12 with which they are associated by the rollers 18.

Ball bearings 26 are also arranged on either side of the stack of levers 14. Thus, in the example of the figures where four levers 14 are mounted on the shaft 22, five ball bearings 26 are used. Generally speaking, the number of thrust ball bearings 26 is equal to the number of levers 14 plus one.

Two side rings 28 are mounted on the shaft 22, on either side of the subassembly formed by parts 14, 24 and 26.

Two circlips 30 are arranged on either side of the side rings 28 and engaged in peripheral grooves 32 of the common shaft 22, which makes it possible to maintain axially the stack formed of the parts 14, 26, 24 and 28 along of the shaft 22. An elastic washer 34 is inserted axially between one of the side rings 28 and the nearest circlip 30, which allows the axial play of the parts mounted around the common shaft 22 to be taken up.

As visible at figure 1 , in the mounted configuration of the dobby, part of the opening 16 is left free by the levers 14. On the figure 1 , this part of the opening 16 is shown in gray, assuming that no sealing device would be used.

The opening 16 is delimited by a first edge 62 of the cover 6 which is parallel to the axis A22, as well as by two edges, only one of which is visible to the figures 1 And 2 , with the reference 64, and which are parallel to each other and perpendicular to axis A22. The opening 16 is also defined by an edge 41 of the frame 4 which is turned towards the cover 6 in the mounted configuration of the cam mechanism 2.

In order to close the gray part of the opening 16 visible to the figure 1 , the cam mechanism 2 comprises a stack E40 of sealing spacers 40 which are of two types, namely intermediate sealing spacers 40A and end sealing spacers 40B.

On the figures 3 And 5 , insert A corresponds to a cut at the level of an intermediate spacer 40A, while insert B corresponds to a cut at the level of an end spacer 40B.

The sealing spacers 40, whether of type 40A or 40B, are made by molding plastic material, for example polyamide. The 40A intermediate sealing spacers are identical to each other. Likewise, the end sealing spacers 40B are identical to each other.

The number of intermediate spacers 40A is equal to the number of levers 14. The number of end spacers 40B is equal to 2 plus the difference between the maximum number of levers that it is possible to mount in the cam mechanism, here 8, and the number of levers installed in the cam mechanism. In the example, the number of intermediate sealing spacers is four and the number of end sealing spacers is 2 + (8 - 4) = 6.

A 40A intermediate sealing spacer is shown alone in the Figure 9 , in top view at insert A and in two elevation views corresponding to its two opposite sides, to inserts B and C.

The intermediate sealing spacer 40A comprises a strip 402 which extends on an external side of the spacer visible at the insert C of the Figure 9 and oriented upwards in the mounted configuration of the spacer in the machine 2, between a first end 404, which is arranged near the edge 41 of the frame 4 in the mounted configuration of the spacer, and a second end 406, which is arranged, in the same mounted configuration, near the cover 6.

This strip 402 comprises two longitudinal edges 408 and 410 which are orthogonal to the axis A22 in the mounted configuration of the spacer and which are configured to be supported against at least one longitudinal edge 410 or 408 of the strip 402 of an adjacent sealing spacer 40.

On the side opposite the strip 402, the intermediate sealing spacer 40A has an internal radial edge 412 in the shape of an arc of a circle centered on an axis A40 which forms a primary axis for this spacer and to which the longitudinal edges 408 and 410 are perpendicular. The internal radial edge 412 extends around the primary axis A40 over an angular sector whose vertex angle α is strictly less than 180°, for example of the order of 140°.

We denote R40 as the radius of curvature of the radial edge 412, this radius of curvature is chosen equal to the external radius of the ball bearings 26 and of the rings 24 and 28, which is common. The edge 412 thus defines a passage opening for the common shaft 22 centered on the primary axis A40.

Alternatively, the internal radial edge 412 extends along an irregular contour distinct from a radius of curvature while defining the passage opening centered on the primary axis A40.

The concave volume defined in the edge of an intermediate sealing spacer 40A, on the side of its radial edge 412, is configured to receive a part of the common shaft 22 equipped with elements 24 to 28.

In the assembled configuration of the E40 stack, the different primary axes A40 of the intermediate sealing spacers 40A coincide with the axis A22.

The strip 402 of an intermediate sealing spacer has a first width f402 in the vicinity of its ends 404 and 406 and a second width f'402, strictly less than the width f402, in an intermediate zone corresponding approximately to the angular sector of vertex angle α.

On its two sides respectively visible at inserts B and C of the Figure 9 , the spacer 40A is provided with stiffening ribs 414.

At its end 404, the intermediate sealing spacer 40A is provided with a first groove 416 which extends parallel to its primary axis A40 and opens onto the two sides of this spacer visible at inserts B and C of the Figure 9 .

This groove 416 also opens towards the top of the inserts A and B of the Figure 9 and has a dovetail shape, with a profile perpendicular to the axis A40 which has a bottom 418 whose width f418 is greater than the width f420 of its mouth 420 opposite the bottom 418. This profile is constant over the length of the groove 416, between the two opposite sides of the spacer 40A.

On the other hand, each spacer 40 is pierced with a through hole 422 which opens on its two opposite sides visible to the inserts B and C of the Figure 9 and which constitutes a housing for receiving a support shaft 42 whose longitudinal axis A42 is parallel to the axes A10 and A22. We note A422 the longitudinal axis of the orifice 422, which is parallel to the primary axis A40 of the spacer 40 and coincides with the axis A42 in the mounted configuration of the cam machine 2. The through orifice is a cylindrical-shaped receiving housing centered on axis A422.

The intermediate sealing spacer 40A also includes a hook 424 provided on the side of this spacer visible at insert B of the Figure 9 and intended to engage in a corresponding housing 426 provided on the opposite side of another spacer 40A or 40B, as visible on the insert C of the figures 9 And 10 . The hook 424 and the housing 426 make it possible to join together two adjacent sealing spacers 40 of the stack E40, that is to say to maintain, in relation to each other, the adjacent spacers stacked along the common tree 22.

On the other hand, in the vicinity of its end 404, on the side visible to the insert B of the Figure 9 , the end sealing spacer 40B comprises a second hook 425 intended to engage in a corresponding housing 427 provided on the opposite side of another spacer 40A or 40B, as visible on the insert C of the figures 9 And 10 . The hook 425 and the housing 427 also make it possible to join together two adjacent sealing spacers 40 of the stack E40, that is to say to maintain, in relation to each other, the adjacent spacers stacked along the common shaft 22.

Thus, the continuity of the intermediate sealing spacers 40A, that is to say their maintenance with respect to the adjacent spacers stacked along the common shaft 22, can take place thanks to the hooks 424 and 425 and to the corresponding housings 426 and 427. In the illustrated execution, each end sealing spacer 40B and each intermediate sealing spacer 40A has hooks 424 and 425 on one side of the spacer, and housings 426 and 427 on the opposite side of the spacer.

The spacers are stacked on the common shaft 22 when arranged adjacently along the common shaft and made continuous to form the sealing device with a seal 52 or 54.

The intermediate sealing spacer 40A also includes a second groove 436 formed near its upper end 406 and which extends parallel to its primary axis A40, opening onto the two sides of this spacer respectively visible at inserts B and C of the Figure 9 . This groove 436 also has a bottom 438 and a mouth 440 which extends over the entire length of the groove 436, between the two sides of the spacer. In section perpendicular to the A40A axis, the profile of the groove 436 is dovetailed, with its bottom 438 which has a width f438 greater than the width f440 of the mouth 440.

We note 442 and we call "nose" the part of the intermediate end spacer 40A close to its end 406, at the level of which the strip 402 has its maximum width f402. The through hole 422 is provided in the nose 442. On its side visible to the insert B of the Figure 9 , the nose 402 is bordered by a rib 444 intended to engage under the strip 402 of another adjacent sealing spacer, when they are stacked along the common shaft 22 within the stack E40, so as to create a partial overlap between these two spacers, which improves the sealing effect obtained at the level of the noses 442. In the same way, the end 404 is provided with a rib 446 projecting relative to the side of the sealing spacer visible at insert B and intended to engage inside one end 404 of an adjacent spacer, which improves the sealing obtained at the level of the ends 404.

The end seal spacer 40B shown at inserts A, B and C of the Figure 10 has a structure comparable to that of the spacer 40A shown in Figure 9 . In particular, this end sealing spacer 40B defines a strip 402 which extends between a first end 404, which is arranged near the edge 41 of the frame 4 in the mounted configuration of the spacer, and a second end 406 , which is arranged, in the same mounted configuration, near the cover 6. The longitudinal edges 408 and 410 of the strip 402 are also perpendicular to a primary axis A40 of this spacer and configured to bear against at least one longitudinal edge 410 or 408 of the strip 402 of an adjacent sealing spacer 40.

For this end sealing spacer 40B, the strip 402 has a width f402, measured parallel to its primary axis A40 and between its edges 108 and 410, which is constant, with the same value as the maximum value for the spacer interlayer sealing 40A.

In addition, the radial internal edge 412 is circular, that is to say it extends over 360° around the primary axis A40, and has a radius R40 equal to the radius of curvature of the edge 412 of a spacer d 40A interlayer sealing. Alternatively, the internal radial edge 412 extends along an irregular contour distinct from a radius of curvature while defining the passage opening centered on the primary axis A40.

The disc-shaped volume defined in the edge of an end sealing spacer 40B and which is bordered by the edge 412 is configured to receive a portion of the common shaft 22. Thus, the edge 412 defines an opening passage of the common shaft 22.

The end sealing spacer 40B also includes hooks 424 and 425 and corresponding housings 426 and 427, similar to those of an intermediate sealing spacer 40A. This allows continuity of the sealing spacers 40, whatever their type, 40A or 40B.

The end sealing spacer 40B also includes stiffening ribs 414 provided on its two sides visible at the inserts B and C of the Figure 10 , a hook 424, a housing 426 and two grooves 416 and 436 respectively having geometries identical to those of the grooves 416 and 436 of the intermediate sealing spacer 40A.

Thus, the grooves 416 and 436 of the sealing spacers 40 of the stack E40 have the same profile in section perpendicular to their primary axis A40, whether they are grooves 416 and 436 belonging to an intermediate sealing spacer or grooves 416 and 436 belonging to an end sealing spacer.

The end sealing spacer 40B also includes a through hole 422 formed in its nose 442, as well as ribs 444 and 446 respectively identical to the ribs 444 and 446 of the intermediate end spacer 40A. The through hole 422 is a receiving housing of cylindrical shape centered on the axis A422.

Each end spacer 40B is formed of a first portion 401 and a second portion 403. The first portion 401 of an end spacer 40B has, in front view shown at inserts B and C of the Figure 10 , a geometry similar to that of a 40A spacer. The width of the ribs 414, measured parallel to the primary axis A40 in this portion 401, is equal to the width f402 of the strip 402. The portion 403 makes it possible to close, around the primary axis A40, the part of the edge 412 formed in portion 401. At this portion 403, the ribs 414 have a width f403, also measured parallel to the primary axis A40, which is strictly less than the width f402 of the strip 402.

As the end seal spacers 40B completely surround the adjustment rings 24 and the side rings 28, the end seal spacers are centered on the axis A22. More precisely, the edge 412 of the end sealing spacers 40B comprises radial extra thicknesses which constitute a means of centering these spacers around the axis A22, since the external peripheral surfaces of the rings 24 and 28 are centered on the axis A22.

The cam mechanism 2 also comprises a first elastomer seal 52 and a second elastomer seal 54 which each extend along a longitudinal axis A52, A54, these axes being parallel to the axes A10 and A22 in the mounted configuration of the cam mechanism.

The joints 52 and 54 are preferably extruded, in other words produced by an extrusion process, which is particularly simple and economically advantageous.

The joint 52 is produced by an elastomer profile which has a section, perpendicular to the axis A52, which is constant, over the length L52 of the joint 52. The joint 52 comprises a heel 522 and a lip 524. The heel 522 is configured to be engaged and retained inside a reception channel G2 formed by the juxtaposition of the grooves 416 of the different spacers 40 of the stack E40. As the grooves 416 of the different spacers 40 have the same profile, the section of the reception channel G2 is constant over the length of the stack E40 which is measured parallel to the axes A40 and A22 which are combined in the mounted configuration of the sealing spacers 40 in machine 2. The shape of the heel 522 is complementary to that of the reception channel G2. Taking into account the dovetail shape of the transverse profile of the grooves 316, therefore of the reception channel G2 and the heel 522, the joint 52 is firmly retained in position on the stack E40 when its heel 522 is in place in the reception channel G2.

In other words, the grooves 416 of the spacers of the sealing device stacked along the common shaft 22 define the receiving channel G2 of the heel 522 of the seal 52. The receiving channel G2 is adapted to partially accommodate the seal d seal 52. Also, the receiving channel G2 is adapted to position and maintain the seal 52 in the main direction A52 parallel to the longitudinal axis A22.

In this position, the lip 524 comes to rest against the edge 41 of the frame 4, which prevents oil projections from escaping from the internal volume V2, at the interface between the first ends 404 of the sealing spacers 40 and frame 4, in the vicinity of edge 41.

Comparably, the joint 54 is made by an elastomer profile which has a constant section over the length L54 and which has a heel 542 and a lip 544. The juxtaposition of the grooves 436 of the different spacers 40 within the stack E40 constitutes a second channel G4 for receiving the heel 542, which has a constant section over its length of the stack E40. The shape of the heel 542 is complementary to that of the reception channel G4. Taking into account the dovetail shape of the transverse profile of the grooves 346, therefore of the reception channel G4 and the heel 542, the joint 54 is also firmly retained in position on the stack E40 when its heel 542 is in place in the G4 reception channel.

Thus, the lip 544 prevents oil projections from leaving the volume V2 towards the outside of the cam mechanism 2, at the interface between the second ends 406 of the sealing spacers 40 and the cover 6 , in the vicinity of edge 62.

Thus, the sealing device consisting of the stack E40 and the seals 52 and 54 effectively closes the outlet opening 16, around the lever arms 146 of the outlet levers 14.

In practice, the length L52 is equal to the length of the edge 41 measured parallel to the axis A22, while the length L54 is greater than or equal to the length of the edge 62, also measured parallel to the axis A22. Thus, the length L52 or L54 of a seal is greater than or equal to the width ℓ16 of the outlet opening 16, which is measured parallel to the longitudinal axis A22 of the common shaft 22.

We note d the division of the cam mechanism 2, that is to say the distance, measured parallel to the axis X22, which separates two identical components along the common shaft 22. The division d can, by example, be measured as the distance which separates two faces of two adjacent levers 14, these faces being oriented in the same direction.

We note e14 the thickness of a lever 14 which is constant since, in practice, each lever 14 is produced by cutting a steel plate.

The width t 402 of the strip 402 of an intermediate sealing spacer 40A in its intermediate part is equal to the difference between the division d and the thickness e14. Thus, the intermediate zones of the intermediate spacers 40A make it possible to fill the space between two adjacent levers 14, by covering a ball bearing 26 disposed between these levers, which limits the projections of oil through the opening 16, between the levers 14.

Here, the intermediate sealing spacers 40A are each mounted on the periphery of an axial stop 26.

On the other hand, the width ℓ402 is equal to the division d, so that, in the zones of the opening 16 devoid of levers 14, the strips 402 of the sealing spacers 40 which are supported against each other by their longitudinal edges 408 and 410 constitute a continuous surface which opposes the projections of oil towards the outside of the volume V2, through the outlet opening 16.

The ribs 444 and 446 reinforce the seal between two adjacent spacers 40, whether spacers 40A or spacers 40B, while the hooks 424 and the corresponding housings 426, and possibly the hooks 425 and the corresponding housings 427, ensure a precise relative positioning between the spacers 40, within the stack E40.

We denote D4 as the stacking distance of the four support rings 24, which each have a width e24 equal to the division d. These support rings 24 provide a catch-up function between the circlips 30, in the absence of four levers 14. The lateral rings 28 and the catch-up rings 24 have the same geometry, in particular the same axial thickness.

We note L68 the length, measured parallel to the axis A22, of a stack formed of a lateral ring 28 and an axial stop 26. We note L14 the length, also measured parallel to the axis X22, of a stack formed of four levers 14 and four associated ball bearings 26.

The axial distance between the elastic washer 34 bearing against a circlip 30 and the opposite circlip 30 is equal to the sum of the quantities e24, d4, L14 and L68.

The cam mechanism 2 also comprises an arch 70 formed of a longitudinal body 72 parallel to the axis A2 and of two legs 74 perpendicular to the longitudinal body 72 and to the axis A22 and which each define a bearing not shown for the support shaft 42. The arch 70 is immobilized on the frame 4 by means of four screws 76, two of which are inserted in each of the tabs 74.

The longitudinal body 72 is pierced with two threads 71 for receiving two screws 61 for immobilizing the cover 6 on the frame 4. For the clarity of the drawing, the screws 61 are omitted at the figure 1 and reveal the corresponding passage orifices 63, provided in the cover 6 for their passage.

A tool 80 is used to move the common shaft 22 and the elements attached to this shaft, with respect to the frame 4 and around the axis A42, after removal of the cover 6, between a weaving position and a position leveling.

Leveling consists of passing the levers 14 of the so-called weaving configuration of the figures 2 to 4 , where the rollers 18 are supported on the cams 12, in the so-called leveling configuration of the figure 5 , where the rollers 18 are distant from the cams 12. The sealing spacers 40 pivot around the axis A42, with the other elements carried by the common shaft 22, during this passage between these two positions.

In leveling configuration, the levers 14 are decoupled from the drive means constituted by the cams 12, so that the camshaft 10 and the cams 12 can be removed from the frame 4 to be adapted or changed, at the choice of the weaver and depending on the armor to be made.

The cam mechanism 2 of the invention is compatible with the use of a removable leveling means constituted by a tool 80, which makes it possible to pivot the common shaft 22 around the longitudinal axis A42 of the support shaft 42 and the sealing spacers 40 around the axes A422 of their through holes 422.

The tool 80 comprises two uprights 82 and a handle 84 which connects the uprights and which is intended to be maneuvered by an operator to tilt the tool around the axis A42. For the clarity of the drawing, the tool 80 is shown partially and in axis lines at the figures 3 And 5 .

The tilting of the tool 80, in the direction of arrow F1 at the figure 2 , has the effect of moving it from the configuration shown to the figure 2 to that represented in Figure 5 , which has the effect of driving the common shaft 22 and the elements mounted on this shaft of the weaving configuration of the Figure 3 to the leveling configuration of the Figure 5 .

The tilting of the common shaft 22 of the configuration of the Figure 3 to the configuration of the Figure 5 has the effect, taking into account the centering obtained thanks to the edge 412 of the end sealing spacers 40B, of also driving these spacers in the same movement. As the different spacers 40A and 40B of the stack E40 are secured together thanks to the hooks 424 and 425, and to the housings 426 and 427, the entire stack E40 follows the leveling movement imparted to the common shaft 22 by the tool 80. This movement continues until the edge of the levers 14 comes to bear against an internal rib 44 of the frame 4 close to the edge 41, as shown in Figure 5 .

In this position, the seal 52 is away from the edge 41 and its lip 524 is not constrained.

Also in this position, the seal 54 is not in contact with the cover 6 since the latter was removed prior to the installation of the tool 80.

After modification or replacement of the camshaft 10, the levers 14 are returned to the weaving configuration by moving the common shaft from the configuration of the Figure 5 to that of the Figure 3 . This is done by tilting the tool around axis A42, in the opposite direction of arrow F1. As the stack E40 is integral with the common shaft 22 for the reasons explained above, this movement has the effect of automatically returning the joints 52 and 54 to the operational configuration, the joint 52 then being supported against the edge 41 and the seal 54 being ready to receive in support the internal surface 66 of the cover 6. The invention is therefore particularly suitable for cam mechanics which must be manipulated from a weaving configuration to a leveling configuration and vice versa.

One of the screws 76 is surrounded by a washer 78, the outer edge of which is housed in a groove not shown in the common shaft 22 in weaving configuration. This makes it possible to position the common shaft 22 axially in relation to the plates of the frame 4 on which it must be attached before immobilizing it with assembly screws 23 arranged on either side of the parts 14 to 30, 34 and 40, along axis X22. This guarantees a precise positioning of the common shaft 22 on the frame 4, therefore precise contact between the tracks of the cams 12 of the shaft 10 and the rollers 18 of the output levers 14.

Before moving from the weaving position to the leveling position, these screws 23 are removed, to allow the common shaft 22 to move relative to the frame 4.

The E40 stack shown in Figure 11 corresponds to a second embodiment of the shed forming machine of the invention where eight output levers 14 not shown are mounted around the common shaft 22. The elements identical to those of the first embodiment bear the same references. In the following, when a part of the crowd forming machine is not shown on the Figure 11 , this part is identical to the same part of the first embodiment. In this second embodiment, the stack E40 comprises six intermediate sealing spacers 40A and two end sealing spacers 40B, arranged, along the axis A40, on either side of the spacers. 40A interlayer sealing.

As previously, the grooves 316 and 346 of the different sealing spacers 40 together define two reception channels G2 and G4 for receiving the heels 522 and 542 of two seals 52 and 54 which are identical to those shown in the previous figures and whose longitudinal axes are parallel to axis A40, therefore to the longitudinal axis of the common shaft of the shed forming machine.

In fact, the parts visible on the Figure 11 are the same as those visible on the figure 8 , only the distribution between the two types of sealing spacers 40 being different.

According to other embodiments not shown of the shed forming machine of the invention, the number and distribution of the output levers 14 may be different from those mentioned above. In this case, the stack E40 is adapted accordingly, this stack E40 being made up of intermediate sealing spacers 40A and end 40B identical to those shown in the figures.

Whatever the number of levers 14, the stack E40 always includes two end sealing spacers 40B, at its ends.

In all cases, the geometry of the sealing spacers 40 makes it possible to form a sub-assembly with the intermediate sealing spacers 40A by pre-assembling them together by means of their hooks and housings 424 and 426, before bringing them back on the common shaft 22 in a direction radial to this shaft, by bringing the edges 412 of these spacers closer to the axis A22 and by inserting the lever arms 146 into the spaces left free between two intermediate sealing spacers 40A in the intermediate zone where their strips 402 have a minimum width f'402. This subassembly can then be secured with end spacers 40B threaded around the common shaft 22.

The invention is shown in the figures in the case where the sealing spacers 40 support two seals 52 and 54. It is however applicable when these spacers support a single seal, resting against a fixed part which delimits the internal volume V2 of the machine 2. The fixed part(s) against which the seal(s) comes or bear may be the frame 4, the cover 6 or another part.

According to a variant not shown of the invention, the edge 412 of an end sealing spacer 40B extends over an angular sector whose apex angle is less than 360°, while being strictly greater than 180°, preferably greater than 270°. Thus, this edge 412 constitutes in all cases a means of centering the end spacer 40B around the rings 24 or 28, therefore around the axis A22.

According to variants of the invention not shown, the shape of the heels 522 and 542 of the joints 52 and 54 and the section of the reception channels G2 and G4 may be different from those shown in the figures.

Alternatively, instead of being made of elastomer, the seals 52 and 24 can be made of polymer material or composite.

The means of connection between the sealing spacers 40 can be modified, in particular with regard to the number and shape of the hooks 424 and/or 425 and the housings 426 and/or 427. Thus, a spacer 40 may not include only one hook 424 or 425 and one housing 426 or 427, or even no such hook or housing.

Alternatively, the sealing spacers 40 do not include a hook 424 nor a housing 426 but are kept stacked along the common shaft 22 by means of a sealing gasket 52 or 54 which limits the movement of the spacers between they along the common shaft 22

According to a not shown variant of the invention, the intermediate sealing spacers 40A can be configured to receive, on their sides visible to the inserts B and C of the Figure 9 , a complementary sealing member formed by a seal which bears, in a sealed manner, on one face of an adjacent output lever, this face being perpendicular to the axis A22. This additional seal is partially housed in the intermediate sealing spacer, at its intermediate zone. Here it is applied the technical education of EP-A-3 162 933 , the contents of which are incorporated herein by reference.

Alternatively, the tool 80 can be replaced by an electric motor. In fact, the cam machine 2 is compatible with a motorized leveling drive, which allows to tilt, reversibly, the sealing device formed by parts 40, 52 and 54 with the common shaft 22 and around the axis A42, during the transition from the leveling configuration to the weaving configuration. Indeed, when leveling the heddle frames of the loom, for example when it comes to releasing the tension of the layers of warp threads, it is not necessarily necessary to access the volume V2. In this regard, the sealing device formed by parts 40, 52 and 54 can pivot around axis A42, which allows, in the leveling configuration, to separate the lips 524 and 544 of the portions 41 and 66 fixed parts 4 and 6, against which they respectively rest in the weaving configuration, while the cover 6 remains in place on the frame 4.

According to another variant of the invention not shown, it can be implemented within a dobby, instead of a cam machine. In other words, the crowd forming machine of the invention may be a dobby. In this case, each output lever is driven in its oscillating movement by an internal connecting rod of the machine.

The embodiments and variants envisaged above can be combined with each other to generate new embodiments of the invention, within the scope of the appended claims.

Claims (15)

1. A shed forming machine (2), of the mechanical cam or dobby type, for a weaving machine,

   said machine comprising:

   - output levers (14) oscillating about a common shaft (22) centered on a longitudinal axis (A22);

   - a cover (6) defining an outlet opening (16) through which the output levers pass;

   - a frame (4) that, along with the cover, delimits an interior volume (V2) of the machine; and

   - a sealing device (40, 52, 54) intended for closing the outlet opening of the hood and comprising sealing struts (40) stacked along the common shaft and arranged on either side of the output levers, as well as at least one seal (52, 54), each sealing strut comprising:

   - a band (402) that extends from a first end (404), located near the frame (4), to a second end (406), located near the cover (6), and comprises two longitudinal edges (408, 410), orthogonal to the longitudinal axis (A22) of the common shaft (22) and configured to abut at least one longitudinal edge of the band of an adjacent sealing strut; and

   - an inner radial edge (412) that defines a common shaft (22) passage opening centered on a primary axis (A40) coincident with the longitudinal axis of the common shaft at least when the machine is in the weaving configuration,

   characterized in that

   - the seal (52, 54) extends along a main direction (A52, A54) parallel to the longitudinal axis (A22) of the common shaft (22) and abuts a fixed part (4, 6) of the machine;

   - each sealing strut (40) is provided with at least one groove (416, 436) which extends parallel to its primary axis (A40) and opens out on each side of the sealing strut;

   - the grooves of the sealing struts of the sealing device (40, 52, 54) together define a channel (G2, G4) for receiving a heel (522, 542) of the seal.
2. The shed forming machine according to claim 1, characterized in that, in a plane perpendicular to the primary axis (A40), the groove (416, 436) of each sealing strut (40) is defined by a profile with a bottom (418, 438) whose width (ℓ418, ℓ438) is greater than the width (ℓ420, ℓ440) of its mouth (420, 440).
3. The shed forming machine according to any of the preceding claims, characterized in that the grooves (416, 436) of the sealing struts (40) of the sealing device (40, 52, 54) have the same profile, in a plane perpendicular to their primary axis (A40).
4. The shed forming machine according to any of the preceding claims, characterized in that the seal (52, 54) has a cross-section, perpendicular to its primary direction (A52, A54), which is constant along this primary direction and in that the length (L52, L54) of the seal, measured parallel to its primary direction, is greater than or equal to a width (ℓ16) of the outlet opening (16), measured parallel to the longitudinal axis (A22) of the common shaft (22).
5. The shed forming machine according to any of the preceding claims, characterized in that at least one of the sealing struts (40) is a spacer sealing strut (40A), in that a width of the band of this strut, measured parallel to the primary axis between its two longitudinal edges, has a first value (ℓ402) at its first and second ends (404, 406) and a second value (ℓ'402) in an intermediate area between its first and second ends that covers an angular sector of travel of an output lever (14), in that the first value is equal to the division (d) of the shed forming machine and in that the second value is equal to the division of the shed forming machine minus the thickness (e14) of an output lever, measured parallel to the longitudinal axis (A22) of the common shaft.
6. The shed forming machine according to claim 5, characterized in that the inner radial edge (412) extends around the primary axis (A40) over an angular sector with an apex angle (α) strictly less than 180°.
7. The shed forming machine according to claim 5 or 6, characterized in that the sealing device (40, 52, 54) comprises at least one complementary sealing member mounted in the outlet opening (16), partially housed in the spacer sealing strut (40A) at the intermediate area and which interacts in a sealing manner with a face of an adjacent output lever (14), this face being perpendicular to the longitudinal axis (A22) of the common shaft (22).
8. The shed forming machine according to any of the preceding claims, characterized in that at least one of the sealing struts is an end sealing strut (40B), in that a width of the band of this strut, measured parallel to the primary axis between its two longitudinal edges (408, 410), has a constant value (ℓ402), equal to the division (d) of the shed forming machine (2), from its first end (404) to its second end (406), and in that the sealing strut comprises centering means (412) in relation to the common shaft (A22).
9. The shed forming machine according to any of claims 5 to 7 and according to claim 8, characterized in that it comprises:

   - axial stops (26) arranged around the common shaft (22), on either side of each output lever (14);

   - axial fasteners (30) mounted at each end of the common shaft and configured to retain the axial stops 26 and the output levers (14) on the common shaft;

   - at least two bearing rings (24, 28), each interposed between an axial stop 26 and an axial fastener;

   in that end sealing struts (40B) are mounted around the support rings (24, 28) by the centering means (412); and

   in that spacer sealing struts (40A) are each mounted on the periphery of an axial stop (26) and each delimit a volume for the passage of an output lever (14) to the outside, through the outlet opening (16), at the intermediate area of their band.
10. The shed forming machine according to one of the preceding claims, characterized in that each sealing strut (40) comprises a housing (422) which passes through it along an axis (A422) parallel to the primary axis (A40), which opens on two opposite sides of the sealing strut and which is configured to receive a support shaft (42) and in that, preferably, the machine comprises a hoop (70) formed by a longitudinal body (72) parallel to the longitudinal axis (A22) of the common shaft (22) and two legs (74) perpendicular to the longitudinal body and which each define an articulation bearing of the support shaft (42).
11. The shed forming machine according to any of the preceding claims, characterized in that the shed forming machine (2) is of the dobby type and in that each output lever (14) is driven in an oscillating movement by an internal rod of the machine.
12. The shed forming machine according to any of claims 1 to 10, characterized in that the shed forming machine (2) is of the mechanical cam type and comprises a camshaft (10) parallel to the common shaft (22), rotation of which drives the output levers (14) in an oscillating motion and in that each strut (40) is configured to pivot between a weaving position, in which the output levers are coupled to the camshaft, and a leveling position, in which the output levers are decoupled from the camshaft.
13. The shed forming machine according to any of the preceding claims, characterized in that the sealing struts (40) include interlocking members (424-427) adapted to keep the adjacent struts stacked along the common shaft (22).
14. The shed forming machine according to any of the preceding claims, characterized in that the sealing struts (40) comprise walls (444, 446) that overlap between two adjacent sealing struts when stacked along the common shaft (22).
15. The shed forming machine according to one of the preceding claims, characterized in that a lower receiving channel (G2) of the sealing device (40, 52, 54) receives a first seal (52) which rests against a part (41) of the frame (4) facing the cover (6) in the weaving configuration of the shed forming machine (2) and an upper receiving channel (G4) of the sealing device (40, 52, 54) receives a second seal (54), which rests against a part (66) of the cover facing the frame in the weaving configuration of the shed forming machine.

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