Support assembly

Abstract

A support assembly (20; 41) comprising at least: a bearing (20) including at least one flange portion (30) having at least one retaining portion (31) and a cavity lined with an elastomeric coating (60), the cavity being configured to at least partially receive a suspended element, and a stirrup (41) adapted to cover the bearing (20); the support assembly (20; 41) being characterized in that the elastomeric coating (60) has a variable radial hardness so as to exhibit variable torsional and radial stiffness. Figure for the abbreviation: Fig. 5

Description

Title of the invention: Support assembly Technical field

[0001] The present disclosure relates to a support assembly, as well as to a stabilizer assembly for a vehicle comprising such a support assembly and a stabilizer bar.

[0002] The support assembly may be suitable for any joint, not only that of a vehicle stabilizer bar, but also for example a suspension wishbone or leaf spring joint. The stabilizer assembly may be suitable for any type of stabilizer bar and any type of vehicle, in order to limit the roll of the vehicle. In particular, such a stabilizer assembly may be used for any axle of the vehicle. Prior art

[0003] In a vehicle with axles, the two wheels of the same axle are generally connected by a stabilizer bar. The stabilizer bar, also called an anti-roll or anti-roll bar, is a suspension element of the vehicle. This bar has the function of creating a spring which unites the two wheels of the same axle. It thus makes it possible to reduce rolling during turns and to mitigate the deformations undergone by the suspension, in order to keep the tires of said wheels in optimal contact with the ground and to ensure maximum grip.

[0004] Each end of the stabilizer bar is thus fixed to the suspension triangle of a wheel, by means of ball-jointed rods, while its central part is fixed to the chassis of the vehicle using at least two bearings.

[0005] The function of these bearings is to allow the stabilizer bar to be fixed to the chassis of the vehicle while providing a certain flexibility, the stabilizer bar having to be able to move slightly relative to the chassis.

[0006] For this purpose, the bearings generally comprise a metal flange and an elastic ring interposed between the stabilizer bar and the flange. This elastic ring, often made of elastomer, is thus generally placed around the stabilizer bar and then gripped by the flange creating a compression which holds the ring in place.

[0007] Such bearings are generally covered by a bracket responsible for holding the stabilizer bar. The adhesion process, in particular gluing, must be carefully carried out to ensure adequate adhesion between the metal flange and the surface to which the bracket is fixed.

[0008] These bearings generally have excessive torsional rigidity (or stiffness). These bearings are then too rigid with regard to rotational movements around the longitudinal axis of the bearing. The bearing therefore transmits vibrations and shocks from the vehicle more directly to the passengers, because the bearing does not deform sufficiently to absorb such shocks. Driving becomes uncomfortable and generates unpleasant sensations for the vehicle's occupants.

[0009] In addition, excessive torsional rigidity can lead to premature wear of certain parts of the bearing due to a high concentration of stresses. More particularly, this excessive torsional rigidity generally occurs when the elastic ring is poorly bonded to the stabilizer bar. The elastic ring is then subjected to excessive mechanical torsional stresses which can weaken it. Thus, if the elastic ring is not correctly bonded, it can deform or crack prematurely, which can lead to failure of the bearing. Furthermore, sliding or unwanted movements between the elastic ring and the stabilizer bar appear due to this insufficient adhesion, thus generating a high noise.

[0010] Similarly, when the caliper and the metal flange are not properly bonded to each other, this can lead to interference between the two components when they are subjected to stresses generated by the movements of the vehicle, in particular during turns or sudden changes of direction. These stresses include, in addition to torsional forces, axial forces but also radial or conical forces. The axial forces are applied along the axis of the stabilizer bar, while the conical and radial forces act respectively diagonally and perpendicularly to this axis.

[0011] More specifically, this interference occurs because irregular or misaligned metal surfaces rub and collide with each other, generating unwanted vibrations and noise, in other words, clatter. In essence, an inadequate connection between the yoke and the metal flange allows torsional, axial, conical and / or radial forces to cause relative movements between the two parts, resulting in a grinding or rattling noise. To avoid this problem, it is then crucial to ensure optimal adhesion between these different components and therefore guarantee precise alignment when assembling them.

[0012] For the sake of clarity, it is recalled that noise refers to unwanted sounds or excessive friction noises between the bearing and the surface of the stabilizer bar but also between the caliper and the metal flange. For a driver, the noise generated can be extremely annoying for several reasons. Indeed, friction noises (by sliding) or grinding noises can make the journey uncomfortable for the driver. The driving experience is then unpleasant, especially over long distances. This phenomenon is particularly noticeable during the period Winter, when the polymer making up the elastic ring becomes harder due to lower temperatures. Thus, when the polymer hardens, it increases the risk of friction or squeaking, thus amplifying the noises perceived inside the vehicle. In addition, these excessive noises can distract the driver from their concentration on the road.

[0013] It is then essential to improve the adhesion between the elastic ring and the stabilizer bar, but also between the caliper and the metal flange, to be able to minimize the points of excessive tension and friction which could generate noise in the long term. In other words, it is important to be able to control more precisely the way in which the stabilizer bar interacts with the bearings to optimize the distribution of contact pressure when bonding the elastic ring to the stabilizer bar but also when bonding the caliper to the metal flange. Indeed, a uniform distribution of the contact pressure guarantees better contact between the surfaces to be bonded and avoids the concentration of stresses at a single point (tension points above).

[0014] There is therefore a real need for a support assembly for a vehicle stabilizer bar, as well as a vehicle stabilizer assembly which are free, at least in part, from the drawbacks inherent in the aforementioned known configurations. Presentation of the invention

[0015] The present disclosure relates to a support assembly, comprising at least: - a bearing comprising at least one flange part comprising at least one retaining portion and a cavity lined with an elastomer coating, the cavity being configured to receive at least partially a suspended member, which may in particular be a stabilizer bar, and - a bracket capable of covering the bearing. The elastomeric coating has variable radial hardness so as to exhibit variable torsional and radial stiffness.

[0016] Variable radial hardness refers to the ability of the elastomer, i.e. the elastomeric coating, to exhibit different levels of rigidity (or stiffness) along a radial distance from a central axis. Thus, the resistance of the elastomer to deformation varies as a function of the radial distance. The elastomeric coating of the invention is then formulated so that its resistance to deformation is higher or lower in different areas around the suspended member.

[0017] A variable radial hardness of the elastomer coating then contributes to reducing the unequal mechanical stresses (pressures) during the bonding of the suspended member and the elastomer coating but also during the adhesion of the stirrup and the flange part of the bearing.

[0018] More particularly, such variable radial hardness causes the elastomeric coating to exhibit equally variable torsional and radial stiffness. Appropriate variability of torsional and radial stiffness helps to maintain uniform pressure on the adhesive, thereby helping to ensure better adhesion. In other words, uniform pressure ensures close contact between the stirrup and the flange portion, as well as close contact between the elastomeric coating and the suspended member, thereby ensuring efficient transmission of loads and stresses, which minimizes the risks of unwanted movements or structural failures.

[0019] For example, the portions of the elastomer coating in contact with the stabilizer bar may be more rigid in order to provide better stability and support to the suspended member, thereby reducing the kinematic stresses which contribute to cracking or sliding of the elastomer coating on the suspended member but also to heterogenizing the contact pressure between the caliper and the flange portion. The bearing is therefore quieter and the noise is reduced, or even non-existent. Similarly, the portions of the elastomer coating furthest radially from the stabilizer bar may be formulated to be more flexible, which allows for better absorption of shocks and vibrations.

[0020] To control the radial hardness in different portions of the elastomer coating, it is proposed for this purpose to adjust the chemical composition or the internal structure of the elastomer. For this purpose, in order to control and adjust the radial hardness, it is known to those skilled in the art to adjust the proportions of the different components of the elastomer, such as monomers, polymers, vulcanizing agents and fillers.

[0021] Furthermore, it is also known to the person skilled in the art to evaluate the hardness of elastomeric materials using the Shore hardness scale. This scale measures the resistance of the material to penetration by a conical or spherical tip, thus recording its hardness. Thus, the different portions of the elastomeric coating have different levels of hardness measured according to the Shore scale. In any event, the person skilled in the art is able, understanding the usefulness of having an elastomeric coating having a radially variable hardness, to define the different levels of radial hardness across the layers of the elastomeric coating that he considers more suited to the specific needs and constraints of his application.

[0022] In certain embodiments, the bearing is adhered to the caliper by gluing, cold or hot, or by vulcanization.

[0023] There are then at least two alternatives for bonding the bearing, in particular the flange part, to the caliper. In the case of gluing, an adhesive is applied to the contacting surfaces of the bearing and the caliper. These surfaces are then assembled and subjected to appropriate pressure to promote a strong and durable bond. The The choice of adhesive often depends on the materials the bearing and caliper are made of (usually steel, aluminum, or composite material), as well as the intended operating conditions, such as temperature, humidity, and mechanical stresses to which the assembly will be exposed.

[0024] As for vulcanization, it is recalled that this method involves the use of heat and pressure on the bearing in the presence of a vulcanizing agent. This chemical process transforms the material into a more rigid and resistant structure, thus promoting its adhesion to the caliper.

[0025] According to certain embodiments, the elastomer coating comprises a first radial portion, a second radial portion and a third radial portion successive in the direction of a central axis of the cavity, the elastomer coating having a variable radial hardness over the entire first, second and third radial portions.

[0026] This embodiment relates to the presence of three successive radial portions of the elastomer coating: a first radial portion, a second radial portion and a third radial portion. Each radial portion has a variable radial hardness which decreases or increases progressively in the direction of the central axis of the cavity.

[0027] For example, the first radial portion and the second radial portion may each have a decreasing radial hardness while the third radial portion has an increasing radial hardness. Conversely, the first radial portion and the second radial portion may each have an increasing radial hardness while the third radial portion has a decreasing radial hardness. From these two examples, the person skilled in the art understands that several combinations not described are possible as long as each portion has a decreasing or increasing variable hardness. Thus, each radial portion may have specific physical properties, a specific chemical composition, or other characteristics that can be adjusted to meet the specific needs of the design of a stabilizer assembly.

[0028] As indicated above, the variation in radial hardness, especially when it is gradual, can be achieved by adjustments to the chemical formulation of the elastomer or by modifications in the internal structure of the material.

[0029] Of course, the person skilled in the art also understands that a “portion” of the elastomeric coating corresponds to a specific layer of this coating which is arranged around the suspended member in a manner which follows a radial direction from the center of the suspended member. Each portion (or layer) can therefore be in direct contact with the suspended member, in other words positioned immediately adjacent to the surface of the stabilizer bar without any material between said portion and the suspended member, or may be in indirect contact with the suspended member, that is, separated from the surface of the suspended member by one or more other layers or portions.

[0030] In some embodiments, the flange portion is annular, its cavity being cylindrical, conical, and / or elliptical, U-shaped, or omega-shaped in cross-section and configured to completely surround the suspended member.

[0031] The present disclosure further relates to a support assembly, as defined above, further comprising a second bearing with at least one flange portion comprising at least one retaining portion and a cavity lined with an elastomeric coating, the stirrup being capable of covering the second bearing. The first and second bearings are assembled so that the cavity of the second bearing receives the first bearing, the second bearing being adhered to the stirrup and to the first bearing.

[0032] In this configuration, the first bearing is inserted, integrated or incorporated into the second bearing. In other words, the second bearing is radially further away than the first bearing from the central axis of the cavity. Each bearing, whether the first bearing or the second bearing, may then have the configurations and / or properties described above. For example, the first bearing and / or the second bearing may have an elastomer coating with a variable hardness that increases or decreases according to a first configuration or an elastomer coating comprising a first radial portion, a second radial portion and a third radial portion successively in the direction of the central axis of the cavity, the elastomer coating having a variable radial hardness over the entire first, second and third radial portions.

[0033] Once the first bearing and the second bearing are assembled, the stirrup is then positioned so as to cover the second bearing.

[0034] According to certain embodiments, the second bearing is adhered to the first bearing and to the caliper by gluing, cold or hot, or by vulcanization.

[0035] The person skilled in the art understands that the first bearing and the second bearing are assembled by known methods: vulcanization or bonding. For the sake of clarity, it is recalled that vulcanization is a chemical manufacturing process which involves the treatment of an elastomeric material with vulcanizing agents. The person skilled in the art is able to choose bonding or vulcanization as the method for assembling the first bearing and the second bearing depending on his needs and the specific constraints of his application.

[0036] According to certain embodiments, the flange portion of the first bearing and the second bearing is annular. The elastomer coating of the first bearing comprises on its outer surface intended to be in contact with the elastomer coating of the second bearing at least one boss and / or a hollow intended to fit in a manner complementary to the shape of the outer surface of the elastomeric coating with which it is in contact.

[0037] The outer surface of the elastomer coating of the first bearing is specifically designed to be in contact with the outer surface of the elastomer coating of the second bearing. On the outer surface of each of the two bearings, there is at least one boss and / or hollow designed to fit complementary to the shape of the outer surface of the other bearing. In other words, said at least one boss and / or hollow of the first bearing is designed to fit with the irregularities of the outer surface of the elastomer coating of the second bearing, thus ensuring a close connection between the two bearings. This design then allows efficient transmission of loads and stresses between the two bearings. Indeed, the boss and / or hollow plays an advantageous role in preventing the first bearing and the second bearing from coming apart, in particular when they are subjected to axial forces.When an axial force is exerted on the assembly, it attempts to separate the two bearings from each other. However, due to the presence of boss(es) and / or depression(s), an interlock occurs between the two elastomeric surfaces in contact. In other words, this interlock creates additional resistance to axial movement between the two bearings, thus preventing any unwanted sliding or movement that could subsequently generate noise.

[0038] Of course, the boss(es) and / or hollows present are designed with a certain intentional roughness. This roughness is necessary to prevent sliding between the two surfaces in contact.

[0039] Several shapes of bosses and / or hollows are possible. For example, said at least one boss or said at least one hollow has a sinusoidal, square, rectangular, triangular or sawtooth shape.

[0040] According to certain embodiments, said outer surface intended to be in contact with the elastomer coating of the second bearing has a plurality of successive bosses and / or hollows.

[0041] Each of the successive bosses and / or hollows may have one of the shapes described above. For example, a first boss may have a square shape while a second successive boss has a triangular shape.

[0042] According to some embodiments, the flange portion of the first bearing and / or the second bearing is configured to fully engage the suspended member.

[0043] When the cavity completely surrounds the suspended member, the first bearing and / or the second are each considered "solid", which means that the first bearing and / or the second bearing each have(s) a unitary mechanical structure without significant slots, openings or discontinuities in their structure.

[0044] Thus, the cavity being a single piece, called monobloc (and not the result of the assembly of two split bearings each having a flange portion cavity). The suspended member is then completely directly enveloped by the cavity of the first bearing and indirectly completely enveloped by the cavity of the second bearing, or the suspended member is completely directly enveloped by the cavity of the first bearing only, or the suspended member is completely indirectly enveloped by the cavity of the second bearing only.

[0045] Alternatively, the first bearing and / or the second bearing comprises first and second flange elements configured to be fitted against each other, each flange element comprising a cavity portion lined with said elastomeric coating jointly forming said cavity of the flange portion.

[0046] More specifically, the flange portion of each bearing, i.e., the first bearing and / or the second bearing, forms a split-type bearing which therefore has a mechanical structure provided with a mechanism allowing it to be installed around the chassis or to be removed from its location.

[0047] According to certain embodiments, the elastomeric coating intended to be in direct contact with the stabilizer bar has a cylindrical shape designed to fit the diameter of the stabilizer bar.

[0048] This cylindrical shape aims to ensure a homogeneous distribution of the contact pressure between the suspended member and the elastomer coating during assembly of the bearing, which contributes to a better distribution of the adhesive used in the assembly of the elastomer coating and the suspended member. More particularly and as specified above, a uniform pressure allows optimal adhesion of the adhesive between the suspended member and the bearing, in particular the elastomer coating, thus ensuring a solid and reliable bond between these two components. In addition, to ensure effective adaptation to various stabilizer bar diameters, the elastomer coating is designed to adapt to the diameter of each member without compromising its integrity.

[0049] The present disclosure also relates to a stabilizer assembly for a vehicle, comprising:

[0050] - a stabilizer bar, and

[0051] - at least one support assembly as defined above, the stabilizer bar passing through the cavity of the flange part of the bearing and being integral with the bearing by means of its elastomeric coating; or

[0052] - at least one support assembly as defined above, the stabilizer bar passing through the cavity of the flange part of the first bearing and being secured to the first bearing by means of its elastomer coating.

[0053] The aforementioned characteristics and advantages, as well as others, will appear on reading the detailed description which follows, of examples of embodiment of the bearing, as well as of the proposed stabilizer assembly. This detailed description refers to the attached drawings.

[0054] The attached drawings are schematic and are intended primarily to illustrate the principles of the disclosure. In these drawings, from one figure to another, identical elements (or parts of elements) are identified by the same reference signs.

[0055] [Fig-1] [Fig.l] is a perspective view of a stabilizer assembly;

[0056] [Fig.2] [Fig.2] is a perspective view of an example of a bearing;

[0057] [Fig.3] [Fig.3] is a perspective view of the flange of [Fig.2];

[0058] [Fig.4] [Fig.4] is a sectional view of the flange of [Fig.2];

[0059] [Fig.5] [Fig.5] represents two sectional views of the flange of [Fig.2] according to a first embodiment of the invention;

[0060] [Fig.6] [Fig.6] represents two sectional views of the flange of [Fig.2] according to a second embodiment of the invention; and

[0061] [Fig.7] [Fig.7] illustrates an adhesive tape intended to surround a stabilizer bar of the stabilizer assembly, so as to constitute the elastomer coating of the bearing, according to a third embodiment of the invention. Description of the embodiments

[0062] In order to make the invention more concrete, an example of a stabilizing assembly is described in detail below, with reference to the accompanying drawings. It is recalled that the invention is not limited to this example.

[0063] [Fig.l] represents a stabilizing assembly 1 for a vehicle which is understood as any mobile structure, preferably an automobile such as a truck or a car or a utility vehicle, designed for the transport of people or goods.

[0064] More particularly, the stabilizer assembly 1 comprises a stabilizer bar 10, solid or hollow, painted or not, the central part 11 of which is equipped with two first support assemblies each comprising a first bearing 20. Such first bearings 20 are intended to be fixed to the chassis of the vehicle while ends 12 of the stabilizer bar 10 are intended to be fixed to parts of the vehicle integral with each wheel of the same axle, in particular the suspension triangle of each wheel of the axle. The first support assembly further comprises a stirrup (not visible in this figure) mounted on each first bearing 20 so as to hold the stabilizer bar 10 in position. For this purpose, each first bearing 20 is adhered to its stirrup by gluing or by vulcanization.

[0065] The first bearings 20 may be solid or in the form of two split bearings intended to be assembled together. More specifically, a solid bearing is characterized by a unitary mechanical structure without significant slots, openings or discontinuities in its structure whereas a split bearing (or half-bearing) has a mechanical structure with an opening or slot, allowing it to be installed around the frame and assembled with another split bearing or removed from around the frame.

[0066] For example, when the first bearing 20 is solid, it can completely envelop the stabilizer bar 10 along an axis A corresponding to the direction of extension of the stabilizer bar 10 when the first bearing 20 is mounted. On the other hand, when the first bearing 20 is split, it can surround the stabilizer bar 10 only on one side of the axis A while another first split bearing 20 surrounds the stabilizer bar 10 on the other side of the axis B.

[0067] In this example, the first bearing 20 is solid and has a general shape with a U-shaped cross-section but may, alternatively, have a cylindrical, conical and / or elliptical or omega-shaped cross-section. Since the flange portion 30 may also match the shape of the first bearing 20, its cavity may be cylindrical, conical and / or U-shaped, elliptical or omega-shaped cross-section so as to completely surround the stabilizer bar 10.

[0068] The flange portion 30 corresponds in this case to a flange 30. Such a solid bearing may be in the form of an adhesive tape, as illustrated in [Fig.7], specially designed to surround the stabilizer bar 10 by winding. More precisely, the method of applying this tape, so as to constitute the elastomeric coating of the bearing, consists of winding the tape around the stabilizer bar 10 thus ensuring close and uniform contact. Such tapes are available in different thicknesses to adapt to the specific needs of the application.

[0069] On the other hand, the flange portion 30 may be of semi-cylindrical, semi-conical or semi-elliptical shape when the first bearing 20 is split and thus partially surrounds the stabilizer bar 10. In the latter case, the flange portion 30 comprises first and second flange elements 30 configured to be attached to one another. Each flange element 30 then comprises a cavity portion, each lined with the elastomer coating 60, jointly forming said cavity of the flange portion 30.

[0070] It should be noted that the elastomer coating 60 of the first bearing 20 intended to be in direct contact with the stabilizer bar 10 may have an advantageously cylindrical shape. More precisely, this cylindrical shape aims to guarantee a homogeneous distribution of the contact pressure between the stabilizer bar 10 and the elastomer coating 60 during the assembly of the first bearing 20, which contributes to a better distribution of the glue used in the assembly of the elastomer coating 60 and the stabilizer bar 10. In addition, to guarantee effective adaptation to various diameters of stabilizer bar 10, the elastomer coating 60 is designed to adapt to the diameter of said stabilizer bar without compromising its integrity.

[0071] In the remainder of the description and for the sake of brevity, a "bearing" represents a solid bearing or a split-type bearing. In other words, the embodiments which refer to a solid bearing also refer and are perfectly applicable to a split-type bearing and vice versa.

[0072] Figures 3 and 4 show this flange portion 30 (or flange 30 in this example) of the first solid bearing 20 in perspective and in section along its median plane, respectively. Of course and as recalled above, the person skilled in the art is able to adapt the exemplary embodiments described below to a split bearing.

[0073] The flange part 30 comprises at least one retaining portion 31 which extends laterally to the axis A as illustrated in [Fig.4] by a sectional view along the axis B. Each retaining portion 31 has a bearing surface 32 forming the bearing surface of the flange part 30 and more broadly of the first bearing 20, and a through bore 33 perpendicular to the axis A and therefore perpendicular to the bearing surface of the flange part 30. Each bore 33 is provided with a metal sleeve 34. This metal sleeve 34 is here shouldered, that is to say T-shaped. However, in other examples, it could be simply cylindrical.

[0074] As illustrated in [Fig. 4], the first bearing 20 optionally comprises at least one insert 50 extending over substantially the entire length of the cavity of the flange portion 30. Such an insert 50 is embedded in the elastomer coating 60 (not visible in this figure). “Substantially” means that the insert 50 extends over at least 90% of the length of said cavity, preferably at least 99% of its length.

[0075] In the present example, the insert 50 takes the form of a two-dimensional sheet formed by a plurality of unidirectional cords extending in the same direction of extension, here the direction of the axis A. The sheet is arranged along the cavity of the flange portion 30 so that the insert 50 covers the entire surface of the cavity. The insert 50 can extend beyond the cavity so as to form at least a portion of the bearing surface 32 of each retaining tab 31. A fillet 51 is thus formed by the insert 50 at the interface between the cavity and the bearing surface 32. In the present example, each cord has a diameter of 2 mm and is made of polyamide reinforced with glass fibers. These glass fibers are continuous fibers. The cords are assembled together within the sheet using a resin which is also polyamide.

[0076] The insert 50 may be made of another material such as a metallic material, for example aluminum. The insert 50 may alternatively be made of plastic, its thickness being able to be 4 mm for example, or of a so-called “composite” material which refers to any material manufactured from the combination of two or more different materials.

[0077] Of course, the person skilled in the art is able to choose other materials that he considers more suitable depending on his specific needs and the constraints of the application. The choice of the material of the insert 50 may thus depend on the required mechanical properties, the corrosion resistance, the ease of manufacture and other technical considerations. For example, among the metallic materials commonly used for such applications, mention may be made of steel or aluminum.

[0078] In another variant, the insert 50 is formed from at least two insert segments (or sections) 50. For example, a first insert segment 50 extends over 50% of the length of said cavity of the flange portion 30 and a second insert segment 50 extends over 45% of the length of the cavity. Thus, the insert 50, by its first and second insert segments 50, extends over 95% of the length of the cavity.

[0079] Thanks to such an insert 50 in all of its variants, the mechanical strength and the radial stiffness of the flange portion 30 are significantly increased. As indicated above, the insert 50 is not an essential component of the first bearing 20, whether it is solid or split. In other words, the first bearing 20 has a first embodiment in which the flange portion 30 comprises the insert 50 and has a second embodiment in which the flange portion 30 does not contain the insert 50. It is further understood that all of the examples described in the present application apply equally well to a first bearing 20 comprising or not comprising the insert 50.

[0080] However, the addition of the insert 50 in the flange portion 30 of the first bearing 20 certainly helps to increase the radial stiffness of the first bearing 20 but does not make it possible to reduce, for example, the torsional rigidity (or stiffness), radial, conical or axial, of said first bearing 20, and which occurs when the elastomer coating is poorly bonded to the stabilizer bar.

[0081] The invention then proposes, according to a first variant, to improve the adhesion between the elastic ring (the elastomer coating 60) and the stabilizer bar 10 in the first bearing 20 and while improving the adhesion between the flange part 30 and the stirrup, the elastomer coating 60 having a variable radial hardness, which makes it possible to have a variable torsional and radial stiffness.

[0082] Indeed, a variable radial hardness of the elastomer coating 60 contributes to reducing the unequal mechanical stresses (pressures) on the bonding surface between the stabilizer bar 10 and the elastomer coating 60 which surrounds it but also on the bonding surface between the flange portion 30 and the stirrup. By minimizing the unequal stress points, the adhesion between the elastomer coating 60 and the stabilizer bar 10, but also between the stirrup and the flange portion 30, is improved.

[0083] More particularly, by the variability of the radial hardness, the elastomeric coating 60 has equally variable torsional and radial stiffness. Such variability in torsional and radial stiffness helps to maintain uniform pressure on the glue.

[0084] Such variable radial hardness may then be progressively increasing or decreasing in the direction of the stabilizer bar 10. In other words, the elastomer coating 60 exhibits a first tendency where its hardness progressively decreases as one approaches the stabilizer bar 10. In practice, this means that the portions of the elastomer coating 60 located closest to the stabilizer bar 10 are the most flexible, while the portions of the elastomer coating 60 furthest from the stabilizer bar 10 are the most rigid (hard). Furthermore, the elastomer coating 60 exhibits a second tendency where its hardness progressively increases as one approaches the stabilizer bar 10.In practice, this means that the portions of the elastomer coating 60 located closest to the stabilizer bar 10 are the most rigid (hard), while the portions of the elastomer coating 60 furthest from the stabilizer bar 10 are the most flexible.

[0085] Thus, as illustrated in [Fig. 5] which illustrates a longitudinal sectional view corresponding to the axis A and therefore in the direction of extension of the stabilizer bar 10, as well as a view according to a transverse section along the axis B, the elastomer coating 60 comprises a first radial portion PI, a second radial portion P2 and a third radial portion P3. In this example, the first portion PI, the second portion P2 and the third portion P3 together have a decreasing variable radial hardness. In other words, the hardness of the first portion PI is greater than the hardness of the second portion P2 which itself is greater than the third portion P3.

[0086] The flange portion 30 is here adhered to the stirrup 41 (which may be made of steel, aluminum or composite material) by gluing. The flange portion 30 may however be adhered to the stirrup 41 by vulcanization.

[0087] Thus, by this first variant, the pressure exerted on the stabilizer bar 10 by the elastomer coating 60, but also the pressure exerted on the stirrup 41 by the flange part 30 becomes substantially homogeneous. The adhesion between these components is therefore much better and the noise is reduced, or even eliminated.

[0088] The invention further proposes, according to a second variant, a second support assembly for the stabilizer bar 10, comprising the first bearing 20 as well as a second bearing 21 as shown in [Fig. 6]. More precisely, [Fig. 6] represents two views, exploded and non-exploded, according to a longitudinal section corresponding to the axis A and therefore to the direction of extension of the stabilizer bar 10. In this configuration, the first bearing 20 and the second bearing 21 are assembled so that the second bearing receives the first bearing 20. In other words, the second bearing 21 is radially further away than the first bearing 20 from the center of the stabilizer bar 10. Each bearing, whether the first bearing 20 or the second bearing 21, may have the configurations and / or the properties described above. For example, the first bearing 20 and / or the second bearing 21 may have an elastomer coating (referenced respectively 60 and 61) with a variable hardness that increases or decreases.

[0089] In this configuration, the second bearing 21 is surmounted by the stirrup 41 to which it is adhered by gluing, cold or hot, or by vulcanization.

[0090] Advantageously, it should however be noted that when the first bearing 20 has an elastomer coating 60 with a lower variable radial hardness than that of the elastomer coating 61 of the second bearing 21, the torsional stiffness of the bearing assembly is then lower, which allows a more flexible response to the forces applied to the stabilizer bar 10. The pressure exerted on the stabilizer bar 10 is therefore substantially homogeneous and the bonding of the stabilizer bar and the elastomer coating 60 of the first bearing 20, and the bonding between the flange portion 30 and the stirrup 41, becomes better.

[0091] Furthermore, it should be noted that in this second variant, the flange portion 30 of the first bearing 20 and / or the second bearing 21 may be configured to completely surround the stabilizer bar 10. In this case, the first bearing 20 and / or the second bearing 21 are each considered “solid”, which means that the first bearing 20 and / or the second bearing 21 each has a mechanical structure without significant slots, openings or discontinuities in its structure. Of course, this does not exclude the first bearing 20 and / or the second bearing 21 being (or are depending on the context) split-type bearings.In the latter case, the first bearing 20 and / or the second bearing 21 comprises first and second flange elements 30 configured to be attached to each other, each flange element 30 comprising a portion of the cavity lined with said elastomer coating (referenced respectively 60, 61) jointly forming said cavity of the flange part 30.

[0092] The first bearing 20 and the second bearing 21 can also be assembled to each other using different methods known to those skilled in the art, such as overmolding, vulcanization, or gluing, cold or hot.

[0093] Furthermore, the first bearing 20 and / or the second bearing 21 may each comprise the insert 50 which extends substantially along the entire length of the elastomer coating 60 of the cavity of the flange portion 30 of the first bearing 20 and / or along the entire length of the elastomer coating 61 of the second bearing 21. As indicated above, the insert 50 as illustrated in the second bearing 21 makes it possible to further increase the mechanical strength as well as the radial stiffness of the flange portion 30 of the bearing concerned. Alternatively to this configuration, it is possible to position the insert 50 at the interface between the first bearing 20 and the second bearing 21 so that it extends substantially over the entire length of said interface. This latter configuration of the insert is particularly advantageous because the elastomeric coating 61 of the second bearing 21 infiltrates through the openings (or holes) of the insert thus positioned, which makes it possible to create a robust mechanical connection between the first bearing 20 and the second bearing 21. Such a connection thus reinforces the structural integrity of the support assembly.

[0094] Furthermore, as illustrated in [Fig. 6], the elastomer coating 60 of the first bearing 20 comprises on its outer surface intended to be in contact with the elastomer coating 61 of the second bearing 21 a hollow 71 intended to match in a complementary manner the shape (boss 81 here) of the outer surface of the elastomer coating 61 with which it is in contact.

[0095] The boss 81 and / or the recess 71, in this support assembly, plays an advantageous role in preventing disengagement between the first bearing 20 and the second bearing 21, in particular when they are subjected to axial forces. When an axial force is exerted on the assembly, it attempts to separate the two bearings 20, 21 from each other. However, thanks to the presence of the boss(es) 81 and / or the recess(es) 71, an interlock occurs between the two elastomeric surfaces in contact. In other words, this interlock creates additional resistance to axial movement between the two bearings 20, 21, thus preventing any unwanted sliding or movement which could subsequently generate noise.

[0096] Several shapes of boss 81 and / or hollow 71 are possible. For example, boss 81 or hollow 71 has a sinusoidal, square, rectangular, triangular or sawtooth shape.

[0097] Of course, this does not exclude the embodiment in which said outer surface of the elastomer coating 60 of the first bearing 20 has a plurality of bosses 81 and / or successive hollows 71. For example, a first boss 81 may have a square shape while a second successive boss has a triangular shape. Consequently, this also does not exclude the outer surface of the elastomer coating 61 of the second bearing 21 having a plurality of bosses 81 and / or hollows 71 so as to match the shape of the outer surface of the elastomer coating 60 of the first bearing 20.

[0098] Although the present invention has been described with reference to specific exemplary embodiments, it is obvious that modifications and changes may be made to these examples without departing from the general scope of the invention as defined by the claims. In particular, although the bearing and bearing assembly have been described and illustrated in these examples in combination with a stabilizer bar lisatrice, their application is also conceivable for the support of other types of suspended members, and for example in a suspension triangle or leaf spring articulation. Furthermore, individual features of the different illustrated / mentioned embodiments may be combined in additional embodiments. Therefore, the description and the drawings should be considered in an illustrative rather than restrictive sense.

[0099] It is also obvious that all the characteristics described with reference to a method are transposable, alone or in combination, to a device, and conversely, all the characteristics described with reference to a device are transposable, alone or in combination, to a method.

Claims

Claims

1. Support assembly (20; 41), comprising at least: - a bearing (20) comprising at least one flange part (30) comprising at least one retaining portion (31) and a cavity lined with an elastomer coating (60), the cavity being configured to at least partially receive a suspended member, and - a stirrup (41) capable of covering the bearing (20); the support assembly (20; 41) being characterized in that the elastomer coating (60) has a variable radial hardness so as to have a variable torsional and radial stiffness.

2. Support assembly (20; 41) according to claim 1, in which the bearing (20) is adhered to the stirrup (41) by gluing or by vulcanization.

3. Support assembly (20; 41) according to claim 1 or 2, in which the elastomer coating (60) comprises a first radial portion (PI), a second radial portion (P2) and a third radial portion (P3) successive in the direction of a central axis (A) of the cavity, the elastomer coating (60) having a variable radial hardness over the whole of the first, second and third radial portions (PI; P2; P3).

4. A support assembly (20; 41) according to any one of claims 1 to 3, wherein the flange portion (30) is annular, the cavity being cylindrical, conical, and / or elliptical, U-shaped or omega-shaped in cross-section and configured to completely surround the suspended member.

5. Support assembly (20; 21; 41) according to any one of claims 1 to 4, comprising a second bearing (21) with at least one flange portion (30) having at least one retaining portion (31) and a cavity lined with an elastomeric coating (61), the stirrup (41) being capable of covering the second bearing (21), the support assembly (20; 24; 41) being characterized in that the first and second bearings (20; 21) are assembled so that the cavity of the second bearing (21) receives the first bearing (20) and in that the second bearing (21) is adhered to the stirrup (41) and to the first bearing (20).

6. A support assembly (20; 21; 41) according to claim 5, wherein the second bearing (21) is adhered to the first bearing (20) and to the stirrup (41) by gluing or by vulcanization.

7. Support assembly (20; 21; 41) according to claim 5 or 6, wherein the flange portion (30) of the first bearing (20) and of the second bearing (21) is annular, and wherein the elastomer coating (60) of the first bearing (20) comprises on its outer surface intended to be in contact with the elastomer coating (61) of the second bearing (21) at least one boss and / or a hollow intended to match in a complementary manner the shape of the outer surface of the elastomer coating (61) with which it is in contact.

8. Support assembly (20; 21; 41) according to claim 7, wherein said outer surface intended to be in contact with the elastomeric coating (61) of the second bearing (21) has a plurality of successive bosses and / or hollows.

9. A support assembly (20; 21; 41) according to any one of claims 5 to 8, wherein the flange portion (30) of the first bearing (20) and / or the second bearing is configured to completely surround the suspended member.

10. Support assembly (20; 21; 41), according to any one of claims 5 to 8, wherein the first bearing (20) and / or the second bearing (21) comprises first and second flange elements (30) configured to be attached against each other, each flange element (30) comprising a cavity portion lined with said elastomeric coating (60; 61) jointly forming said cavity of the flange portion (30).

11. A support assembly (20; 21; 41) according to any one of claims 5 to 10, wherein the elastomeric coating (60) intended to be in direct contact with the stabilizer bar (10) has a cylindrical shape adapted to fit a diameter of the suspended member.

12. Stabilizer assembly (1) for a vehicle, comprising: - a stabilizer bar (10), and - at least one support assembly (20; 41) according to any one of claims 1 to 4, the stabilizer bar (10) passing through the cavity of the flange portion (30) of the bearing (20) and being integral with the bearing (20) by means of its elastomeric coating (60); or - at least one support assembly (20; 21; 41) according to any one of claims 5 to 11, the stabilizer bar (10) passing through the cavity of the flange portion (30) of the first bearing (20) and being integral with the first bearing (20) via its elastomer coating (60).