FR2853370A1 - BEARING PROVIDED WITH AN ELASTOMER INSERT AND AGRICULTURAL MACHINE COMPRISING SUCH A BEARING - Google Patents

Abstract

The present invention provides a bearing (101) comprising an outer ring (3) and an inner ring (104) respectively provided with raceways (6, 7), and several rolling bodies (5) arranged between said outer ring (3). and said inner ring (104) so as to roll in said raceways (6, 7). This bearing (101) is characterized in that said inner ring (104) is provided with at least one groove (108) opening out at least on one side (9) of said bearing (101), said groove (108) being intended to receive an elastomer insert (110). The bearing according to the present invention thus advantageously integrates a sealing function. It also makes it possible to reduce or even eliminate the transmission of vibrations. The present invention also relates to an agricultural machine, in particular a disc mower, comprising such a bearing (101).

Description

Description

  The present invention relates to a bearing of the type comprising an outer ring and an inner ring respectively provided with raceways, and rolling bodies disposed between said outer ring and said inner ring so as to roll in said raceways.

  Such a bearing finds its application in a very large number of fields, and in particular in agricultural machinery.

  Thus by way of example, document EP O 240 084 describes a disc mower provided with such bearings for guiding the rotation of the intermediate wheels. This known agricultural machine comprises discs pivotally linked to a casing and driven in rotation about a respective axis directed upwards. The discs are also linked to a respective toothed wheel arranged inside the casing. Each toothed wheel meshes with at least one intermediate wheel also disposed inside the casing. The toothed wheels and the intermediate wheels 1 5 thus constitute a gear train intended to transmit to each disc a rotational movement coming from a driving source.

  Each intermediate wheel is pivotally linked to the casing by means of a bearing comprising an outer ring, an inner ring and rolling bodies. The outer ring and the inner ring are respectively provided with a raceway. For their part, the rolling bodies are arranged between the outer ring and the inner ring so as to roll in the raceways. The outer ring of the bearing is linked to the intermediate wheel. The inner ring is mounted on a shaft passing through the walls of the housing. The shaft has a shoulder allowing it to rest on one of the walls of the casing. In this known casing each tree is associated with a bowl by means of a screw. The bowl is supported on the other wall of the housing. The screw allows the shaft and the bowl to be brought together so as to press them against their respective walls.

  As a general rule, the interior of such a casing is partially filled with oil 30 in order to lubricate the undercarriage. One of the difficulties encountered with this type of mechanism consists in guaranteeing the tightness of the casing. This is all the more important in agricultural machinery where any leak of lubricant directly pollutes the soil and / or crops.

  In this prior document, the seal at the intermediate wheels is achieved by means of a first O-ring disposed between the shoulder of the shaft and the corresponding wall of the casing and of a second O-ring disposed between the cup. and the respective wall of the housing. There is also a third O-ring provided between the shaft and the bowl.

  Another difficulty encountered in the design of machines in general consists in reducing the noise emitted by these machines. In example 10, in particular of disc mowers, each engagement between the toothed wheels and the intermediate wheels generates vibrations. These vibrations are transmitted in particular to the casing which then plays the role of a sounding board.

  Considering the number of meshing which one can have with a mower comprising up to ten discs at present, the noise level reached by such machines 15 is very important.

  The explanation of the problems encountered was illustrated by taking the example of a disc mower. It goes without saying that such problems can appear on other agricultural machines and also in other sectors of activity where machines or vehicles are designed.

  One of the aims of the present invention is to propose a simpler and less expensive solution for obtaining the tightness of a casing.

  Another object of the present invention is to reduce the noise level generated by the machines during their operation.

  To this end, the bearing according to the present invention is characterized in that the inner ring has at least one groove opening out at least on one side of the bearing, said groove being intended to receive an elastomer insert.

  Thus, during the mounting of the bearing, the insert is intended to come into contact with a neighboring construction element, such as the wall of a housing for example, so as to provide a seal between the bearing and this construction element .

  In addition, the insert also makes it possible to avoid any direct contact between the bearing and the neighboring building element. The material constituting the insert advantageously makes it possible to dampen or even eliminate the transmission of vibrations between the bearing and the neighboring building element. This gives a very marked reduction in the noise level produced by the machine during its operation.

  Preferably, the groove intended to receive the insert opens out 5 on an internal face of the bearing in addition to open out on the side. Therefore during the mounting of the bearing, the deformation of the insert advantageously avoids any direct contact between the inner ring and the shaft which supports it. The bearing is therefore completely isolated from the construction elements which surround it.

  Consequently, the reduction in noise level is further improved.

  The present invention also relates to an agricultural machine comprising such a bearing.

  Other characteristics of the invention, to be considered separately or in all their possible combinations, will appear further in the following description of nonlimiting exemplary embodiments of the invention shown in the accompanying drawings in which: - Figure 1 shows a bearing according to the present invention seen in partial section along its axis of rotation, said bearing being provided with an insert, - Figure 2 shows the bearing of Figure 1 before the insertion of the insert, - the FIG. 3 represents a view in partial section of the insert of FIG. 1 before it is put in place on the bearing, - FIG. 4 represents, seen in partial section, an example of mounting the bearing of FIG. 1, - FIG. 5 shows a second bearing according to the present invention seen in partial section along its axis of rotation, this other bearing being provided with two inserts, - Figure 6 shows the bearing of Figure 5 o only one of the two inserts is put in place, - Figure 7 shows a partial sectional view of the insert in Figure 5 before it is put in place, - Figure 8 shows, seen from above, an agricultural machine using bearings according to the invention, - Figure 9 shows, seen from above and on another scale, part of the cutting device of the agricultural machine of Figure 8, - Figure 10 shows, seen in section along the arrow X in Figure 9 and on another scale, the cutting device of Figure 9, - Figure 11 shows a third bearing according to the present invention seen in partial section along its axis of rotation, - Figure 12 shows a partial section view of the insert in FIG. 11 10 before it is put in place.

  Figure 1 shows a first example of a bearing (1) according to the present invention seen in partial section along a plane passing through its axis of rotation (2). In a manner known to those skilled in the art, said bearing (1) comprises an outer ring (3), an inner ring (4), and rolling bodies 15 (5). Said outer ring (3) is provided with a raceway (6). Said inner ring (4), also provided with a raceway (7), is coaxial with said outer ring (3). For their part, said rolling bodies (5) are arranged between said outer ring (3) and said inner ring (4) so as to roll in said raceways (6, 7). In a manner also known, said bearing (1) may additionally comprise a cage, not shown, intended to maintain a homogeneous angular distribution of said rolling bodies (5) around said axis of rotation (2).

  In the exemplary embodiments shown in the figures, said rolling bodies (5) are spherical and they are arranged in a single row. Furthermore, the contact of said rolling bodies (5) on said rings (3, 4) takes place radially with respect to said axis of rotation (2). However, it goes without saying that the present invention also relates to bearings (1) whose said rolling bodies (5) have a cylindrical or conical shape. Similarly, said rolling bodies (5) can be arranged in more than one row. In addition, the contact of said rolling bodies 30 (5) on said rings (3, 4) can also take place obliquely with respect to said axis of rotation (2).

  However, according to an important characteristic of the present invention, the inner ring (4) of said bearing (1) advantageously comprises at least one groove (8) opening at least on one side (9) of said bearing (1), said groove (8) being intended to receive an elastomer insert (10).

  In the embodiment shown in Figures 1 and 2, said inner ring (4) has a single groove (8). In addition the latter opens only on the side (9) of said bearing (1).

  In order to describe the present invention more precisely, FIG. 2 represents said bearing (1) before the insertion of said insert (10). For its part, FIG. 10 3 represents this time said insert (10) before it is placed on said bearing (1). Figures 2 and 3 are shown in the same view as for Figure 1.

  In the light of Figures 1 and 2, said groove (8) is advantageously circular and concentric with said inner ring (4). Said groove (8) is thus defined by an inside diameter (11), an outside diameter (12), and a depth (13). Said depth (13) is measured from the side (9) of said inner ring (4). Referring now to Figure 3, said insert (10) is for its part defined by an inner diameter (14), an outer diameter (15) and a thickness (1 6).

  Advantageously, the inside diameter (14) of said insert (10) before it is placed on said bearing (1) is slightly less than the inside diameter (11) of said groove (8). The establishment of said insert (10) in said groove (8) thus generates a slight deformation of said insert (10). This deformation remains compatible with the elasticity of the material constituting said insert (10). Once in place, this deformation induces a tightening of said insert (10) on the wall of the internal diameter (11) of said groove (8). This tightening advantageously makes it possible to maintain said insert (10) in said groove (8) during the subsequent manipulations of said bearing (1). Therefore, the operation of placing said insert (10) in said groove (8) can be performed well before said bearing (1) is mounted in a machine. In addition, the operation of mounting said bearing (1) in the machine is greatly facilitated.

  Preferably, said insert (10) is provided with a chamfer (17) intended to facilitate the positioning of said insert (10) in said groove (8). In fact, during the installation of said insert (10), it is the oblique face of said chamfer (17) which comes into contact with the flank (9) of said bearing (1) and not a radial face 5 of said insert (10 ). The slope of said chamfer (17) generates a progressive deformation of said insert (10) when the latter is pushed into said groove (8).

  In the light more particularly of FIG. 1, it can be noted that the thickness (16) of said insert (10) is advantageously greater than the depth (13) of said groove (8). Furthermore, once put in place, the outside diameter (15) 10 of said insert (10) remains smaller than the outside diameter (12) of said groove (8).

  Thus when said insert (10) is placed on said bearing (1), part of said insert (10) protrudes somewhat from the side (9) of said bearing (1) so as to create a reserve of material. For its part, the free space between the outside diameter (12) of said groove (8) and the outside diameter (15) of said insert (10) 15 advantageously allows said reserve of material to deform during assembly of said bearing ( 1). This deformation of said insert (10) is visible in particular in FIG. 4 which schematically represents a very general example of mounting of said bearing (1) in accordance with the present invention.

  Thus, with reference to FIG. 4, said bearing (1) is mounted on a shaft 20 (18). Said shaft (18) of diameter (19) therefore passes through said inner ring (4) whose diameter (20) is identified in FIG. 1. The diameter (19) of said shaft (18) is substantially equal to the diameter ( 20) of said inner ring (4). However, in a manner known to those skilled in the art, the diameter (19) of said shaft (18) can voluntarily be chosen slightly larger or slightly smaller than the diameter (20) of said inner ring (4) . This difference between said diameters (19, 20) makes it possible to produce a more or less tight connection between said shaft (18) and said inner ring (4). The order of magnitude of such a difference in diameters is a few hundredths of a millimeter. This is therefore incommensurate with the difference in diameters existing in the mounting example shown in Figure 10 where we are actually trying to create a space between a shaft (42) and an inner ring (104) of a bearing (101).

  In the general mounting example, said bearing (1) also bears against a neighboring construction element (21) symbolically represented in FIG. 4 by a ring. It goes without saying that any type of stop can constitute said construction element (21). Thus, in a non-exhaustive manner, said building element (21) can be constituted by a shoulder of said shaft (18), by another bearing, by a toothed wheel, by a wall of a casing, etc. When mounting said bearing (1) on said shaft (18), said construction element (21) comes into contact with said insert (10) and deforms the latter somewhat while remaining within the acceptable limits for the material constituting said insert (10). There is thus obtained a perfect seal between said construction element (21) and the inner ring (4) of said bearing (1).

  In the light of FIG. 4 and in a particularly advantageous manner, the dimensions of said groove (8) and of said insert (10) are determined so that, during the mounting of said bearing (1), all that remains is even a space between said building element (21) and said sidewall (9). By thus avoiding any direct contact between said construction element (21) and said inner ring (4), the transmission of vibrations between the latter is very greatly reduced. Indeed, the elasticity of the material constituting said insert (10) makes it possible to dampen the vibrations transmitted directly between said construction element 20 (21) and said inner ring (4).

  For the sake of clarity in FIG. 4, no construction element bearing on the outer ring (3) of said bearing (1) has been shown. It goes without saying that in reality and in particular in the light of FIG. 10, such a construction element is actually present. Similarly, the construction elements 25 making it possible to press said bearing (1) against said construction element (21) and to maintain said bearing (1) in this position have not been shown because they are within the reach of the skilled in the art.

  Figure 5 shows a second embodiment of a bearing according to the present invention. This bearing (101) comprises a certain number of elements which have been described previously. These elements will therefore keep the same reference number and will not be described again. It also includes a certain number of elements which are comparable to elements of said bearing (1) described above. These elements will be assigned the same reference number as these comparable elements of said bearing (1) but increased by 100. They will only be described if necessary.

  Thus, FIG. 5 represents a second bearing (101) in accordance with the present invention seen in partial section along a plane passing through its axis of rotation (2). Said bearing (101) also comprises an outer ring (3), an inner ring (104), and rolling bodies (5). In this second embodiment, said inner ring (104) now comprises two grooves (108) each opening at least on a respective flank (9) of said bearing 10 (101). Said grooves (108) are each intended to receive an elastomer insert (110).

  FIG. 6 represents, in the same view as for FIG. 5, said bearing (101) of which only one of said inserts (110) is put in place. For its part, FIG. 7 represents on the other hand one of said inserts (110) before it is placed on said bearing (101).

  Preferably, the two grooves (108) and the two inserts (110) of the same bearing (101) are identical. Therefore, the part of the description below concerning the second embodiment also applies to said groove (108) and to said insert (110) shown on the left in FIGS. 5 and 6.

  In the embodiment shown in Figures 5 and 6, said groove (108) also opens onto an internal face (20a) of said bearing (101) in addition to opening onto a respective flank (9). Said internal face (20a) designates the side of said inner ring (104) oriented towards said axis of rotation (2). Said internal face (20a) thus materializes the diameter (20) of said inner ring (104).

  Said groove (108) is in this case defined by an outside diameter (112) and a depth (113). Preferably, said groove (108) comprises a face (108a) substantially perpendicular to said axis of rotation (2) and opening onto said internal face (20a), and a face (108c) substantially parallel to said axis of rotation ( 2) and opening onto said side (9). In light of FIG. 6, the junction between said face (108a) and said face (108c) is produced by means of a slope (108b). By way of nonlimiting example, said slope (108b) draws an angle between 30 and 60 degrees with said axis of rotation (2). Preferably, said angle is 45 degrees.

  Referring now to FIG. 7, said insert (110) is for its part defined by an inside diameter (114), an outside diameter (115) and a thickness 5 (116). In addition, the outer periphery of said insert (110) this time comprises a face (1 lOa) substantially perpendicular to an axis of symmetry (57) of said insert (110), and a face (1 lOc) substantially parallel to said axis of symmetry (57 ). The junction between said face (11 Oa) and said face (11 Oc) is carried out by means of a slope (1 10 Ob). Preferably, said slope (110b) draws with said axis of symmetry (57) the same angle as the angle drawn by said slope (108b) with said axis of rotation (2).

  Advantageously, the outside diameter (115) of said insert (110) before positioning is slightly greater than said outside diameter (112) of said groove (108). The establishment of said insert (110) in said groove (108) 15 thus generates a slight deformation of said insert (110), deformation compatible with the elasticity of the material constituting said insert (110). Once in place, this deformation induces a pressure of the wall (11 Oc) of said insert (110) against the wall (108c) of said groove (108). This pressure advantageously makes it possible to maintain said insert (110) in said groove (108) during the subsequent manipulations of said bearing (101). Advantageously, said slope (110b) facilitates the positioning of said insert (110) in said groove (108) in the same way as said chamfer (17) of the first embodiment.

  In the light of FIGS. 5 and 6, it can be noted that the thickness (116) of said insert (110) is advantageously greater than the depth (113) of said groove 25 (108). Thus when said insert (110) is placed on said bearing (101), part of said insert (110) protrudes somewhat from the corresponding flank (9) of said bearing (101) so as to create a reserve of material. In addition, once put in place, the inside diameter (114) of said insert (110) remains greater than the diameter (20) of said inner ring (104). Therefore during the mounting of said bearing 30 (101) on a shaft, it avoids any risk of damage or tearing of said insert (110).

  The various advantages provided by said bearing (101) will appear even more clearly in the light of the example of use shown in FIGS. 8 to 10.

  Indeed, Figure 8 shows, in top view, an agricultural machine 5 according to the present invention and more specifically a mower (22). Said mower (22) is coupled to a motor vehicle (23) which pulls it in a direction and a direction of advance indicated by the arrow (24). In the following description, the following concepts "front" and "rear", "front" and "behind" are defined relative to the direction of advance (24) and the concepts "right" and "left" are defined looking at said mower (22) from the rear in the direction of advance (24).

  In a manner known to those skilled in the art, said mower (22) comprises a cutting device (25) intended to cut a standing product such as grass for example. Said mower (22) also comprises a chassis (26) making it possible to link said cutting device (25) to said motor vehicle (23).

  In the embodiment shown in Figure 8, said agricultural mower (22) is of the rear mounted type. Thus one end of said chassis (26) is intended to be coupled to a three-point linkage (27) disposed at the rear of said motor vehicle (23). The other end of said frame (26) is however linked to said cutting device (25) by means of a hinge. Said frame (26) advantageously allows said cutting device (25) to pass from a substantially horizontal working position, as shown in FIG. 8, to a transport position, not shown, and vice versa. Preferably, said chassis (26) comprises a suspension device (28) intended during work to transfer at least part of the weight of said cutting device 25 (25) on said motor vehicle (23). Advantageously, said suspension device (28) also allows said cutting device (25) to follow the irregularities of the ground independently of the position of said motor vehicle (23). Such a frame (26) of a mower (22) is well known to those skilled in the art, it will therefore not be described further.

  For its part said cutting device (25) comprises a casing (29), at least one cutting member (30), and at least one guide bearing (31) intended to pivotally link said cutting member (30) audit housing (29). During work, it said casing (29) rests at least partially on the ground, transverse to said direction of advance (24). Said cutting member (30) is arranged above said casing (29). In addition, said cutting member (30) is driven in a direction of rotation (32) about an axis (33) directed upwards. In the embodiment 5 shown in FIGS. 8 to 10, said cutting device (25) more precisely comprises six cutting members (30) linked to said casing (29) by means of a respective guide bearing (31) . Each cutting member (30) is rotated about a respective axis (33) and in a respective direction (32).

  Preferably, said cutting members (30) are aligned on a straight line and arranged in the same extension plane.

  In a manner known to those skilled in the art, this rotational movement of said cutting member (30) allows at high speed, about 3000 revolutions per minute, the latter to cut said product standing.

  Indeed, in the light more precisely of FIGS. 8 and 9, said cutting member (30) advantageously comprises a support (34) and two cutting elements (35). Said support (34) extends in a plane substantially perpendicular to said axis of rotation (33). Said cutting elements (35) are linked to the periphery of said support (34), on either side of said axis of rotation (33). Preferably, said support (34) has an oval shape and said cutting elements (35) are advantageously arranged at the ends of a large diameter of said oval shape. As said cutting member (30) is rotated during work, said cutting elements (35) therefore describe circles (36) around said axis of rotation (33). The high speed of movement thus attained by said cutting elements (35) allows the latter to impact cut said product on foot.

  Referring to Figure 8, the drive of said cutting members (30) is carried out from the PTO of said motor vehicle (23). To do this, said mower (22) comprises in particular a telescopic transmission shaft with universal joints (37), a pulley-belt system (38) and a return casing 30 (39).

  In the light of FIG. 9, the rotational movement arriving at said gearbox (39) is then distributed to the various cutting members (30) using a gear train. In a manner known to those skilled in the art, said gear train is constituted by intermediate wheels (40) and toothed wheels (41) arranged inside said casing (29). The gear train being lubricated with oil, said casing (29) must therefore be sealed. Each toothed wheel (41) is linked to a respective cutting member (30) so as to drive it in rotation. For its part, each intermediate wheel (40) is mounted to rotate freely by means of a bearing according to the present invention. This connection of said intermediate wheel (40) is visible more precisely in FIG. 10.

  Note however that the various elements of Figure 9 have been shown in transparency so as to clearly show all the details of the interior of said housing (29). Note also that to avoid overloading Figure 9, a cutting member (30) only has been shown. However, said guide bearing (31) corresponding to this cutting member (30) has not been drawn.

  Referring now to FIG. 10, said intermediate wheel (40) is more precisely linked to the outer ring (3) of said bearing (101). For its part, said inner ring (104) is linked to said casing (29) by means of a shaft (42). Said intermediate wheel (40) can thus rotate freely around the axis of rotation (2) of said bearing (101) so as to transmit the rotational movement to the other wheels of said gear train. For the sake of clarity in FIG. 10, no connecting element between said outer ring (3) and said intermediate wheel (40) has been shown.

  In the mounting example shown in FIG. 10, said shaft (42) is advantageously linked in a removable manner to said casing (29) which in particular makes it possible to facilitate the mounting and dismounting operations of said intermediate wheel (40) provided with its bearing (101). To do this, a hole (47) is in particular provided in one of the walls (43) of said casing (29). Thus during the assembly of said casing (29), said bearing (101) provided with said inserts (110) and said intermediate wheel (40) is slid inside said casing (29) so that said ring interior (104) or coaxial with said hole (47). Then said shaft (42) is successively engaged in said hole (47) and in said inner ring (104). Preferably, there is additionally provided a hole (48) in the other wall (44) of said housing (29), said hole (48) of said wall (44) being coaxial with said hole (47) of said wall (43). In the embodiment shown in Figure 10, said shaft (42) also passes through this other hole (48). The forces coming from said intermediate wheel (40) are thus better distributed towards the two walls (43, 44) of said casing (29).

  Advantageously, said shaft (42) has a shoulder (49) intended to come into abutment against the external face of said wall (43) during the assembly of said casing (29). Said shoulder (49) thus makes it possible to define the axial position of said shaft (42) relative to said casing (29). Maintaining said shaft (42) in this defined position is ensured by means of a screw (45) and a bowl (46). To this end, said shaft (42) further includes a hole (50) allowing the passage of a threaded portion of said screw (45). The head of said screw (45) bears on it on said shaft (42). The threaded part of said screw (45) is then caught in a threaded hole (52) provided in said bowl (46). For its part, said bowl (46) is threaded through said hole (48). In addition, said bowl (46) has a shoulder (51) intended to bear against the outside face of said wall (44). Thus when tightening said screw (45), said shaft (42) is held fixed relative to said housing (29).

  In addition, the tightening of said screw (45) also causes the two walls (43, 44) to come closer to said casing (29). In fact, the distance separating said two walls (43, 44) is initially greater than the width of said bearing (101) measured at the level of said inserts (110). This in particular facilitates the introduction and sliding of said bearing (101) in said casing (29) during assembly. With this approximation, said walls (43, 44) come into contact with a respective insert (110) of said bearing (101) and slightly deform the latter. In the same way as for the mounting example shown in FIG. 4, a perfect seal is thus obtained between said walls (43, 44) of said casing (29) and the inner ring (4) of said bearing (101). Any leakage of lubricant through said holes (47, 48) is therefore avoided.

  In the embodiment shown in FIG. 10, the walls (43, 44) of said casing (29) are brought closer to one another until said shaft (42) comes to bear against said bowl ( 46). In a particularly advantageous manner, the dimensions of said grooves (108), said inserts (110) and said shaft (42) are determined so that there remains all the same when mounting a space between said walls (43, 44 ) of said casing (29) and said flanks (9) of said bearing (101). This avoids any direct contact between said housing 5 (29) and said bearing (101). Thus, in the same way as for the mounting example shown in FIG. 4, the direct transmission to said casing (29) of vibrations from said gear train is greatly reduced.

  Also advantageously, the diameter of the part of said shaft (42) on which said bearing (101) is mounted is slightly less than the diameter (20) of said inner ring (104). The order of magnitude of this difference in diameters is in tenths of a millimeter, or even in millimeters.

  Even if this difference in diameter remains small, it is still much larger than the differences in diameter encountered in the mounting example shown in FIG. 4.

  Referring to Figure 10, the shape of said grooves (108) and said inserts (110) is determined so that the deformation of said inserts (110) when tightening said screw (45) is partly oriented towards the 'axis (2) of said bearing (101). As a result, during assembly, a reduction in the internal diameter (114) of said insert (110) is obtained, which allows said inner ring (104) to be centered relative to said shaft (42). This avoids any direct contact between said shaft (42) and said bearing (101). It follows in this case that said bearing (101) is completely isolated from the construction elements which surround it.

  Any direct or indirect transmission of vibrations between said bearing (101) and said casing (29) is therefore very greatly reduced or even eliminated. This results in a significant reduction in the operating noise of said mower (22).

  It emerges from the description concerning FIGS. 5 to 7 and 10 that said slopes (108b; 11Ob) play an important role in the directed deformation of said insert (110) towards the axis of rotation (2) of said bearing (101). However, there are other forms of groove and insert which make it possible to obtain this advantage of directed deformation.

  Indeed, Figure 11 shows, in the same view as for Figures 2 and 6, a third embodiment of a bearing according to the present invention. This bearing (201) comprises a certain number of elements which have been described previously. These elements will therefore keep the same reference number and will not be described again. It also includes a certain number of elements which are comparable to elements of said bearing (1) 5 described above. These elements will be assigned the same reference number as these comparable elements of said bearing (1) but increased by 200. They will only be described if necessary.

  In this third exemplary embodiment, said groove (208) is this time defined by an outside diameter (212), an intermediate diameter (53), a depth (213), and an intermediate depth (54). Furthermore, said groove (208) comprises a face (208a) substantially perpendicular to said axis of rotation (2) and opening onto said internal face (20a) of said bearing (201), and a face (208c) substantially parallel to said axis of rotation ( 2) and opening onto said side (9). In the light of FIG. 11, the junction between said face (208a) and said face (208c) is produced by means of a face (208d) substantially parallel to said face (208c) and of a face (208e) substantially parallel to said face (208a).

  Said faces (208d, 208e) of this third embodiment example have therefore replaced said slope (108b) of the second embodiment example.

  Referring to Figure 12, said insert (210) is defined by an inner diameter (214), an intermediate diameter (55), an outer diameter (215), a thickness (216), and a thickness intermediate (56). The outer periphery of said insert (210) has four faces (21 Oa, 21 Oc, 21 Od, 210e). Said face (210a) is substantially perpendicular to the axis of symmetry (57) of said insert (210) and said face (210c) is substantially parallel to said axis of symmetry (57). The slope (1 Ob) of said insert (110) according to the second exemplary embodiment is replaced by said faces (210d, 210e) of the insert (210) according to the third exemplary embodiment. Preferably, said face (210d) is substantially parallel to said face (210c) and said face (210e) is substantially parallel to said face (21 Oa).

  Advantageously, the outside diameter (215) of said insert (210) before being placed on said bearing (201) is slightly greater than said outside diameter (212) of said groove (208). The establishment of said insert (210) in said groove (208) thus generates a slight deformation of said insert (210), deformation compatible with the elasticity of the material constituting the latter. Once in place, this deformation induces a pressure on the wall (210c) of said insert (210) against the wall (208c) of said groove (208). This pressure advantageously makes it possible to maintain said insert (210) in said groove (208) during the subsequent manipulations of said bearing (201).

  In light of FIG. 11, it can also be noted that said intermediate thickness (56) is greater than said intermediate depth (54). Thus when said insert (210) is placed on said bearing (201), said face 10 (210e) advantageously comes into contact with said face (208e) and part of said insert (210) protrudes somewhat from the sidewall (9). said bearing (201) so as to create a reserve of material. In addition, once put in place, the internal diameter (214) of said insert (210) remains greater than the diameter (20) of said internal ring (204). Therefore during the mounting of said bearing (201) on a shaft, any risk of damage or tearing of said insert (210) is avoided. The presence and the dimensions of said faces (208a, 208c, 208d, 208e; 210a, 210c, 210d, 210e) advantageously make it possible to direct the deformation of said insert (210) towards the axis of rotation (2) of said bearing (201) during of the assembly of the latter.

  The bearings (1; 101; 201) and the agricultural machine (22) which have just been described are only examples which cannot in any way limit the field of protection defined by the following claims.

  Thus said inserts (10; 110; 210) can also be made of thermoplastic or any other material having a good elasticity characteristic to guarantee sealing and / or a good damping capacity 25 in order to reduce or even eliminate the vibration transmission.

Claims (28)

claims   1. Bearing comprising an outer ring (3) and an inner ring (4; 104; 204) provided respectively with raceways (6, 7), and several rolling bodies (5) arranged between said outer ring (3) and 5 said inner ring (4; 104; 204) so as to roll in said raceways (6, 7), characterized in that said inner ring (4; 104; 204) is provided with at least one groove (8 ; 108; 208) opening at least on one side (9) of said bearing (1; 101; 201), said groove (8; 108; 208) being intended to receive an elastomer insert (10; 10 110; 210).   2. Bearing according to claim 1, characterized in that said inner ring (4; 104; 204) has two grooves (8; 108; 208) each opening at least on a respective flank (9) of said bearing (1; 101 ; 201), said grooves (8; 108; 208) being each intended to receive an insert (10; 110; 210) of elastomer.   3. Bearing according to claim 1 or 2, characterized in that said groove (8) is defined by an inside diameter (11), an outside diameter (12), and a depth (13), and by the fact that said insert (10) is defined by an inside diameter (14), an outside diameter (15) and a thickness (16).   4. Bearing according to claim 3, characterized in that before the insertion of said insert (10) on said bearing (1), the internal diameter (14) of said insert (10) is slightly less than an internal diameter (11) of said groove (8).   5. Bearing according to claim 3 or 4, characterized in that said insert (10) is provided with a chamfer (17) intended to facilitate the positioning of said insert (10) in said groove (8).   6. Bearing according to any one of claims 3 to 5, characterized in that the thickness (16) of said insert (10) is advantageously greater than the depth (13) of said groove (8).   7. Bearing according to any one of claims 3 to 6, characterized in that once put in place, the outside diameter (15) of said insert (10) remains smaller than the outside diameter (12) of said groove (8 ).   8. Bearing according to claim 1 or 2, characterized in that at least one of said grooves (108; 208) also opens onto an internal face (20a) of said bearing (101; 201).   9. A bearing according to claim 8, characterized in that said groove (108) is defined by an outside diameter (112) and a depth (113), and by the fact that said insert (110) is defined by a diameter inside (114), an outside diameter (115) and a thickness (116).   10. Bearing according to claim 9, characterized in that said groove comprises: - a face (108a) substantially perpendicular to an axis of rotation (2) of said bearing (201) and opening onto said internal face (20a), and - a face (108c) substantially parallel to said axis of rotation (2) and opening onto said flank (9), the junction between said face (108a) and said face (108c) being produced by means of a slope (108b).   11. Bearing according to claim 9, characterized in that said slope (108b) draws an angle between 30 and 60 degrees with said axis of rotation (2), said angle preferably being equal to 45 degrees. 30 12. A bearing according to any one of claims 9 to 11, characterized in that the outer periphery of said insert (10) comprises: - a face (l 10a) substantially perpendicular to an axis of symmetry (57) of said insert (110) , and - a face (110c) substantially parallel to said axis of symmetry (57), the junction between said face (110A) and said face (110c) being produced by means of a slope (11 Ob).   13. A bearing according to claims 11 and 12, characterized in that said slope (11 Ob) draws with said axis of symmetry (57) the same angle as the angle drawn by said slope (108b) with said axis of rotation ( 2). 10 14. Bearing according to any one of claims 9 to 13, characterized in that before the installation of said insert (110) on said bearing (101), the outside diameter (115) of said insert (110) is slightly greater than the outside diameter (112) of said groove (108). 15. A bearing according to any one of claims 9 to 14, characterized in that the thickness (116) of said insert (110) is greater than the depth (113) of said groove (108).   16. Bearing according to any one of claims 9 to 15, characterized in that when said insert (110) is placed on said bearing (101), the internal diameter (114) of said insert (110) remains greater than diameter (20) of said inner ring (104).   17. A bearing according to claim 8, characterized in that said groove (208) is defined by an outside diameter (212), an intermediate diameter (53), a depth (213), and an intermediate depth (54), and by the fact that said insert (210) is defined by an inside diameter (214), an intermediate diameter (55), an outside diameter (215), a thickness 30 (216), and an intermediate thickness (56).   18. A bearing according to claim 17, characterized in that said groove (208) comprises: - a face (208a) substantially perpendicular to said axis of rotation (2) and opening onto said internal face (20a) of said bearing (201), and - a face (208c) substantially parallel to said axis of rotation (2) and opening onto said flank (9), the junction between said face (208a) and said face (208c) is carried out by means of: - a face ( 208d) substantially parallel to said face (208c), and - from a face (208e) substantially parallel to said face (208a).   19. Bearing according to claim 17 or 18, characterized by. the fact that the outer periphery of said insert (210) comprises: - a face (210a) substantially perpendicular to an axis of symmetry (57) 15 of said insert (210), and - a face (210 Oc) substantially parallel to said axis of symmetry (57), the junction between said face (210a) and said face (210c) being produced by means of: - a face (210d) substantially parallel to said face (210c), and 20 - a face (210e) is substantially parallel to said face (210a).   20. Bearing according to any one of claims 17 to 19, characterized in that before the installation of said insert (210) on said bearing (201), the outside diameter (215) of said insert (210) is slightly greater than the outside diameter (212) of said groove (208).   21. Bearing according to any one of claims 17 to 20, characterized in that said intermediate thickness (56) is greater than said intermediate depth (54).   22. Bearing according to any one of claims 17 to 21, characterized in that when said insert (210) is placed on said bearing (201), the internal diameter (214) of said insert (210) remains greater than diameter (20) of said inner ring (204).   23. Agricultural machine, characterized in that it comprises at least one bearing (11; 101; 201) according to any one of claims 1 to 22.   24. Agricultural machine according to claim 23, characterized in that it is an agricultural mower (22) comprising: - a cutting device (25) intended to cut a standing product, and - a frame ( 26) intended to link said cutting device (25) to a motor vehicle (23), said cutting device (25) in turn comprises a casing (29) and at least one cutting member (30) driven in rotation around an axis (33) directed upwards, the drive of said cutting member (30) is carried out using in particular an intermediate wheel (40) which is connected to said casing (29) by means of said bearing (1; 101; 201).   25. Agricultural mower according to claim 24, characterized in that said intermediate wheel (40) is linked to the outer ring (3) of said bearing (1; 101; 201) and said inner ring (4; 104; 204) is linked to said casing (29) by means of a shaft (42) passing through at least one wall (43) of said casing (29).   26. Agricultural mower according to claim 25, characterized in that 25 during the mounting of said cutting device (25), said intermediate wheel (40) with said bearing (1; 101; 201) provided with said at least one insert (10 ; 110; 210) are slid inside said casing (29) between said wall (43) and another wall (44) of said casing (29).   27. Agricultural mower according to claim 26, characterized in that the axial maintenance of said shaft (42) relative to said casing (29) is ensured by means of a screw (45) and a bowl (46), and by the fact that the tightening of said screw (45) brings about said walls (43, 44) by means of which at least one of said walls (43, 44) comes into contact with said corresponding insert (10; 110; 210) so as to somewhat distort the latter.   28. Agricultural mower according to claim 27, characterized in that the diameter of the part of said shaft (42) on which said bearing (1; 101; 201) is mounted is slightly less than the diameter (20) of said inner ring (4 ; 104; 204), the difference between said diameters being greater than one tenth of a millimeter.