• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:FR3082902A1
    申请号:FR1855692
    申请日:2018-06-26
    公开日:2019-12-27
    发明作者:Sebastien Bazard；Emmanuel Charles；Michel Lambert
    申请人:SKF AB；
    IPC主号:
    专利说明:

    Ball bearing, unit of measurement of friction torque under load equipped with such a bearing, and test bench for rotating device equipped with such a unit of measurement
    Technical field of the invention
    The present invention relates to the field of ball bearings, and more particularly for use in units for measuring friction torque under load. The invention also relates to the field of test benches, and more particularly test benches intended for measuring the friction torque of a rotating device, in particular of a suspension stop device for a motor vehicle.
    State of the art
    In known manner, an automotive suspension system comprises a strut supporting an axle and a vehicle wheel. A suspension stop is arranged in the upper part of the strut, opposite the wheel and the ground, between a suspension spring and an upper member secured to the vehicle body. The spring is arranged around a damper piston rod, the end of which can be secured to the vehicle body.
    The suspension stop includes a bearing, a lower cup, an upper cup, and at least one seal disposed between the cups. The various constituent elements of the suspension stop can be formed from plastic, the cups being able to be reinforced by rigid inserts, in particular made of metal, in order to increase their mechanical resistance. The upper cup is interposed between an upper ring of the bearing and the upper member, while the lower cup is interposed between a lower ring of the bearing and the suspension spring. Thus, the suspension stop is adapted to transmit axial forces between the suspension spring and the vehicle body, while allowing relative angular movement between the rings of the bearing.
    The central axis of the suspension stop and the central axis of the strut with spring can be inclined relative to each other, the relative inclination of the axes can be between 5 ° and 10 °. The suspension stop is thus subjected to the resulting radial forces.
    In addition to the performance in mechanical strength and sealing, a key parameter of the quality of the suspension stop is its friction torque under load. It is essential to know this mechanical characteristic of the suspension stop because it will subsequently result in the suspension performance of the motor vehicle on which the stop will be installed, as well as its driving comfort. Dedicated test benches for measuring the friction torque under load of the suspension stops have been developed in order to optimize their structure, materials and designs. These test benches must propose test conditions approaching the application conditions.
    In known manner, a test bench for measuring the friction torque under load of a suspension stop comprises a tubular sleeve provided with a cylindrical bore in which two suspension stops are mounted head to tail, each of the stops being mounted at one of the axial ends of the bore. Each of the fixed cups of the stops is blocked in the bore. The movable cups in rotation of the stops are associated in rotation by a shaft, said shaft exerting a load on the stops. The bore extends around a central axis inclined relative to the horizontal at an angle characteristic of the relative inclination between each of the stops and the shaft simulating a strut. An oscillating movement in rotation about the central axis is applied to the shaft by a motor, said movement being transmitted to the two suspension stops tested.
    Such a test bench thus makes it possible to test suspension stops under conditions of oscillating movement, inclination, axial load and radial load (resulting from the defined inclination and the applied axial load) close to the application conditions . The test bench is also provided with at least one friction torque sensor to determine the friction torque resulting from the oscillation of the two suspension stops. The two associated stops for the friction torque measurement can be identical, or else different with a stop under test and the other stop being of known characteristics.
    The friction torque of a suspension stop tested in such a test bench is strongly influenced by the loads to which the suspension stop is subjected. In addition, this problem arises not only for the characterization of the friction torque under load of a suspension stop, but also for the characterization of any rotating device having application conditions under load. It is therefore desirable to provide a test bench with a unit for measuring the friction torque under load which ensures reliable and repeatable measurement.
    Furthermore, any rotating system under axial load, in particular a suspension stopper in use in a motor vehicle or tested in a test bench, but also other types of bearings such as clutch-declutching stops, is subject to the problem of moving its position between a loaded position and an unloaded position. Such a rotating system can be coupled to a rotating shaft and loaded axially. Such a shaft is generally mounted in a fixed casing, at least one bearing being interposed between the shaft and the casing in order to support said shaft in rotational movement.
    In this type of application, the bearing comprises an inner ring integral with the shaft with a raceway formed by a concave groove, an outer ring mounted in the casing and with a raceway formed by a concave groove, and at minus a row of balls between the raceways of the rings in order to support their relative rotation. It is known to mount the outer ring of the bearing with a free adjustment in the fixed casing, in order to allow the bearing to accompany the axial movement of the shaft.
    However, the rings can be found in non-optimized relative positions, with a radial plane alignment defect in particular. The contact between the balls and the rolling tracks can be angular, part of the axial load can then be transmitted from the shaft to the bearing. In addition, additional friction torque can be induced by the bearing, affecting the torque of the shaft and therefore of the rotating system. It is therefore desirable to provide a bearing suitable for an application with a rotating system and under axial load, in particular a test bench with a unit for measuring friction torque under load.
    Summary of the invention
    The present invention aims to provide a ball bearing which makes it possible to support a device in rotation and under load without the above-mentioned disadvantages, which is particularly usable in a unit for measuring friction torque under load of a rotating device, for example a suspension stop, capable of reproducing the conditions of application, being adaptable for any type of rotating device, and delivering reliable and repeatable measurements.
    The invention relates to a ball bearing comprising a first ring provided with a first raceway, a second ring provided with a second raceway, the two rings being concentric and in relative rotation about a central axis, and a row of balls mounted radially between said first and second rolling tracks.
    According to the invention, the first raceway is a concave annular groove formed on a surface of the first ring, and the second raceway is a cylindrical surface of the second ring.
    Thanks to the invention, an axial movement of the first ring drives the balls housed in the groove forming the first raceway, these balls sliding axially against the cylindrical surface forming the second raceway of the second ring. Whatever the relative radial position between the first and second rings, the rolling between the balls and the rings is optimized without inducing additional friction torque.
    According to other advantageous but not compulsory characteristics of the ball bearing, taken individually or in combination:
    - The bearing includes a cage for circumferentially holding the balls.
    - The first ring is an inner ring provided with a bore and an outer cylindrical surface, the first raceway being a concave annular groove formed in said outer cylindrical surface, and the second ring is an outer ring provided with a outer surface and a cylindrical inner bore, the second raceway being formed by said cylindrical inner bore.
    - The first ring is an inner ring provided with a bore and an outer cylindrical surface, the first raceway being formed by said outer cylindrical surface, and the second ring is an inner ring provided with an outer surface and d a cylindrical inner bore, the second raceway being a concave annular groove formed in said cylindrical inner bore.
    - The inner ring is rotating.
    - The outer ring is not rotating.
    According to another aspect, the invention relates to a unit for measuring friction torque under load for a rotating device and comprising a torque sensor.
    The measurement unit comprises a shaft, a first end of which is intended to be coupled to the rotating device. The measurement unit comprises a tubular casing with a central bore, and fixed to one face of a plate, said shaft passing through the plate and coming to extend in the bore of the casing.
    The measurement unit also comprises at least one bearing according to any one of the preceding embodiments, and which is interposed between the bore of the casing and the shaft in order to support said shaft in rotational movement. Said bearing comprises an inner ring mounted integrally on the shaft, an outer ring mounted integrally on the shaft, and a row of balls arranged between a first rolling track provided with one of the two rings and consisting of a concave annular groove formed on one surface, and a second raceway provided with the other ring and consisting of a cylindrical surface.
    The measuring unit comprises a measuring plate arranged in the casing, said measuring plate having a first face coupled to a second end of the shaft by means of an Oldham seal so that the shaft transmits only a torque to said measurement plate, said measurement plates and shaft having shapes corresponding to the Oldham seal, and said measurement plate having a second face cooperating with the torque sensor. A stop is interposed between the second end of the shaft and the first surface of the measurement plate, said stop comprising a first ring secured to the first surface of the measurement plate, a second ring secured to the second end of the shaft, at least one row of rolling elements interposed between the rings, the row of rolling elements radially surrounding the Oldham joint.
    The rotating shaft and under load of the measurement unit is thus supported by a ball bearing according to the invention. When the shaft is not under load, the components of the ball bearing are each in a given position ensuring the rotation of the shaft. When the shaft is under load, said shaft moves axially. The inner ring of the bearing follows this axial movement, the outer ring remaining fixed in the housing. The balls slide axially on the cylindrical surface of the second raceway during the relative axial displacement of the bearing rings, said balls being axially maintained in the first recessed raceway, and being axially free relative to the second raceway cylindrical. Thanks to the invention, the bearing does not induce additional friction torque, the torque measured by the measurement unit being that of the rotating device. In addition, no residual part of the axial load is transmitted to the bearing.
    According to other advantageous but not compulsory characteristics of the unit of measurement, taken individually or in combination:
    - The second face of the measurement plate includes a projecting portion coupled with the torque sensor.
    - The housing includes a free end located opposite the shaft, and closed by a cover.
    - The torque sensor is also provided with a load measurement means.
    - The measurement unit includes a temporary coupling means between the cover and the casing, the cover coming into contact with the torque sensor.
    - The temporary coupling means comprises at least one screw extending into corresponding holes in the cover and the casing.
    - The measurement unit comprises a temporary coupling means between the measurement plate and the housing, the measurement plate then being fixed to the housing.
    - The measurement plate comprises at least one portion in radial projection capable of cooperating with the temporary coupling means and the casing.
    - The casing comprises at least one window in which is housed the at least one portion in radial projection of the measurement plate.
    - The temporary coupling means comprises at least one screw extending into corresponding holes in the measuring plate and the casing.
    According to another aspect, the present invention also relates to a test bench for measuring the friction torque of a rotating device, comprising a first fixed plate, a second plate movable in translation able to approach or move away from said first plate so as to be able to apply an axial load to the rotating device, a test chamber defined between said plates, a drive means integral with the first plate, a measurement unit integral with the second plate and in accordance with any one of the preceding modes of embodiment of the invention, a first support coupled in rotation with the drive means and a second support coupled with the measuring unit, the first support being intended to be integral with a first element movable in rotation of a device rotating arranged in the test chamber, the second support being intended to be integral with a second element of said rotating device.
    Brief description of the drawings
    The invention will be better understood on reading the description which follows given solely by way of nonlimiting example.
    The description is made with reference to the accompanying drawings in which:
    - Figure 1 is a front view of a test bench for suspension stop device and equipped with a measurement unit according to the invention;
    - Figure 2 is a perspective side view of the test bench of Figure 1;
    - Figure 3 is a detail view of a suspension stop device in the test bench of Figure 1 in an axial section;
    - Figure 4 is a detailed perspective view of a drive means for the test bench of Figure 1;
    - Figure 5 is a detail view of the measurement unit of the test bench of Figure 1 in an axial section I-I;
    - Figure 6 is a detail view of the measurement unit of Figure 5 along an axial section II-II in a first configuration;
    - Figure 7 is a detail view of the measurement unit of Figure 5 along an axial section II-II in a second configuration; and
    - Figure 8 is a view of a bearing for the measurement unit of Figure 5 in an axial section.
    detailed description
    Figures 1 and 2 illustrate a test bench, referenced 1 as a whole, for measuring the friction torque of a rotating device 2, here a suspension stop. For reasons of clarity of the description and of the Figures, the test bench 1 is not illustrated with the fixed chassis which supports and secures it to the ground.
    The test bench 1 comprises a first lower plate 3. This first plate 3 extends along a horizontal plane, is fixed and integral with the chassis of the test bench 1.
    The test bench 1 comprises a second plate 4. This second plate 4 extends along a horizontal plane parallel to the first plate 3, and is movable in translation relative to the first plate 3.
    The test bench 1 comprises four tubular guides 5, integral with the first plate 3 and with a third upper plate 7 also fixed and integral with the chassis. The tubular guides 5 each extend between the first lower plate 3 and the third fixed upper plate 7, along an axis perpendicular to the plates 3, 4 and 7. The tubular guides 5 pass through the second movable plate 4, and each form a guide in translation of said plate 4.
    The test bench 1 also includes a movement transmission mechanism 6, here of known type with screw 8, which ensures the translational movement of the second plate 4. The transmission mechanism 6 is advantageously fixed on the third plate 7 The second plate 4 is movable in translation between the first plate 3 and the third plate 7.
    The test bench 1 comprises a test chamber 9 defined between the first fixed plate 3 and the second plate 4 movable in translation. The suspension stop 2 intended to be tested in the test bench is housed in said test chamber 9.
    The second plate 4 is movable in translation in order to exert an axial load on the suspension stop 2 tested in the test bench 1, as will be explained in more detail below. The second plate 4 remains fixed during the tests, and is only put into translation during the configuration and adjustment phases of the test conditions.
    Advantageously, the first and second plates 3, 4 each comprise a thickness of thermally insulating material 3-1, 41 respectively, on their internal faces in the test chamber 9.
    According to a variant not illustrated, the test bench 1 comprises a support frame with side walls also covered with a thickness of thermally insulating material on their internal faces in the test chamber 9. The test chamber 9 is thus isolated thermally. Advantageously, the test bench can also include a temperature regulation means (not illustrated) inside the test chamber 9 so as to regulate the temperature of the tests in order to reproduce the conditions of application. It is also possible to provide a means of checking the humidity in the test chamber 9.
    The test bench 1 comprises a drive means 10 integral with the first fixed lower plate 3, and a first lower support 11 coupled in rotation with the drive means 10. The test bench 1 also includes a measurement unit 12 secured to the second upper plate 4 movable in translation, and a second upper support 13 coupled with the measurement unit 12. The suspension stop 2 intended to be tested in the test bench 1 is coupled to the first support 11 d on the one hand, and on the second support 13 on the other hand.
    FIG. 3 illustrates the suspension stop 2 mounted in the test chamber of the test bench 1. The suspension stop 2 here presented in this embodiment is of the MacPherson type (“MacPherson Suspension Bearing Unit” or “MSBU” in English).
    The suspension stopper 2 comprises a single bearing 14 with oblique contact, a lower cup 15 movable in rotation, and an upper cup 16. The suspension stopper 2 and its constituent elements generally have a shape of revolution, around a central axis X2. The cups 15 and 16 delimit between them an internal housing in which the bearing 14 is housed. The suspension stopper 2 may advantageously comprise external and / or internal sealing means in order to ensure the sealing of the bearing against external pollution .
    In the present embodiment, the bearing 14 comprises an inner ring, an outer ring, as well as a row of rolling elements, here balls, with oblique contact disposed between the rings (not referenced). The bearing 14 is preferably at an oblique contact in order to limit the forces and friction internal to the suspension stop 2 in service.
    The lower cup 15 is movable in rotation about the axis X2 and relative to the upper cup 16. The lower cup 15 is annular, and comprises a central tubular portion and a radial portion extending from the tubular portion towards the outside. The lower cup 15 forms a lower support for the bearing on a first upper axial side, and forms a support capable of cooperating with a strut spring of a vehicle on a second lower axial side.
    In the embodiment presented, the first lower support 11 of the test bench 1 comprises a support rod 17 which extends along an axis X17 inclined at an angle A17 relative to the axis X2 of the suspension stop 2. The support rod 17 comprises a lower first end 17-1 coupled to the drive means 10, the description of which will follow, and a second upper end 17-2 provided with a first adaptation means 18 in shape agreement with the lower surface of the lower cup 15. The first adaptation means 18 of the support rod 17 makes it possible to restore the structural and mechanical characteristics of a strut spring of a motor vehicle. The first adaptation means 18 is integral with the support rod 17 by means of at least one fixing screw 19. The first adaptation means 18 can thus be easily mounted or removed from the support rod 17, in particular by replacement case for a first means of adaptation of another shape adapted for another suspension stop tested.
    Alternatively, the support rod can be replaced by a strut provided at its second end with a spring intended to come into abutment against a bearing surface of the first cup of the suspension stop.
    The upper cup 16 is annular around the axis X2, and forms an upper support for the bearing 14. The upper cup 16 is generally fixed in a suspension device of a motor vehicle, said upper cup 16 being integral with the chassis of the vehicle. The suspension stop 2 is mounted in the test bench 1 so that the upper cup 16 is not fixed, and can transmit a friction torque induced by the oscillating rotary movement of the lower cup 15.
    In the embodiment presented, the second upper support 13 of the test bench 1 comprises a shaft 20 provided with a first lower end 20-1 coupled to the upper cup 16 of the suspension stop 2, and a second upper end 20-2 coupled to the measurement unit 12, the description of which will follow. The second support 13 also comprises a second adaptation element 21 integral with the upper cup 16, said second adaptation element 21 being coupled to the first end 20-1 of the shaft 20 via a pivot connection 22. Thus, the coupling between the shaft 20 and the suspension stop 2 is adaptable to any type of stop tested and of inclination of the support rod 17.
    Advantageously, the second adaptation element 21 may comprise a lower portion 21-1 secured to the upper cup 16, and an upper portion 21-2 coupled to the first end 20-1 of the shaft 20 via of the pivot link 22, the two portions 21-1 and 21-2 were integral with one another by a fixing screw 21-3. The lower portion 21-1 of the second adaptation means 21 can thus be easily mounted or dismounted from the upper portion 21-2, and therefore from the shaft 20, in particular in the event of replacement for a second adaptation means of another shape suitable for another suspension stop tested.
    Alternatively, the suspension stop can be of another structural design, the test bench 1 according to the invention being adapted to receive and test any type of suspension stop. Indeed, it suffices to provide the second end 17-2 of the support rod 17 with a first adaptation element with a lower cup and / or the first end 20-1 of the shaft 20 with a second element d 'adaptation with a top cup which are able to be coupled with these elements of the suspension stop to be tested.
    The first lower support 11 is coupled in rotation with the drive means 10. The first support 11 comprises the support rod 17 having a first end 17-1 coupled to the drive means 10, as illustrated in FIG. 4.
    The first support 11 comprises a guide 23 with which the first end 17-1 of the support rod 17 is coupled by means of a coupling element 24 with a pivot connection 25. The guide 23 comprises two transverse rails 23-1 and 23-2, the coupling element 24 comprising projecting portions capable of cooperating with said rails 23-1, 23-2. Once the coupling element 24 is positioned on the rails 23-1, 23-2 of the guide 23, the coupling element 24 is fixed in this desired position by fixing means (not shown), for example screws, clamping means or any other temporary fixing means. The rod 17 is thus coupled to the guide 23 so that an angle of inclination of the rod 17 can be defined relative to the suspension stop 2 on the one hand, and the guide 17 on the other hand.
    The first support 11 also comprises a support plate 26 coupled in rotation with the drive means 10. The guide 23 is integral in movement with support plate 26 by any suitable means, for example fixing screws. The rod 17 is thus coupled to the drive means 10 by means of the coupling element 24 mounted on the guide 23 which makes it possible to ensure an inclination of said rod 17, and of the support plate 26.
    The entire first support 11 is mounted on the fixed lower plate 3 of the test bench. The support plate 26 is driven by the drive means 10 via a shaft (not shown) passing through an opening provided with said plate 3.
    The drive means 10 is illustrated in Figure 1, and comprises a motor 27 rotating a drive plate 28 around an axis of rotation X28. A connecting rod 29 is provided with a first end coupled in pivot connection 30 with said drive plate 28, and with a second end coupled in pivot connection 31 with a first end of a crank 32. Said crank 32 has a second end coupled in rotation with the support plate 26 of the first support 11 by means of a shaft (not shown) passing through the lower plate 3.
    In the present embodiment of the invention, the drive means 10 is of the known type connecting rod-crank and makes it possible to transform a rotary movement into an oscillating movement around an axis. The crank 32 transmits this oscillating movement to the support plate 26, and by successive connections to the guide 23 with the coupling element 24, to the support rod 17 with the first adaptation means 18, and finally to the lower cup 15 of the suspension stop 2 tested in the test bench 1. The test bench 1 with such a drive means 10 makes it possible to reproduce the movements endured by the suspension stop 2 tested in the application conditions.
    In contrast to the drive means 10 to which the lower cup 15 of the suspension stop 2 is coupled, the test bench 1 comprises a measurement unit 12 coupled to the upper cup 16 of said stop 2.
    More specifically, the upper cup 16 is coupled to the measurement unit 12 via the second support 13 including the second adaptation means 21 coupled to the first end 20-1 of the shaft 20. The measurement unit measure 12 is illustrated in Figures 5 and 6 according to a first mounting configuration, and in Figure 7 according to a second mounting configuration.
    The measurement unit 12 comprises a tubular casing 33 with a central bore 33-1 extending along a central axis X33, and fixed on an external face of the second plate 4 movable in translation. The casing 33 advantageously comprises a radial rim 33-2, a plurality of fixing screws 34 passing through openings made through said rim 33-2 to come together with corresponding openings made in the second plate 4.
    The second plate 4 is also provided with a bore 4-2 traversed by the shaft 20, said shaft 20 coming to extend in the bore 33-1 of the casing 33 along an axis X20 coincident with the central axis X33. The shaft 20 thus makes it possible to couple on one side the suspension stop 2 in the test chamber 9 with the measurement unit 12 mounted on the side opposite to the second plate 4, outside of the test chamber 9.
    Two bearings 35, 36 are interposed between the bore 33-1 of the casing 33 and the shaft 20 in order to support said shaft 20 in rotational movement. In the present embodiment, the bearings 35, 36 are similar and only the bearing 36 will be described below, illustrated in detail in FIG. 8.
    The bearing 36 comprises an inner ring 33-2, an outer ring 33-3, the rings being concentric and in relative rotation about the central axis X33 of the bore 33-1 of the casing 33, and a row of balls 361 arranged radially between the rings.
    The shaft 20 comprises a stepped outer surface 20-3, the cylindrical surfaces on which the inner ring of the bearings 36 are mounted being formed to a smaller diameter than a middle part of the outer surface shaft of larger diameter. The inner ring 36-2 comprises a cylindrical bore 36-4 mounted tightly on a cylindrical portion of the outer surface 20-3 of the shaft 20. The shaft 20 thus has a stepped outer surface 20-3 allowing easy mounting of the bearings 35, 36. Shoulders are formed at the periphery of the shaft 20 in order to provide axial supports for the inner rings of the bearings 35, 36. Two retaining rings 37, 38 are mounted integrally on the shaft 20 in order to axially blocking the inner rings of the bearings 35, 36. A retaining ring 38 is notably mounted around the second end 20-2 of the shaft 20.
    Advantageously, the ring 37 is formed from a thermally insulating material in order to avoid a thermal bridge between the test chamber 9 and the measurement unit 12 through the shaft 20.
    The bore 33-1 of the housing 33 is essentially cylindrical. The outer ring 36-3 comprises a cylindrical outer surface 36-8 mounted tightly in the bore 33-1 of the casing 33. The casing 33-1 advantageously comprises a lower shoulder in order to ensure a lower axial retention for the outer ring of the bearing 35. An intermediate spacer 46 is mounted axially between the bearings 35 and 36 in order to ensure an upper axial retention of the outer ring of the bearing 35, and a lower axial retention of the outer ring 36-3 of the bearing 36. A ring holding 47 is mounted integrally in the bore 33-1 of the casing 33 in order to ensure upper axial retention of the outer ring 36-3 of the bearing 36.
    The inner ring 36-2 comprises a cylindrical outer surface 366 provided with a concave annular groove 36-5 forming an inner raceway in which the balls 36-1 are housed. The outer ring 36-3 comprises a cylindrical bore 36-7 forming an outer raceway against which the balls 36-1 are radially in contact. The relative rotation of the inner 36-2 and outer 36-3 rings around the central axis X33 is ensured by the rolling contacts between the balls 36-1 and the inner 36-5 and outer 36-7 tracks.
    In the illustrated embodiment, the inner ring 36-3 is massive, that is to say obtained by machining or grinding with removal of material from metal tubes, bars, forgings or laminated blanks . The outer ring 36-2 can be formed by cutting a metal tube, and rectify in order to adjust the geometric tolerances.
    Advantageously, the bearing 36 is also provided with an annular cage 36-9 provided with a plurality of recesses in which the balls 36-1 are housed. The balls 36-1 of the row are thus held circumferentially, and advantageously in a regularly spaced manner in order to standardize the loads.
    The support rod 17 being inclined relative to the lower cup 15 of the suspension stop 2 on the one hand, and the second plate 4 movable in translation applying an axial load on the suspension stop 2 on the other hand, radial loads are induced in the suspension stop 2, and on the upper cup 16 in particular. The radial loads exerted by the upper cup 16 on the shaft 20 are transmitted to the casing 33 fixed to the second plate 4 by means of the bearings 35, 36. This arrangement constitutes a means of filtering the radial loads so that they do not come not influence the friction torque measurements in the measurement unit 12.
    The measurement unit 12 also includes a measurement plate 39 arranged in the housing 33.
    The measuring plate 39 has a lower face coupled to the second end 20-2 of the shaft 20 via an Oldham seal 40 so that the shaft 20 transmits only a torque to said measuring plate 39. Oldham seals are well known in the art, and said measuring plates 39 and shaft 20 have shapes corresponding to Oldham 40 seals. More specifically, the underside of the measuring plate 39 includes a portion 39-1 projecting extending in a first axial plane, the second end 20-2 of the shaft 20 comprises a projecting portion 20-4 extending in a second axial plane and perpendicular to the first axial plane, and the seal of Oldham 40 comprises on its upper face a groove receiving the protruding portion 39-1 of the measuring plate 39, and on its lower face a groove receiving the protruding portion 20-4 of the shaft 20. The friction torque transmitted by the upper cup 16 of the stop d e suspension 2 when the lower cup 15 has an oscillating rotary movement is transmitted to the shaft 20, then to the measurement plate 39 via the Oldham seal 40.
    The measuring plate 39 has an upper face, opposite the lower face coupled to the seal of Oldham 40, which cooperates with a torque sensor 41. The upper face of the measuring plate 39 comprises a projecting portion 39-3 coupled with the torque sensor 41 by a plurality of fixing screws.
    A stop 42 with balls is axially interposed between the measuring plate 39 and the shaft 20.
    The stop 42 includes an upper ring which is secured to the underside of the measurement plate 39 by fixing screws. The stop 42 radially surrounds the seal of Oldham 40. The stop 42 comprises a lower ring which is integral with the second end 20-2 of the shaft 20, and even more precisely with the retaining ring 38 mounted at the end 20 -2 of the shaft 20. A row of rolling elements, here balls, is axially interposed between the upper and lower rings so as to form a stop 42 whose rings are rotating in parallel radial planes and around the 'axis X33. The stop 42 allows the axial loads to be transmitted between the shaft 20 and the measurement plate 39.
    FIG. 6 illustrates a first configuration of assembly and operation of the test bench 1, and in particular of the measurement unit 12.
    The housing 33 includes a free end situated opposite the shaft 20, and closed by a cover 43, the cover 43 coming into contact with the torque sensor 41 and the upper edge of the housing 33. The housing 33 and the cover 43 are secured to each other by fixing screws 44 fixed in openings made through the upper edge of the casing 33 and the cover 43.
    Thus, the second plate 4 can exert an axial load on the suspension stop 2 via the cover 43 secured to the casing 33. The axial load is transmitted from the second plate 4 successively to the casing 33, to the cover 43, to the sensor of torque 41, to the measuring plate 39, to the shaft 20 via the thrust bearing 42 with balls, then to the upper cup 16 of the suspension thrust bearing 2 by means of the second support 13. The bearings 35 , 36 are also freely mounted in the casing so as not to interfere with the axial load.
    Furthermore, and unlike the second mounting configuration of the measurement unit 12 illustrated in FIG. 7 and which will be described below, the measurement plate 39 and the housing 33 are separated from each other, fixing screws 42 having been removed. The measurement plate 39 is therefore free to deform under the effect of a friction torque transmitted by the shaft 20 via the Oidham seal 40.
    Thus the torque sensor 41 is coupled to the suspension stop 2. The drive means 10 applies an oscillating movement in rotation to the lower cup 15 of the suspension stop 2 via the first support 11. A torque of friction is generated between the lower cup 15 and the upper cup 16. This friction torque is transmitted from the upper cup 16 to the second support 13, and in particular to the shaft 20, then to the measurement plate 39 via the Oldham seal. The torque sensor 41 then measures the friction torque via the measuring plate 39.
    Advantageously, the torque sensor 41 can also be provided with a load measurement means.
    FIG. 7 illustrates a second configuration of assembly and operation of the test bench 1, and in particular of the measurement unit 12.
    The measurement plate 39 includes a portion 39-2 in radial projection. The housing 33 includes a window 33-3 in which is housed the portion 39-2 in radial projection of the measuring plate 39. The portion 39-2 comes to rest axially on with a radial flange 33-4 of the housing 33. The housing 33 and the measurement plate 39 are secured to one another by a fixing screw 45 fixed in openings made through the portion 39-2 and the flange 33-4.
    Advantageously, the measurement plate 39 can comprise a plurality of projecting portions 39-2, and the casing 33 can comprise as many windows 33-3 with radial rim 33-4 to cooperate with said portions 39-
    2.
    In the first mounting configuration of the measurement unit 12 illustrated in FIG. 6, the measurement plate 39 and the casing 33 are separated from one another.
    In this second mounting configuration of the measurement unit 12, the measurement plate 39 is fixed to the casing 33, and therefore to the second plate 4. The second plate 4 remains fixed during the tests, and is only brought into translation during the configuration and adjustment phases of the test conditions. The measuring plate 39 is therefore blocked in movement in this second mounting configuration. The friction torque transmitted by the shaft 20 to the measuring plate 39 via the Oldham seal 40 cannot be transmitted to the torque sensor 41.
    Furthermore, and contrary to the first mounting configuration of the measurement unit 12 illustrated in FIG. 6, the cover 43 and the casing 33 are separated from one another, the fixing screws 44 having been removed.
    The torque sensor 41 is not in charge with the measurement plate 39, and is not in a configuration for measuring the friction torque of said plate 39.
    On the one hand, the second plate 4 can exert an axial load on the suspension stop 2 via the measurement plate 39 secured to the housing 33. The axial load is transmitted from the second plate 4 successively to the housing 33, at measuring plate 39, to the shaft 20 by means of the stop 42 with balls, then to the upper cup 16 of the suspension stop 2 by means of the second support 13.
    On the other hand, the torque sensor 41 is decoupled from the suspension stop 2. The torque sensors known on the market are not suitable for operating continuously over long periods of time. Thanks to this second mounting configuration, it is possible to carry out endurance tests, and therefore for long periods of time, on a suspension stop 2 without having to use another test bench or to remove the measurement unit 12. The coupling / decoupling of the measurement unit 12 is greatly simplified by only the mounting / dismounting of fixing screws 44, 45.
    In the first configuration of the measurement unit 12 of the test bench 1, the shaft 20 is loaded axially. The inner ring of the bearing 36 is integral in rotation and axially with the shaft 20, and is in a first axial position. In the second configuration of the measurement unit 12 of the test bench 1, the shaft 20 is not loaded axially. Between these two configurations, the shaft 20 is axially offset, this offset being of the order of a tenth of a millimeter, or even a millimeter. The inner ring of the bearing 36 is thus found in a second axial position which is axially offset from its first position when the shaft 20 is loaded. The balls 36-1 are housed in the groove forming the inner raceway 36-5 of the inner ring 36-2, and thus accompany the axial movement of the inner ring 36-2 between the first and second positions. The outer ring 36-3 is fixed axially in the casing, the balls 36-1 repositioning axially by sliding on the cylindrical surface of the bore 36-7 of the outer ring 36-3. The balls 36-1 thus ensure the rotational support of the inner 36-2 and outer 36-3 rings of the bearing 36 in the two configurations of the test bench 1.
    The bearing 35 also has its inner ring and its balls adjusted axially with respect to its outer ring of cylindrical outer raceway in a manner similar to the bearing 36 previously described.
    The performances of the bearings 35, 36 are thus optimized and provide rotational support for the shaft 20 without inducing an additional friction torque. The torque sensor 41 measures a torque undisturbed by possible misalignment of the bearings 36-2, 36-3.
    The test bench 1 can therefore be used both for friction torque measurements in a first mounting configuration illustrated in FIG. 6, and for endurance tests in a second mounting configuration illustrated in FIG. 7, of any type. suspension stop in the conditions of applications of oscillating movement, inclinations, axial and radial loads, or even temperatures.
    It may be particularly advantageous to provide a series of tests including a first measurement of the friction torque of the suspension stop 2, then an endurance test, and a final measurement of the friction torque at the end of the endurance test. Intermediate friction torque measurements can also be considered. All this is made possible by the test bench according to the invention having two possible configurations, the transition from one configuration to the other being achievable in a simplified manner.
    The present invention of a measurement unit has been described in a nonlimiting example of a test bench for a suspension stop device. It is understood that a measurement unit in accordance with the invention can be implemented in any means for measuring friction torque under load of any rotating device operating under such application conditions.
    The present invention of a ball bearing has been described in a nonlimiting example of application to a test bench for a suspension stop device. A ball bearing according to the invention can be used in any other application with a rotating system.
    权利要求:
    Claims (9)
    [1" id="c-fr-0001]
    claims
    1. Bearing (35, 36) comprising a first ring (36-2) provided with a first raceway (36-5), a second ring (36-3) provided with a second raceway (36- 7), the two rings (36-2, 36-3) being concentric and in relative rotation about a central axis (X33), and a row of balls (36-1) mounted radially between said first and second tracks of bearing (36-5, 36-7), characterized in that the first raceway (36-5) is a concave annular groove formed on a surface (36-6) of the first ring (36-2), and the second raceway (36-7) is a cylindrical surface of the second ring (36-3).
    [2" id="c-fr-0002]
    2. Bearing according to claim 1, wherein a cage (36-9) is provided to circumferentially hold the balls (36-1).
    [3" id="c-fr-0003]
    3. A bearing according to any one of the preceding claims, in which the first ring (36-2) is an inner ring provided with a bore (36-4) and an outer cylindrical surface (36-6), the first raceway (36-5) being a concave annular groove formed at said outer cylindrical surface (36-6), and the second ring (36-3) is an outer ring provided with an outer surface (36-8) and a cylindrical inner bore (36-7), the second raceway being formed by said cylindrical inner bore (36-7).
    [4" id="c-fr-0004]
    4. A bearing according to any one of the preceding claims, wherein the first ring is an inner ring provided with a bore and an outer cylindrical surface, the first raceway being formed by said outer cylindrical surface, and the second ring is an inner ring provided with an outer surface and a cylindrical inner bore, the second raceway being a concave annular groove formed in said cylindrical inner bore.
    [5" id="c-fr-0005]
    5. Unit (12) for measuring friction torque under load for a rotating device (2) and comprising:
    - a torque sensor (41),
    - a shaft (20), a first end (20-1) of which is intended to be coupled to the rotating device (2),
    - A tubular casing (33) with a central bore (33-1), and fixed on one face of a plate (4), said shaft (20) passing through the plate (4) and coming to extend in the bore (33-1) of the housing (33),
    - at least one bearing (35, 36) according to any one of the preceding claims and which is interposed between the bore (33-1) of the casing (33) and the shaft (20) in order to support said shaft (20 ) in rotational movement, said bearing (35, 36) comprising an inner ring (36-2) mounted integrally on the shaft (20), an outer ring (36-3) mounted integrally in the casing (33), and a row of balls (36-1) arranged between a first raceway (36-5) provided with one of the two rings (36-2) and consisting of a concave annular groove formed on a surface (36-6) , and a second raceway (36-7) provided to the other ring (36-3) and consisting of a cylindrical surface,
    - a measurement plate (39) arranged in the casing (33), said measurement plate (39) having a first face coupled to a second end (20-2) of the shaft (20) by means of an Oldham seal (40) so that the shaft (20) transmits only a torque to said measurement plate (39), said measurement plates (39) and shaft (20) having shapes corresponding to the Oldham seal (40), and said measuring plate (39) having a second face cooperating with the torque sensor (41), and
    - a stop (42) interposed between the second end (20-2) of the shaft (20) and the first surface of the measurement plate (39), said stop (42) comprising a first ring integral with the first surface of the measuring plate (39), a second ring integral with the second end (20-2) of the shaft (20), at least one row of rolling elements interposed between the rings, the row of rolling elements radially surrounding the Oldham seal (40).
    [6" id="c-fr-0006]
    6. Unit of measurement according to any one of the preceding claims, in which the casing (33) comprises a free end situated opposite the shaft (20) and closed by a cover (43), and a means of temporary coupling (44) between the cover (43) and the casing (33), the cover (33) coming into contact with the torque sensor (41).
    [7" id="c-fr-0007]
    7. Measuring unit according to any one of the preceding claims, in which the measuring unit (12) comprises a temporary coupling means (45) between the measuring plate (39) and the casing (33), the plate measurement (39) then being fixed to the housing (33), the measurement plate (39) comprising at least one portion (39-2) in radial projection capable of cooperating with the temporary coupling means (45) and the housing ( 33).
    [8" id="c-fr-0008]
    8. Measuring unit according to any one of claims 6 to 8, in which the temporary coupling means comprises at least one screw (45) extending in corresponding holes of the measuring plate (39) and of the housing (33 ).
    [9" id="c-fr-0009]
    9. Test bench (1) for measuring the friction torque of a rotating device (2), comprising:
    - a first fixed plate (3),
    a second plate (4) movable in translation which can approach or move away from said first plate (3) so as to be able to apply an axial load to the rotating device (2),
    - a test chamber (9) defined between said plates (3, 4),
    - a drive means (10) integral with the first plate (3),
    - a measurement unit (12) according to any one of claims 5 to
    8, said measurement unit (12) being integral with the second plate (4),
    - A first support (11) coupled in rotation with the drive means (10), the first support (11) being intended to be integral with a first element (15) movable in rotation of a rotating device (2) arranged in the test chamber (9), and a second support (13) coupled with the measurement unit (12), the second support (13) being intended to be integral with a second element (16) of said rotating device (2).
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    同族专利:
    公开号 | 公开日
    JP2020003066A|2020-01-09|
    FR3082902B1|2020-11-27|
    KR20200001472A|2020-01-06|
    CN110645263A|2020-01-03|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2785566A|1954-03-15|1957-03-19|Barden Corp|Rolling quality tester for rolling bearings|
    US3200633A|1963-02-04|1965-08-17|Tamar Electronics Ind Inc|Torque test device|
    GB2197933A|1986-09-30|1988-06-02|Shigeo Takahashi|Roller structure|
    JPS6389428U|1986-12-01|1988-06-10|
    FR2659404A1|1990-03-12|1991-09-13|Skf Gmbh|BEARING FOR MOUNTING SHAFTS OR THE LIKE HAVING LIMITED AXIAL MOVEMENT.|
    US20060151235A1|2003-03-26|2006-07-13|Kazuo Chikaraishi|Steering device|CN111609892A|2020-07-01|2020-09-01|东山县极点工业设计有限公司|Improved precision evaluation equipment for grooved industrial products|
    CN111947925A|2020-08-03|2020-11-17|西安航天精密机电研究所|High-precision rolling bearing friction torque testing device and method|
    法律状态:
    2019-06-26| PLFP| Fee payment|Year of fee payment: 2 |
    2019-12-27| PLSC| Search report ready|Effective date: 20191227 |
    2020-06-26| PLFP| Fee payment|Year of fee payment: 3 |
    2021-06-25| PLFP| Fee payment|Year of fee payment: 4 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1855692A|FR3082902B1|2018-06-26|2018-06-26|BALL BEARING, UNIT OF MEASUREMENT OF FRICTION TORQUE UNDER LOAD EQUIPPED WITH SUCH A BEARING, AND TEST BENCH FOR ROTATING DEVICE EQUIPPED WITH SUCH A UNIT OF MEASUREMENT|
    FR1855692|2018-06-26|FR1855692A| FR3082902B1|2018-06-26|2018-06-26|BALL BEARING, UNIT OF MEASUREMENT OF FRICTION TORQUE UNDER LOAD EQUIPPED WITH SUCH A BEARING, AND TEST BENCH FOR ROTATING DEVICE EQUIPPED WITH SUCH A UNIT OF MEASUREMENT|
    KR1020190064211A| KR20200001472A|2018-06-26|2019-05-31|Ball bearing, unit for measuring friction torque under load provided with such a bearing, and test bench for rotating device provided with such a unit for measuring|
    CN201910547998.XA| CN110645263A|2018-06-26|2019-06-24|Ball bearing, friction torque measuring unit and test bench|
    JP2019117470A| JP2020003066A|2018-06-26|2019-06-25|Ball bearing, unit provided with the bearing for measuring friction torque under load, and test bench for rotary device provided with the unit for measuring|
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