Bearing for a shed forming machine or motion transmission system, heald movement lever equipped with such a bearing, and shed forming machine equipped with such a lever or bearing

Abstract

To provide a bearing for reducing the material fatigue of a machine.SOLUTION: A bearing (25) for a shed forming machine or a system for transmitting a motion to a frame of a loom comprises an inner ring (72), an outer ring (74) and rolling elements (76). The inner ring has two lateral surfaces vertical to a long axis and centered on a main axis line (A72), and defines a circular external peripheral ring (80) centered on the long axis line. The outer ring (74) defines the circular inner ring (72) centered on the main axis line. The inner ring (72) comprises at least one slot (90), is open onto the two lateral surfaces, extends opposite a part of the external peripheral ring (80), and forms a material bridge (94) between the slot and the external peripheral ring. The material bridge (94) extends above an angular sector (99) of the inner ring, the angular sector being centered on the main axis line (A72) of the bearing and having a vertex angle (α1) which is larger than a vertex angle (β2) of an angular sector occupied by the two rolling elements (76), or equal thereto.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present invention relates to a bearing for use in a system for transmitting motion to a shed-forming machine or to a loom frame, and to a lever of a loom mechanism equipped with such a bearing. The invention also relates to a shed-forming machine equipped with such a lever or such a bearing. [Background technology]

[0002] In the field of weaving, a loom intertwines warp and weft threads to create fabric. A shed former controls the movement of the warp threads using heddles attached to a heddle frame. Multiple heddle frames are provided depending on the complexity of the weave of the fabric to be produced.

[0003] It is known to control each heddle frame individually between high and low positions, by means of a mechanical transmission system consisting of pulling elements in the form of connecting rods and levers. Some of the levers have rollers fitted in bearings which are actuated by rotating cams. Shed formers which group together the cams and other control elements of the heddle frame are called "cam machine" types, and the mechanical transmission system connecting the shed formers and heddle frames within a loom is called the "moving transmission system" of the loom frame.

[0004] EP-A-0225266, for example, teaches a lever structure for a cam machine. The lever includes two rollers, which are jointly actuated by a rotating cam consisting of two tracks. To reduce friction, each roller includes a bearing consisting of an inner ring and an outer ring that contact each track of the cam. The outer ring is rotatable relative to the inner ring of the rolling bearing by means of rolling elements interposed between the inner and outer rings. The inner ring is solid and rigid. Such bearings have a limited service life when subjected to repeated stresses due to fatigue of the material, which is subjected to large localized repeated stresses.

[0005] For productivity reasons, shed formers operate at high frequencies. The cams rotate at high speeds, driving the heddle frame between two high and low positions, placing heavy loads on the tensioning elements. In particular, each roller is subjected to particularly high loads, as it moves at high speeds according to the cam profile and relies on the contact between the cam track and the roller's outer ring, coupled with the acceleration defined by the cam profile. Because the shed former's movement, and therefore the roller movement, alternates, the roller bearings are subjected to repeated cycles of highly localized forces in the load zone, which can lead to material fatigue, premature component failure, and roller component failure.

[0006] Due to the localized forces on the rollers at the roller / cam contact, the outer ring of the bearing is loaded and tends to ovalize due to centrifugal deformation at the level of the roller / cam load area and centrifugal deformation in the area next to the load area. However, the inner ring of the bearing is intact and rigid and undergoes little or no deformation, which geometrically leads to loss of load contact or loss of the rolling elements outside the load area and an increase in the load on the rolling elements in the axis of force, further aggravating the effects of material fatigue on the rolling elements and tracks.

[0007] Known approaches to reducing material fatigue consist of using thicker and therefore heavier parts, which increase the inertial effect and consequently generate higher forces at the rolling element level, limiting the expected benefits in terms of reduced material fatigue and therefore bearing life. These thicker parts can also cause problems of cost and size adequacy of the bearing components in the reduced space dictated by the size of the machine. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] European Patent Application Publication No. 225266 Summary of the Invention [Problem to be solved by the invention]

[0009] It is to these problems that the present invention is more particularly directed and seeks to solve by providing a bearing structure that allows for reduced material fatigue during load cycles in a similar structural space. [Means for solving the problem]

[0010] To this end, the present invention relates to a bearing intended for a system for transmitting motion to the frame of a shed-forming machine or loom. The bearing comprises an inner ring, an outer ring, and rolling elements. The inner ring is centered on a main axis and has two side faces perpendicular to the main axis, and has a circular shape centered on the main axis. Peripheral Route The outer ring is a circular ring centered on the main axis. Medial pathway The rolling elements are arranged to guide the outer ring to rotate relative to the inner ring around the main axis. Peripheral and Inner Routes According to the present invention, the inner ring is provided with at least one slot, which is Peripheral Route and a slot extending opposite to a part of the Peripheral Route The inner ring has openings on two sides forming a material bridge between the rolling elements. The material bridge extends over an angular section of the inner ring, the angular section being centered on the main axis of the ring and having an apex angle greater than or equal to the apex angle of the angular section occupied by two rolling elements, preferably greater than or equal to the apex angle of the angular section occupied by five rolling elements, more preferably greater than or equal to the apex angle of the angular section occupied by nine rolling elements, even more preferably greater than or equal to the apex angle of the angular section occupied by thirteen rolling elements, and even more preferably greater than or equal to the apex angle of the angular section occupied by thirteen rolling elements. The inner ring further comprises at least one bore for fixing the bearing.

[0011] According to the present invention, the inner ring, more precisely the slot, Peripheral RouteThe material bridge located between the inner ring and the bearing elastically deforms to ovalize the deformation of the inner ring, thereby distributing the load over an increased number of rolling elements compared to conventional bearings, limiting material fatigue and reducing the risk of premature or accidental component failure. This reduces material fatigue. Meanwhile, the load supported by each rolling element is more uniform, preventing stress peaks and further reducing material fatigue.

[0012] According to advantageous, but not essential, aspects of the invention, such a bearing may incorporate one or more of the following features taken in any technically feasible combination: The angle of the apex of the corner of the inner ring is greater than 20°, preferably greater than 70°, more preferably greater than 120°. The material bridge extends in the shape of a circular arc around the main axis of the inner ring with a constant radial width. The radial width is substantially equal to the radial width of the slot. The radial width of the material bridge is less than 30%, preferably less than 20%, more preferably less than 10% of the radius of the path of the outer ring of the inner ring, and the radial width of the material bridge is less than 30%, preferably less than 20%, more preferably less than 10% of the radius of the path of the outer ring of the inner ring. Peripheral Route is less than 10% of the radius of the route. The slot extends between two rounded ends of a diameter equal to the width of the slot. · The rolling elements are rollers. The rolling elements are balls. -The inner ring has multiple slots. · Inside The ring has two slots that are diametrically opposed to the central axis. The inner ring consists of a slot and two fixing holes.

[0013] The present invention also relates to an output lever with a driven roller of a cam mechanism, output The lever has two rollers, at least one of which has a bearing as described above. The inner ring of the bearing is output Lever web and outputThe outer ring is secured by a securing element to one or both of the flanges attached to the lever, and has a peripheral ring with a circular outer shape.

[0014] The present invention also relates to a cam-type shed former equipped with an output lever as described above.

[0015] Advantageously, the output lever oscillates between high and low positions about the axis of the cam machine as a function of the cam profile acting in contact with the peripheral track of one of the rollers, this contact being made in a radial load area adapted to the angular area of ​​the inner ring in which the slot is formed.

[0016] According to another aspect, the invention finally provides a shed-forming machine of the cam or dobby type, comprising a mechanical transmission system to the weaving machine designed around a plurality of articulation mechanisms of parallel axes, one of which comprises a bearing as described above.

[0017] Furthermore, the material bridge may be defined to extend on both sides of a centerline oriented according to the maximum intensity of the contact force between the roller and the cam, or according to the maximum value of the radial force acting on one of the articulation mechanisms of the transmission system comprising the bearing, the maximum value of the radial force being the largest during the shed formation cycle and corresponding to the radial load applied to the rolling elements.

[0018] The invention will be better understood and other advantages will become more apparent in the light of the following description, given by way of example only and made with reference to the accompanying drawings, of three embodiments of a bearing according to the invention, an embodiment of an output lever with a follower roller according to the invention, and an embodiment of a shed former also according to the invention, in which: [Brief explanation of the drawings]

[0019] [Figure 1] FIG. 1 is a schematic diagram of a shed former comprising bearings according to the first and third embodiments of the present invention, showing the shed former in the first embodiment. [Figure 2] FIG. 2 is a view showing a part of the shed former of FIG. 1, showing the shed former in a second embodiment. [Figure 3] FIG. 3 is a partial cross-sectional view taken along the plane AA shown in FIG. [Figure 4] FIG. 4 is a front view of the bearing shown in cross section in FIG. [Figure 5] FIG. 5 is a perspective view of the inner ring of the bearing of FIG. [Figure 6] FIG. 6 is a front view of a state-of-the-art bearing similar to FIG. 4, illustrating the behavior of this bearing under the influence of a load. [Figure 7] FIG. 7 is a front view of the bearing of FIG. 3, showing the behavior of the bearing under the influence of a load similar to that of FIG. [Figure 8] FIG. 8 is a front view similar to FIG. 4 of a bearing according to a second embodiment of the present invention. [Figure 9] FIG. 9 is an enlarged front view of Detail IX of FIG. 1, showing a movement transmission member that constitutes a bearing according to a third embodiment of the present invention. [Figure 10] FIG. 10 is a cross-sectional view taken along plane BB of FIG. [Figure 11] FIG. 11 is a front view of the bearing of FIG. DETAILED DESCRIPTION OF THE INVENTION

[0020] 1 shows a schematic diagram of a shed former 2 for ease of understanding. Here, the shed former 2 is a cam device.

[0021] The machine 2 comprises a frame 4, a set of main cams 6 and a set of output levers 8. In practice, a plurality of main cams 6 are mounted on a common shaft 7 and are juxtaposed along a longitudinal axis A7 of the shaft 7. Similarly, a plurality of output levers 8 are mounted on a common shaft 9 and are juxtaposed along a longitudinal axis A9 of the shaft 9. The frame 4 is fixed when the shed former 2 is in use and is used to position and control the other elements of the shed former 2. outputIt is equipped with various members necessary for driving the lever 8. A cover (not shown) closes the frame 4 at the top, output In the remainder of this document, the cams 6 and output Lever 8 is visible in FIG.

[0022] The cam 6 includes a central portion 10 and a peripheral portion 12. The central portion 10 has a cylindrical shape with a circular cross section centered on the axis A7. A hole 14 is formed through the central portion 10, and the hole 14 is formed around the axis A7.

[0023] The peripheral portion 12 extends radially relative to the central portion 10 relative to the axis A7 and defines two tracks 16, 18, each of which is output It has a profile with a radial surface offset relative to the plane of the lever 8 and is intended to come into contact with other mechanical elements, as will be explained later in this specification.

[0024] In the example shown, the cam 6 is made from a single piece of metal and the tracks 16, 18 are machined.

[0025] The cam 6 is mounted on a shaft 7 interacting with the hole 14 and is centered on an axis A7. The cam 6 is thus rotatably movable relative to the frame 4 about the axis A7, the rotational movement of the cam 6 being represented by the arrow F6 in Figure 1 being controlled by drive means (not shown) known per se.

[0026] The output lever 8 comprises a web 20, two flanges 22 and two drive rollers 23, 24. The rollers 23, 24 each comprise a bearing 25, which is in accordance with the first embodiment of the invention.

[0027] output The web 20 of the lever 8 is of plate-like construction, preferably made of metal, and comprises a central portion 26 traversed by a circular hole 28 and centred on the axis A9.

[0028] Axis A9 is parallel to axis A7, and output lever 8 is mounted for pivotal movement relative to frame 4 about axis A9 by means of bearings which interact with bore 28 and axis 9. These bearings are not shown.

[0029] output Lever 8 web The central portion 26 further includes two extensions 30 and two arms 32. The extensions 30 and the arms 32 are connected to the central portion 26, and the extensions 30 and the arms 32 extend radially relative to the axis A9, which extends in different directions from each other.

[0030] In the illustrated example, the arm portion 32 and one of the two extension portions 30 each extend in a direction opposite to the other with respect to the axis A9, and the other extension portion 30 extends in a direction forming a right angle with the direction of the first extension portion, with the apex of the right angle being located on the axis A9.

[0031] The two flanges 22 are each secured by a fixing element 34. output It is fixed to one or the other of the lateral surfaces of the web 20 of the lever 8 and has a contour superimposed on the contour of the respective extension 30 in a direction parallel to the axis A9.

[0032] In the example shown, the flange 22 is made of metal and the fastening element 34 is, for example, in the form of a screw-nut pair or in the form of another rivet.

[0033] Each of the flanges 22, in interaction with the extension 30 to which it is fixed, defines a volume for accommodating one of two drive rollers 23 or 24 arranged along one of the two lateral surfaces of the web 20. In FIG. 1, roller 23 is arranged at a higher position than roller 24.

[0034] Advantageously, the bearings 25 of the rollers 23, 24 have the same structure and operate in the same manner, the detailed structure of the bearings 25 being described later in this specification.

[0035] Each drive roller 23 or 24 is mounted to the output lever 8 via a bearing 25 by means of a fixing element 36 which interacts in concert with the flange 22 and the web 20 of the output lever 8 .

[0036] Each fixed element 36 defines an axis A36 which is parallel to the axis A9 of the output lever 8 and therefore to the axis A7 of the cam 6.

[0037] In the example shown, the fastening elements 36 are rivets.

[0038] The shape of the cam 6, particularly the contours of the tracks 16, 18, and the relative positioning of the cam 6, output lever 8 and drive rollers 23, 24 are designed so that each drive roller 23, 24 is in permanent contact with either of the respective tracks 16, 18.

[0039] It will be appreciated that the continuous rotational movement of the cam 6, represented by the arrow F6, is translated into a reciprocating oscillating movement of the output lever 8. output The pivoting movement of the lever 8 is represented by arrows F8 and F9 in FIG. 1, which represent the movement of one end of the arm 32 away from the axis A9.

[0040] The cam machine 2 further includes a mechanical transmission system 38 that connects the output lever 8 to the heddle frame 40. In the illustrated example, the transmission system 38 includes an adjustable clip 42, a roller transmission 44 with bearings 45, a drive rod 46, a drive lever 48, a link 50, and a frame attachment 52 connected to one end of the frame 40. A link (not shown) connected to the drive lever 48 connects the drive lever 48 to another lever of the same type located near the other end of the frame 40, not shown.

[0041] The bearings 45 of the rollers 44 are bearings according to a second embodiment of the invention, which will be described in more detail later in this specification.

[0042] The position of the clip 42 along the arm 32 is adjustable by the user by means of an adjustment member 54 which influences the geometrical shed parameters of the frame 40. The roller 44 is fixed to the clip 42. Once the position of the clip 42 relative to the arm 32 is defined, the transfer roller 44 becomes integral with the arm 32, i.e. the transfer roller 44 follows the swinging movement of the arm 32 as indicated by the arrows F8 and F9.

[0043] The transmission roller 44 defines a pivot axis A44, which is parallel to the axes A9 and A7.

[0044] The drive rod 46 has an elongated shape defining a longitudinal axis A46 and includes a first end 56 and a second end 58 opposite the first end 56.

[0045] The first end 56 is attached to the transmission roller 44 so as to rotate about a pivot axis A44.

[0046] The adjustable clip 42, drive roller 44, and drive rod 46 together provide a kinematic pivotal connection about axis A 44. The construction of the transfer roller 44 and the construction of the drive rod 46 and clip 42 assembly will be described in more detail later in this specification.

[0047] The drive lever 48 has a double L-shaped baffle shape and is made up of a plate-shaped body 60 defining a first end 62 and a second end 64 opposite the first end 62. The first end 62 is centered on an axis A62 and rotates about the axis A62. Drive It has a hole for receiving a connecting member (not shown) that can ensure rotational movement of the connecting rod 46 relative to the lever 48.

[0048] Similarly, the second end 64 is oriented about an axis A64 such that the first end 66 of the rod 50 is Drive A hole (not shown) is provided to receive a connecting member connectable to the second end 64 of the lever 48, and the connecting member extends about an axis A64. Drive This allows for relative rotational movement of the rod 50 with respect to the lever 48 .

[0049] The link 50 further includes a second end 68 opposite the first end 66 to which the clip to the frame 52 is secured.

[0050] The drive lever 48 further comprises a central bore 70, which is spaced apart from the first end 62 and the second end 64 and is centred on an axis A70. The central bore 70 accommodates a number of coupling members which, on the one hand, are integral with the frame (not shown) of the loom comprising the frame 40 and, on the other hand, allow a rotational movement of the drive lever 48 about the axis A70.

[0051] The axes A62, A64, and A70 are parallel to each other and to the axes A7 and A9.

[0052] It will be appreciated that the mechanical transmission system 38, comprising multiple articulations about axes A62, A64 and A70, enables the oscillating movement of the output lever 8, indicated by arrows F8 and F9, to be transmitted to an amplified vertical oscillating movement of the heddle frame 40, indicated by arrows F40 and F41.

[0053] The heddle frame 40 swings between two high and low positions, and by extension: output It may be noted that the lever 8 itself oscillates between two high and low positions.

[0054] In Figure 1, the cam 6 is shown in a first angular position relative to the frame about axis A7. In Figure 2, the cam 6 is shown in a second angular position relative to frame 4 which is different from the angular position shown in Figure 1. As the cam 6 makes one revolution about axis A7, the machine 2 performs a so-called "shed formation" cycle.

[0055] The drive roller 23 approaches the axis A7 passing from the configuration of FIG. 1 to the configuration of FIG. 2 by rotating the cam 6 in the direction of the arrow F6, so that outputLever 8 oscillates about axis A9 in the direction of arrow F8. As cam 6 continues to rotate in the direction of arrow F6, the contours of tracks 16, 18 interacting in concert with drive rollers 23, 24 continuously generate a reciprocating oscillating motion in the directions of arrows F8, F9 which is captured by mechanical transmission system 38 and causes frame 40 to move alternately in the directions of arrows F40 and F41.

[0056] FIG. 3 shows, in cross section, the cam 6 and the roller 23, which is one of the extensions 30. output It is attached as a yoke between one of the flanges 22 of the lever 8 and is fixed by a fixing member 36 .

[0057] The roller bearing 25 of the roller 23 includes an inner ring 72 , an outer ring 74 , and a rolling element 76 .

[0058] The bearing 25 is also shown in FIGS. 4 and 7, and the inner ring 72 is shown in isolation in perspective view in FIG.

[0059] The inner ring 72 is formed in a plate shape, is preferably made of metal, and has a circular outer shape centered on the main axis A72. Inside The ring 72 has two radially extending side surfaces 78 parallel to the major axis A72, a circular base centered on the major axis A72, and a cylindrical shape with a radius R80. Peripheral Route Define 80.

[0060] The outer ring 74 is made of a metal plate and has an annular shape. It has a cylindrical shape with a circular base centered on the axis A72. Medial pathway The inner ring 82 defines the inner ring 72. Peripheral Route 3, the ring 74 has a trapezoidal radial cross section with parallel or nearly parallel rings and blanks that converge in a centrifugal direction relative to the axis A72.

[0061] Medial pathway 82 and Peripheral Route 80 define a volume therebetween for accommodating the rolling elements 76. In other words, the rolling elements 76 are Peripheral Route 80 and Medial pathway 82, which are radially interposed with respect to the main axis A72. The rolling elements 76 are designed to guide the outer ring 74 in rotation relative to the inner ring 72 about the main axis A72.

[0062] In the illustrated example, the rolling element 76 is a cylindrical roller, the axis of which is parallel to the main axis A72.

[0063] In a variant not shown, the rolling elements of the set of rolling elements 76 may be balls or tapered rollers, examples of which are not limiting.

[0064] The bearing 25 further comprises two flanges 84 located on either side of the inner disc side surface 78, each of which axially retains the rolling element 76 relative to the axis A72; and Peripheral Route 80 and Medial pathway 3 and extends radially relative to axis A72 to retain the rolling element 76 within a volume bounded by 82. Flange 84 is visible in FIG. Peripheral Route 80 and medial pathway 82, and serves to guide and accommodate the rolling element 76 in the axial direction within the receiving volume formed between the outer ring 74 of the bearing 25. output Between it and the surface of the flange 22 of the lever 8, it serves to define an offset space for free rotation about the axis A72.

[0065] outer ring 74 further includes an outer track 86 which is a cylindrical surface of circular cross section centered on the major axis A72.

[0066] The bearing 25 also includes a fixing hole 88. The fixing hole 88 is formed in the inner ring 72 and fixes the roller 23. output It interacts with the fixing member 36 for attachment to the lever 8. In the example shown, the hole 88 is centered on the main axis A72.

[0067] The inner ring 72 is fixed to the output lever 8 in this manner, and the outer ring 74 is supported on the output lever 8 so as to be rotatable about the main axis A72.

[0068] It should be understood that the outer ring 74, which is in contact with one of the tracks 16 or 18 of the cam 6 via the outer track 86, "rolls" on the corresponding track 16 or 18, reducing friction and wear of the parts. In this sense, the outer track 86 is the peripheral rolling track of the outer ring 74.

[0069] As a result, the force generated by contact of track 16 or 18 on roller 23 is directed radially relative to main axis A72, whatever the angular position of cam 6 and whatever the location of contact between cam 6 and outer track 86 of outer ring 74.

[0070] The inner ring 72 further comprises a slot 90. The slot 90 is formed in the thickness of the inner ring 72 and opens onto two side surfaces 78. The slot 90 separates a central section 92 of the inner ring 72 from a material bridge 94, radially relative to the main axis A72. Peripheral Route 80. In other words, the slot 90 Peripheral Route 80. "Facing" means that the slot 90 is also Peripheral Route Near 80 Peripheral Route 80, or the slot 90 Peripheral Route 80 or part of the outline of the slot 90 Peripheral Route This means that it is close to part of the outline of 80.

[0071] The slot 90 has an inner edge 96 and an outer edge 98 that are interconnected by two connectors 100 that comprise the rounded ends of the slot 90 .

[0072] In the illustrated example, the inner edge 96 and the outer edge 98 are cylindrical sections centered on the major axis A72, and the mating portion 100 is also a cylindrical section of circular cross section centered on a respective axis A100, which is parallel to the major axis A72. In particular, the spacing between the inner edge 96 and the outer edge 98 is constant.

[0073] The inner edge 96 and the outer edge 98 define therebetween a radial width L90 of the slot 90 measured radially relative to the axis A72. Similarly, the radial width L94 of the material bridge 94 is defined as the width measured radially relative to the major axis A72 between the outer edge 98 of the slot 90 and the outer track 86 of the outer ring 74.

[0074] The angular section 99 is defined as a dihedron centered on the axis A72, with its sides passing through the axis A100 of the mating portion 100. The angular section 99 is shown in gray in Figure 4. Here, the angle formed by the main axis A72 connecting the axes A100 of the two mating portions 100 is denoted as α1. Therefore, the angle of the vertex α1 of the angular section 99 of the inner ring 72 represents the angular range of the slot 90 and the angular range of the material bridge 94 together.

[0075] Let us consider plane P1 as a plane passing through axis A7 of cam 6 and axis A72 of bearing 25. Let us also consider load angle β as a measurement of the angle between plane P1 and the contact position between outer ring 74 of bearing 25 and cam 6, carried by main axis A72 of bearing 25. In Figure 1, load angle β is assumed to be non-zero. In Figure 2, cam 6 is in a different position than in Figure 1, and load angle β is zero.

[0076] More generally, it will be appreciated that during the shed formation cycle the intensity and location of application of the contact force between the roller 23 and the cam 6 varies periodically.

[0077] This contact location moves alternately on either side of plane P1, and the load angle β alternates between two extreme values, taking positive or negative values, defining a radial load area of ​​bearing 25. In this way, the force exerted by cam 6 on roller 46 has a periodically varying direction and intensity. In particular, the force on rolling element 76 has a maximum value during the shed formation cycle.

[0078] In the illustrated example, the plane P1 is a plane of symmetry with respect to the inner ring 72 of the bearing 25, in other words, the plane P1 is a plane of symmetry with respect to the slot 90 of the bearing 25.

[0079] Figure 6 shows the results of a numerical simulation of the behavior of a state-of-the-art bearing comprising an inner ring 72', an outer ring 74' and rolling elements 76'. This state-of-the-art bearing 25' has a similar structure to bearing 25 according to the first embodiment of the invention, with one difference being that bearing 25' does not comprise slots of the type of slot 90 and does not comprise material bridges of the type of material bridge 94. Figure 7 shows the results of a numerical simulation of the behavior of bearing 25 of Figures 3 to 5 and 7 according to the first embodiment of the invention.

[0080] In Figures 6 and 7, the bearing 25 or 25' is subjected to a force of the same magnitude and direction, represented by the arrow F1, directed towards the bearing's main axis A72. This force results from the driving torque of the camshaft, in combination with the forces of the frame 40 and the tension elements, which act on and weight the bearing 25 or 25' in question during movement. The deformation of the parts under the influence of force F1 is represented in an exaggerated manner in Figures 6 and 7 to illustrate the effect of the invention. The direction and magnitude of the force resulting from the contact force at the level of each rolling element 76 are represented by arrows, the direction of which is the force resulting from the rolling element's contact force and the length of which is proportional to the magnitude of the resulting force.

[0081] In Figure 6, outer ring 74' is elliptical in the direction perpendicular to the direction of arrow F1, while inner ring 72' shows no deformation. Furthermore, only 15 rolling elements 76' are in contact with outer ring 74'. The longest arrow is indicated in Figure 6 by arrow F6, which represents the maximum contact force of bearing 25 under load.

[0082] In Figure 7, the outer ring 74 has a deformation similar to that of the outer ring 74' of a roller according to the state of the art, while the inner ring 72, in its part, is elastically deformed under the action of the roller force F1. Meanwhile, the force is applied to 19 rolling elements 76. The elastic deformation of the inner ring 72, exaggerated by the crushing of the slots 90, allows more rolling elements 76 to generate a resulting force in response to the application of force F1. The arrow representing the maximum contact force of the bearing under load is indicated by F7 in Figure 7.

[0083] In the example shown, the arrow F7 has a length that is approximately half as long as the arrow F6, in other words, the maximum force that can be received by the rolling elements 76 of the bearing 25 according to the invention is approximately half or less of the maximum force that can be received by the rolling elements 76' of the bearing 25, which is particularly advantageous for reducing material fatigue, according to those skilled in the art.

[0084] As noted above, the load angle β varies continuously between two extreme values ​​during operation on either side of plane P1, and therefore the angular section 99 of slot 90 must have a sufficiently large angle at apex α1 to ensure sufficient elastic deformation of inner ring 72 whatever the value of load angle β.

[0085] According to an embodiment, the loading area is aligned with the angular section 99 of the slot 90. According to another embodiment, the slot 90 extends on either side of a center line oriented according to the maximum intensity of the contact force between the bearing 25 and the cam 6. According to another embodiment, the slot is symmetrical about the mid-plane, which itself symmetrical in extent of the rolling area between the cam 12 and the rollers 23, 24 throughout the shed formation cycle.

[0086] In practice, the slot 90 extends over an angular section 99 of the inner ring 72, with an apex angle α1 greater than 20°. Preferably, the apex angle α1 is greater than 70°, and more preferably greater than 120°. Conversely, it will be appreciated that an apex angle α1 that is too large risks weakening the inner ring 72 over the extent of the corresponding material bridge 94, which is the opposite of the desired effect. In practice, values ​​of the apex angle α1 are less than 160°, especially when the thickness of the material bridge 94 is limited.

[0087] Because the force experienced by the drive roller 23 is distributed among the rolling elements 76, the apex angle α1 of the angular section 99 may be expressed as a function of the number of rolling elements 76 across which the load is distributed.

[0088] 4, β2 is defined as the angle at the vertex of the angular section of the inner ring 72 corresponding to the angular section occupied by two consecutive rolling elements 76. Similarly, the angles at the vertices β5, β9, and β13 are defined as angular sections of the inner ring 72 corresponding to the angular sections occupied by 5, 9, and 13 consecutive rolling elements 76, respectively.

[0089] Thus, slot 90 extends over section 99 where vertex angle α1 is greater than or equal to vertex angle β2. Preferably, vertex angle α1 is greater than or equal to vertex angle β5. More preferably, vertex angle α1 is greater than or equal to vertex angle β9. Even more preferably, vertex angle α1 is greater than or equal to vertex angle β13.

[0090] When a contact force is applied to the bearing 25, the radial width L90 of the groove 90 is preferably large enough so that the inner peripheral edge 96 and the outer peripheral edge 98 do not come into contact with each other due to the load applied to the roller 23.

[0091] Therefore, the slots are Outer periphery The path 80 must have a width L90 that is 5% or more of the radius R80. Preferably, the width L90 is greater than 10% of the radius R80. More preferably, the width L90 is greater than 20% of the radius R80.

[0092] Under the influence of a load, the material bridge 94 will deform elastically. Conversely, a material bridge 94 having too large a radial width L94 will be too stiff and will not deform under the influence of a load. Therefore, the material bridge 94 has a radial width L94 that is less than 30%, preferably less than 20%, and more preferably less than 10% of the radius R80 of the outer circumferential path 80 of the inner ring 72.

[0093] Conversely, it will be appreciated that if the radial width L94 of the material bridge 94 is too small, there is a risk that the material bridge 94 will weaken or even plastically deform, which is undesirable. This is why in practice the width L94 is greater than 20% of the radius R80. Those skilled in the art will of course know how to determine the permissible limits of the radial width L94, which will depend, inter alia, on the shape of the slot 90, the load cycles to which the bearing 25 is subjected, and the material of the inner ring 72.

[0094] In the illustrated example, the radial width L94 of the material bridge 94 is substantially equal to the radial width L90 of the slot 90. By "substantially equal," it is intended to mean that the radial widths L90 and L94 are equal to within 50%, preferably within 20%, of each other.

[0095] In second and third embodiments of the bearing according to the present invention shown in Figures 8 and 9 to 11, respectively, elements similar to those in the first embodiment have the same reference numerals, etc., and operate in the same manner. The following description will focus on the differences between the second and third embodiments and the first embodiment.

[0096] A bearing 102 according to a second embodiment of the present invention is shown in FIG.

[0097] The bearing 102 includes a disk-shaped inner ring 172 centered on an axis A 172 and having two side surfaces 78. Peripheral Route 180. The inner ring 172 is Peripheral Route 180 and outer ring 174 Medial pathway 82, by a rolling element 176 interposed between the outsideIt is rotatable relative to the wheel 174 .

[0098] Inside The wheel 172 comprises a first half-disk 104 and a second half-disk 106 that is complementary to the first half-disk 104 .

[0099] Two fixing holes 188 are formed through the first semicircular plate 104. In the illustrated example, the two holes 188 are formed in the intermediate portion between the axis A172 and the outer peripheral path 180, and are symmetrically arranged on either side of the plane of symmetry of the first semicircular plate 104, which is represented by the vertical line in FIG. 8. Advantageously, the fixing of the inner ring to the output lever according to this embodiment is performed by fixing the inner ring to the output lever along the fixing axis A36. output This allows the lever 8 to be brought closer to the axis A9, thereby output It becomes possible to reduce the dimensions of the lever 8 and, more generally, the construction volume of the machine, which is advantageous for the weight and mechanical constraints of its components.

[0100] A slot 190 is formed in the inner ring 172 and opens onto its two side surfaces 78. In the example shown in Figure 8, the slot 190 is formed substantially within the second half-disk 106.

[0101] Slot 190 has the shape of a portion of a disk, with an arcuate outer edge 198 of a circle and an inner edge 196 formed by two flat surfaces 108. The surfaces 108 are connected to each other by cylindrical connectors centered on axis A 172 opposite outer edge 198 with respect to axis A 172. Outer edges 198 are connected to each of flat surfaces 108 by respective connectors 110. Connectors 110 are portions of a cylinder centered on respective axes parallel to major axis A 172. Slot 190 extends over an angular section 199 centered on major axis A 172, with its apex angle designated α2 measured between the axes of fittings 110 and about axis A 172.

[0102] In the illustrated example, the apex angle α2 of the angular region 199 is substantially equal to 120° and corresponds to the apex angle of the angular region occupied by the 18 rolling elements 176. Therefore, it is larger than the angles defined as the angles β2, β5, β9, β13 according to the first embodiment.

[0103] The slot 190 Peripheral Route extends under a part of 180 and forms a material bridge 194 between the outer surface 198 and Peripheral Route 180. In the illustrated example, the material bridge 194 extends along an arc of a circle centered on the main axis A172 and has a constant radial width L194.

[0104] More generally, the shape and position of the slot 190, and the number and position of the fixing holes 188 are determined during the design of the bearing 102 so as to ensure a firm fixation of the bearing 102 by the positioning and size of the fixing elements on the inner ring 172, and a good distribution of the loads received by the rolling elements 176 due to the elastic deformation of the inner ring 172.

[0105] The bearing 45 of the third embodiment consists of an inner ring 272 centered on the axis A44 of the roller 44. The axis A44 is also the main axis of the inner ring 272. The inner ring 272 Peripheral Route defines 280, Peripheral Route and is rotatable relative to the ring 274 about the axis A44 by rolling elements 276 interposed between 280 and the inner ring 282 of the outer ring 2 74. outside is rotatable relative to the ring 274 about the axis A44 by rolling elements 276 interposed between 280 and the inner ring 282 of the outer ring 74. <​​​The position of clip 42 along arm 32 of lever 8 is adjustable by the operator, while during normal operation of cam arrangement 2 head 204 is integral with output lever 8, i.e., in continuous contact with no play or possibility of relative movement between these parts.

[0107] The head 204 has a central hole formed therein in which the bearing 45 is housed. More specifically, the outer ring 274 of the bearing 45 is received without play within the central hole of the head 204 of the clip 42. In a non-limiting embodiment, the head 204 has a central hole. The bearing 45 is assembled to the clip 42 by, for example, shrinking or welding.

[0108] The drive rod 46 includes two fixing flanges 208 in extension to the first end 56. The flanges 208 each have a hole 210, which is disposed opposite one another and whose walls converge toward one another near the holes 210. The flanges 208 interact with the holes 288 for securing the inner ring 272, and the holes 210 accommodate fixing elements 212 that can secure the flange 208 assembly to the inner ring 272. In the illustrated example, the fixing elements 212 are a screw and nut pair.

[0109] Thus, the drive rod 46 is integral with the inner ring 272 and the ring 74 is head It is integral with the output lever 8 via 204.

[0110] 11, the inner ring 272 is provided with two slots 290, 291. Each slot 290, 291 is here similar to the slot 90 of the bearing 25 of the first embodiment. Each slot 290, 291 opens onto two lateral surfaces 78 of the inner ring 272 and here diametrically opposes the central axis A44. More precisely, the slots 290, 291 are arranged symmetrically on either side of a transverse plane P2, which is perpendicular to the axis A202 of the caliper 202 and contains the axis A44 of the roller 44. In the illustrated example, the slot 290 is positioned closer to the slot 291 than the slot 291. output Close to lever 8.

[0111] Slot 290 defines angular section 299 having vertex angle α3, and slot 291 defines angular section 300 having vertex angle α4. In the illustrated example, angular sections 299 and 300 each encompass angular sections occupied by four rolling elements 276, whose respective vertex angles α3 and α4 are substantially equal to 70°. Thus, angles α3 and α4 are greater than the angle defined as angle β2 in the first embodiment.

[0112] In the illustrated example, the slots 290, 291 have the same shape and the angular sections α3, α4 are equal to each other.

[0113] During the shedding cycle, as the output lever 8 moves in the direction of arrow F9, the drive rod 46 output The lever 8 is pushed back, and the inner ring 272 is in compression against the side of the slot 290. Similarly, when the output lever 8 moves in the direction of arrow F8, the drive rod 46 output Pulled by lever 8, inner ring 272 is in compression on the side of slot 291. It will be appreciated that in the third embodiment, bearing 45, and in particular material bridge 294 or 295 associated with each slot 290 or 291 of inner ring 272, is urged in compression alternately on one side or the other of plane P2.

[0114] Each slot 290 or 291 allows for distribution of forces exerted on the rolling elements 276 during repeated cycles of compression or traction of the drive rod 46 .

[0115] More generally, since the inner ring 272 is primarily subjected to annular compressive forces oriented in two different directions defining two different load areas, the slots 290, 291 are arranged about the axis A44 aligned in respective ways with the load areas so as to promote the distribution of the forces acting on the set of rolling elements 76 in the directions of said forces.

[0116] According to a variant of the invention (not shown), the slots 290, 291 each extend on either side of a centerline oriented according to the maximum intensity of the radial force exerted by the transmission system 38 on the bearing 45.

[0117] According to another variant (not shown), the slots are arranged symmetrically about the mid-plane and are themselves located on the inner ring 272. output The radial force exerted by the lever 8 loading The range of the area is symmetrical.

[0118] In a variant (not shown), the inner ring 272 may be provided with more than two slots of the type 290, 291 so as to distribute the forces exerted by the rolling elements of the set of rolling elements 276.

[0119] More generally, in the example shown, bearing 25 comprises a single slot 90 and fixing hole 88. In a variant (not shown), a bearing of the type of bearing 25 may comprise two fixing holes similar to the holes of bearing 102, or in a different arrangement. According to another variant, a bearing of the type of bearing 25 may comprise two or more slots similar to slots 290 or 291 of the third embodiment.

[0120] Likewise, in a variant (not shown), the bearing 102 of the roller 44 may comprise only a single slot of the type of slot 94 or 194 .

[0121] In all embodiments, the apex angle α1, α2, α3 or α4 of the angular section 99, 199, 299 or 300 and the radial width L90 of the slot of the type of slot 90 may be defined during the design of the inner ring 72, 172 or 272 as a function of the load angle β and the magnitude of the forces to which the bearing 25, 102 or 45 is subjected during shed formation. Similarly, the radial width L94 of the material bridge 94 or equivalent delimited by the slot 90 may be adjusted during design and manufacture depending on the type of forces and their distribution expected during use.

[0122] Slots of the type slot 90 or slots 290, 291 extend along an arc of a circle about the main axis of the inner ring, such as slot 90 about axis A72 of inner ring 72. In a variant (not shown), the slot may extend along an arc of a circle about an axis offset from axis A72. According to yet another variant, the slot may not have a constant curvature, but a continuously varying curvature.

[0123] According to another variant (not shown), the bore 88 formed in the inner ring opens onto a single face of the inner ring of the bearing for assembly thereof. output It is replaced by one or more recesses that can interact with the lever 8 .

[0124] According to another variant (not shown), the width L94 of the material bridge 94 formed by the slot 90 together with the circumferential path 80, measured radially relative to the axis A72 between the outer edge 98 and the circumferential path 80, is not constant but varies continuously, for example to accommodate the forces experienced by the roller, which vary as a function of the load angle β. Thus, certain areas of the material bridge may be stiffened by increasing their radial thickness L94, while other areas may be stiffened by decreasing their radial thickness L94, depending on the local stresses imposed by the cycles of the machine 2.

[0125] In the example shown in Figures 1 to 5, the shed former 2 comprises a cam machine with rollers 23, 24, each of which is provided with a bearing 25 according to a first embodiment of the invention.

[0126] More generally, the rollers of this cam machine may be equipped with bearings of the type 25, 102 or 45, which reduces the risk of bearing failure and allows the productivity of the cam machine to be increased. For example, the cam may be equipped with bearings of the type 25, 102 or 45, due to longer maintenance intervals, higher speeds of the shed former 2 and more severe accelerations. of 6 outside Shape By at least one of the above changes, productivity of the cam machine can be improved.

[0127] According to a variant of the invention not shown, the shed former is of the dobby type and is provided with a mechanical motion transmission system similar to transmission system 38, which comprises bearings of the type of bearing 45. For example, axis A62 or axis A64 may define an articulation mechanism with bearings of the type of the invention.

[0128] The above-described embodiments and variations may be combined with each other to create new embodiments of the present invention. The present application may provide the following aspects, for example: [Point 1] A bearing (25, 102, 45) for a system for transmitting motion to a frame of a shed-forming machine or a loom, comprising an inner ring (72, 172, 272), an outer ring (74, 174, 274), and rolling elements (76, 176, 276), the inner ring is centered on a major axis (A72, A172, A44) and has two side surfaces (78) perpendicular to the major axis, defining an outer ring (80, 180, 280) centered on the major axis; the outer ring (74, 174, 274) defines an inner ring (82) that is circular and centered on the major axis; the rolling elements (76, 176, 276) are interposed between the outer ring and the inner ring in a radial direction relative to the main axis so as to guide the outer ring relative to the inner ring which rotates around the main axis, In the bearing (25, 102, 45), the inner ring (72, 172, 272) has at least one slot (90, 190, 290, 291) that opens on two side surfaces (78) and extends opposite a portion of the path of the outer bearing (80, 180, 280), and the inner ring (72, 172, 272) forms a material bridge (94, 194, 294, 295) between the slot and the outer ring; the material bridge (94, 194, 294, 295) extends over an angular section (99, 199, 299, 300) of the inner ring, the angular section being centered on the main axis (A72, A172, A44) and having a vertex angle (α1, α2, α3, α4) that is equal to or greater than the vertex angle (β2) of the angular section occupied by the two rolling elements (76, 176, 276), the angular section preferably has a vertex angle (β13) greater than or equal to the vertex angle (β5) of the angular section occupied by five rolling elements, more preferably greater than or equal to the vertex angle (β9) of the angular section occupied by nine rolling elements, more preferably greater than or equal to the vertex angle (β13) of the angular section occupied by thirteen rolling elements, The inner ring (72, 172, 272) further comprises at least one hole (88, 188, 288) for fixing the bearing (25, 102, 45). A bearing (25, 102, 45) characterized in that: [Point 2] The bearing (25, 102, 45) according to aspect 1, characterized in that the apex angles (α1, α2, α3, α4) of the angular sections (99, 199, 299, 300) of the inner ring (72, 172, 272) are 20° or greater, preferably 70° or greater, more preferably 120° or greater. [Point 3] A bearing (25, 102, 45) according to aspect 1 or 2, characterized in that the material bridge (94, 194, 294, 295) extends with a constant radial width (L94, L194, L294, L295) along an arc of a circle centered on the main axis (A72, A172, A44) of the inner ring (72, 172, 272). [Point 4] A bearing (25) according to aspect 3, characterized in that the radial width (L94) is substantially equal to the radial width (L90) of the slot (90). [Point 5] A bearing (25) according to aspect 4, characterized in that the radial width (L94) of the material bridge (94) is 30% or less, preferably 20% or less, more preferably 10% or less of the radius (R80) of the outer ring (80) of the inner ring (72). [Point 6] A bearing (25, 45) according to any one of aspects 1 to 5, characterized in that the slot (90, 290, 292) extends between two rounded ends (100) of a diameter equal to the width (L90, L290, L291) of the slot. [Point 7] A bearing (24, 102, 45) according to any one of aspects 1 to 6, characterized in that the rolling elements (76, 176, 276) are rollers. [Point 8] A bearing (25, 102, 45) according to any one of aspects 1 to 6, characterized in that the rolling elements (76, 176, 276) are balls. [Point 9] A bearing (45) according to any one of aspects 1 to 8, characterized in that the inner ring (272) is provided with a plurality of slots (290, 291). [Point 10] A bearing (45) according to aspect 9, characterized in that the ring comprises two slots (290, 291) radially opposed relative to the central axis (A44). [Point 11] Aspects 1 to 8. The bearing (102) according to any one of aspects 1 to 8, characterized in that the inner ring (172) comprises one slot (190) and two fixing holes (188). [Point 12] In the output lever (8) with a cam mechanism follower roller, the lever has two rollers (23, 24), At least one of the rollers A bearing (25, 102) according to any one of aspects 1 to 11; the inner ring (72, 172) of the bearing fixed by a fixing element (36) to one or both of the core (20) of the lever and a flange (22) attached to the lever; the outer ring (74, 174) having a peripheral rolling track (86) with a circular outer shape; An output lever (8) characterized by comprising: [Point 13] A cam-type shed forming machine (2) characterized by comprising the output lever (8) according to aspect 12. [Point 14] In the shed forming machine (2) according to aspect 13, The shed forming machine (2) is characterized in that the output lever (8) oscillates between a high position and a low position around the main axis (A9) of the cam machine according to the contour (16, 18) of the cam (6) which acts in contact with the outer peripheral rolling track (86) of one of the rollers (23, 24), and the contact occurs within a loading area radially aligned with the angular section (99, 199) of the inner ring (72, 172) in which the slot (90, 190) is formed. [Point 15] A cam or dobby type shed forming machine (2) comprising a mechanical transmission system (38) to the loom designed around a plurality of articulation mechanisms between parallel axes (A62, A64, A70), one of the plurality of articulation mechanisms comprising a bearing (45) according to any one of aspects 1 to 11. [Point 16] In the shed forming machine (2) according to any one of aspects 14 or 15, The material bridge (94, 194, 294, 295) extending on both sides of a centerline oriented according to the maximum intensity of the contact force between the rollers (23, 24) and the cam (6) or according to the maximum value of the radial force of one of the joints of the transmission system (38) comprising the bearing (45); The shed forming machine (2) is characterized in that the maximum value of the radial force corresponding to the radial load applied to the rolling elements (76, 176, 276) is greatest during the shed forming cycle.

Claims

1. A bearing (25, 102, 45) for a system for transmitting motion to a frame of a shed-forming machine or a loom, comprising an inner ring (72, 172, 272), an outer ring (74, 174, 274), and rolling elements (76, 176, 276), the inner ring is centered on a major axis (A72, A172, A44), has two side surfaces (78) perpendicular to the major axis, and defines an outer circumferential path (80, 180, 280) centered on the major axis; the outer ring (74, 174, 274) defines an inner path (82) that is circular and centered about the major axis; the rolling elements (76, 176, 276) are interposed between the outer peripheral path and the inner path in a radial direction relative to the main axis so as to guide the outer ring relative to the inner ring which rotates around the main axis, In the bearing (25, 102, 45), the inner ring (72, 172, 272) comprises at least one slot (90, 190, 290, 291), the at least one slot opening on the two side surfaces (78) and extending along a portion of the circumferential path (80, 180, 280), forming a material bridge (94, 194, 294, 295) between the slot and the circumferential path; the material bridge (94, 194, 294, 295) extends over an angular section (99, 199, 299, 300) of the inner ring, the angular section being centered on the main axis (A72, A172, A44) of the bearing and having a vertex angle (α1, α2, α3, α4) greater than or equal to the vertex angle (β2) of the angular section occupied by two rolling elements (76, 176, 276); The radial width (L94, L194, L294, L295) of the material bridge (94, 194, 294, 295) is greater than 20% of the radius (R80) of the outer circumferential path (80, 180, 280) of the inner ring (72, 172, 272); The inner ring (72, 172, 272) further comprises at least one hole (88, 188, 288) for fixing the bearing (25, 102, 45). A bearing (25, 102, 45) characterized by:

2. 2. The bearing (25, 102, 45) of claim 1, wherein the angular section (99, 199, 299, 300) has a vertex angle (α1, α2, α3, α4) that is equal to or greater than the vertex angle (β5) of the angular section occupied by five rolling elements (76, 176, 276).

3. 2. The bearing (25, 102, 45) according to claim 1, wherein the angular section (99, 199, 299, 300) has a vertex angle (α1, α2, α3, α4) that is equal to or greater than the vertex angle (β9) of the angular section occupied by nine rolling elements (76, 176, 276).

4. 2. The bearing (25, 102, 45) of claim 1, wherein the angular section (99, 199, 299, 300) has vertex angles (α1, α2, α3, α4) that are equal to or greater than the vertex angle (β13) of the angular section occupied by thirteen rolling elements (76, 176, 276).

5. 2. The bearing (25, 102, 45) according to claim 1, characterized in that the vertex angles (α1, α2, α3, α4) of the angular sections (99, 199, 299, 300) of the inner ring (72, 172, 272) are greater than or equal to 20°.

6. 2. The bearing (25, 102, 45) according to claim 1, characterized in that the vertex angles (α1, α2, α3, α4) of the angular sections (99, 199, 299, 300) of the inner ring (72, 172, 272) are greater than or equal to 70°.

7. 2. The bearing (25, 102, 45) according to claim 1, characterized in that the vertex angles (α1, α2, α3, α4) of the angular sections (99, 199, 299, 300) of the inner ring (72, 172, 272) are equal to or greater than 120°.

8. 2. The bearing (25, 102, 45) according to claim 1, characterized in that the radial widths (L94, L194, L294, L295) are constant along an arc of a circle centered on the main axis (A72, A172, A44) of the inner ring (72, 172, 272).

9. A bearing (25) according to claim 8, characterized in that said radial width (L94) is substantially equal to said radial width (L90) of said slot (90).

10. 10. The bearing (25) according to claim 9, characterized in that the radial width (L94) of the material bridge (94) is less than or equal to 30% of the radius (R80) of the outer peripheral path (80) of the inner ring (72).

11. 2. A bearing (25, 45) according to claim 1, characterized in that the slot (90, 290, 292) extends between two rounded ends (100) of a diameter equal to the width (L90, L290, L291) of the slot.

12. 2. The bearing (24, 102, 45) of claim 1, wherein the rolling elements (76, 176, 276) are rollers.

13. 2. The bearing (25, 102, 45) of claim 1, wherein the rolling elements (76, 176, 276) are balls.

14. 2. The bearing (45) of claim 1, wherein the inner ring (272) is provided with a plurality of slots (290, 291).

15. 15. A bearing (45) according to claim 14, characterized in that the inner ring (272) comprises two slots (290, 291), said two slots (290, 291) being radially opposed relative to the main axis (A44).

16. 2. The bearing (102) of claim 1, wherein the inner ring (172) comprises a slot (190) and two fixing holes (188).

17. An output lever (8) with a cam mechanism follower roller, said output lever being provided with two rollers (23, 24), At least one of the two rollers comprises a bearing (25, 102) according to claim 1, the inner ring (72, 172) of the bearing is fixed to one or both of the web (20) of the output lever and a flange (22) attached to the output lever by a fixing element (36); An output lever (8) characterized in that the outer ring (74, 174) of the bearing has a peripheral rolling track (86) with a circular outer shape.

18. A cam-type shed forming machine (2) comprising an output lever (8) according to claim 17.

19. A shed former (2) according to claim 18, The shed former (2) is characterized in that the output lever (8) oscillates between a high position and a low position around the main axis (A9) of the cam machine according to the contour (16, 18) of the cam (6) of the shed former (2) in which one of the two rollers (23, 24) acts in contact with the outer peripheral rolling track (86), and the contact occurs within a loading area radially aligned with the angular section (99, 199) of the inner ring (72, 172) in which the slot (90, 190) is formed.

20. A cam-type or dobby-type shed-forming machine (2), comprising a mechanical transmission system (38) to a loom, the mechanical transmission system (38) comprising a plurality of articulated mechanisms having mutually parallel axes (A62, A64, A70), A cam machine or dobby type shed former (2), characterized in that one of the articulation mechanisms comprises a bearing (45) according to claim 1.

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