FR2563592A1 - COUPLING WITH CLAWS AND INTERMEDIATE ELEMENTS FOR THE COMPENSATION OF RADIAL, ANGULAR AND / OR AXIAL SHIFT OF SHAFTS - Google Patents

Abstract

THIS COUPLING HAS A LEADING PART 3 WITH AT LEAST THREE CLAWS 5, A PART CONDUCTED WITH THE SAME NUMBER OF CLAWS 6 AND MOBILE TRANSMISSION ELEMENTS, ESPECIALLY IN THE FORM OF BALLS 7, BETWEEN THE LEADING CLAWS 5 AND THE LEADING CLAWS 6. THE SPACES BETWEEN THE TWO SERIES OF CLAWS, RECEIVING THE TRANSMISSION ELEMENTS 7, TIGHTEN RADIALLY INWARDS OR OUTSIDE, IN PARTICULAR IN THE FORM OF CORNERS. THE TRANSMISSION ELEMENTS ARE ELASTICALLY SUPPORTED, IN PARTICULAR BY AN ELASTIC RING 8 WHICH APPLIES EXTERNAL OR INTERNAL AGAINST THEM.

Description

The invention relates to a claw coupling for compensation of

  radial, angular and / or axial shifts

  of trees, including a leading part at the end of the drive shaft

  ment, a part driven at the end of the driven shaft, at least three claws on the driving part, the same number of claws on the driven part and mobile elements for transmitting torque between the

  leading claws and led claws.

  Known claw couplings are known.

  both of the transmission elements arranged movable between the claws.

  The transmission elements can be rigid and have the form

  of barrels for example or be made up of elastic elements

  only in compression. Also known are claw couplings with sliding corners and an elastic ring (couplings

  Keilflex). All of these couplings have the disadvantage that the

  possible offset is very limited and that the construction

  tion is too complicated. In addition, the sliding friction which

  occurs between the transmission elements and the claws occa-

  zion losses by friction and wear.

  The invention aims to create a claw coupling capable of compensating for greater radial, angular and / or axial shifts between the shafts than the couplings with

  known claws comprising mobile transmission elements.

  In addition, the coupling must have a certain torsional elasticity.

  nelle, so that it is able to dampen tor-

  and jolts in the transmitted torque.

  According to the invention, the spaces which exist on a coupling of the type defined at the start between the claws on the drive side and the claws on the driven side narrow radially inwards or outwards and the elements

  are resiliently supported. These trans-

  put the peripheral forces from the claws of the driving part to the claws of the driven part. Generally, the leading and driven parts will have the form of plates and the claws will be arranged with a uniform distribution on the periphery of the parts, so that they interpenetrate, while leaving between them intermediate spaces for the transmission elements. . These are kept applied against the claws by forces directed radially inwards or outwards. When transmitting peripheral forces, the transmission elements located in front of the driving claws, in the direction of the torque to be transmitted, are subjected to compression, which has the consequence that the elements extend to a certain extent from the narrowed space, by a radial displacement towards the outside or towards the inside and against the elastic forces by which they are applied against the claws. The transmission elements located behind the driving claws, in the direction of the transmitted torque, are not stressed by such compression. Under the effect of elastic forces, they can thus penetrate more into spaces

  shrunk. Thus, the elements, rotating on a circular path during-

  that no torque is transmitted, are alternately moved radia-

  inward and outward under the action of a couple. The assembly must be designed in such a way that the radial force tending to force the elements out of the narrowed spaces cannot

  not become greater than the elastic force now the elements

  applied against the claws. The coupling according to the invention makes it possible to compensate for angular, radial and axial deviations of the shafts. Despite the fact that it uses rigid transmission elements, it has a considerable torsional elasticity because the intermediate transmission elements are displaceable radially to the 'against elastic forces and because the alternately opposite displacements of the neighboring elements are accompanied by a relative rotation of the driving and driven parts. Therefore,

  the coupling also absorbs torsional vibrations. -

  The spaces receiving the transmission elements are delimited by cuneiform faces, or defining corners, claws. These active faces of the claws will generally be flat and parallel to the axis of the coupling, approach one another towards the inside or the outside and receive between them

  the transmission elements. These are preferably spherical

  risky or cylindrical. If the elements are convex or curved in the axial direction, so if they are balls or barrel-shaped elements, an angular offset of the trees is not likely to produce pressures on edges, which is a cause significant wear. According to the preferred embodiment of the invention, the transmission elements are supported by an elastic ring which is applied internally or externally against them. In this case, a single elastic member is sufficient to support all of the transmission elements. The radial force exerted by this ring on the transmission elements is a function of the position occupied by the element in the radial direction. As the elements loaded during the transmission of a torque are displaced approximately over the same radial distance, the radial forces exerted on them by the elastic ring are also substantially the same. He is leaving

  the same applies to items that are not requested during trans-

  mission of a couple. If the elastic ring is applied externally-

  ment against the elements, it may be surrounded by a rigid limiting ring. This limits the deformation of the elastic ring, so that it cannot be overloaded by the transmission elements pushed outwards. In the case of an elastic ring applying internally against the transmission elements, a rigid limiting piece, in the form of a ring for example, can be arranged in a similar manner inside the elastic ring. This limitation part also has the function of avoiding the overloading of the elastic ring by the elements pushed inwards during transmission.

  of a couple. The elastic ring can be supported by an elasto-

  mother, which enhances the damping effect during vibrations

  torsional and jerky in the transmitted torque.

  According to a preferred embodiment of the invention

  tion, balls are used as transmission elements and the faces of the claws against which the balls are applied are

  alternately inclined in opposite directions with respect to the axis.

  The axial inclination (inclination relative to a plane parallel to the axis of the coupling) of the claws, in addition to their radial inclination (relative to a radial plane), makes it possible to obtain a relatively large bending angle over mating. As in the case of constant velocity ball joints with crossed raceways for the balls, the use of a number

  pair of transmission elements provides compensation

  mutual action of the axial forces exerted by the balls under the load of a torque, so that the transmission elements are placed in the planbissector of the coupling in the event of

  bending of it. In this case, the balls are guided axially-

  ment, in particular by a rigid profiled ring which has practically

  the function of the constant velocity ball joint cage.

  According to a particular embodiment of the invention, each transmission element consists of a central cylindrical part carrying an axial journal on each

  end, as well as rollers rotatably mounted on the pins.

  The two faces of the adjacent claws, against which the transmission element is applied, are profiled so that the part

  central unit can only roll on one side and the

  rollers can only roll on the other side. This realization

  sation of the transmission elements such as double rollers and the corresponding profiling of the faces of the claws ensure that the transmission element can roll simultaneously on both sides, so that friction and wear are considerably reduced, in comparison for example with a transmission element

simple cylindrical.

  According to another embodiment, the transmission elements are rotatably mounted between two elastically deformable rings. The rings can be approached axially one of

  the other between the transmission elements and the zones thus brought together

  The rings may be provided with stops. As with the abovementioned limiting means for the elastic ring - applying against the inner side or the outer side of the transmission elements, this conformation of the rings limits their radial deformation, by

  so they cannot be overloaded.

  According to yet another embodiment of the invention, the transmission elements are individually resiliently supported on a rigid ring. While the torsional elasticity of the coupling is necessarily the same in both directions of rotation when the transmission elements are supported by a common elastic ring, the individual support of the elements, with alternately different stiffnesses of the springs, makes it possible to obtain different torsional elasticities for the two directions of rotation. Transmission elements can be supported

  by helical springs or leaf springs for example.

  Whatever the delivery method

  In addition, it also makes it possible to connect a solid shaft and a hollow shaft to each other, which is frequently necessary in drive systems for railway vehicles. When the number of transmission elements is even and greater than four, the coupling does not exhibit imbalances caused by these elements.

  Other features and advantages of the invention

  tion will emerge more clearly from the description which follows

  several non-limiting exemplary embodiments, as well as the accompanying drawings, in which:

  - Figure 1 is a side view of a coupler -

  claw ment according to a first embodiment of the invention; FIG. 2 is a cross section on a larger scale of the coupling of FIG. 1;

  - Figure 3 is a section along line III-

  III of Figure 2; - Figures 4, 5 and 6 are similar views of a claw coupling according to a second embodiment of the invention; - Figures 7 and 8 are cross sections of claw couplings according to a third and a fourth embodiment;

  - Figure 9 is a side view of a coupler -

  claw ment according to a fifth embodiment; - Figure 10 is a cross section on a larger scale of the coupling of Figure 9; - Figure 11 is a section along the line XI-XI of Figure 10; - Figure 12 is a partial side view of the coupling of Figure 10; Figures 13, 14, 15 and 16 are views similar to Figures 9 to 12 of a claw coupling according to a sixth embodiment of the invention; - Figure 17 is an axial section of a transmission element according to a particular embodiment;

  - Figure 18 is a schematic representation

  tick of a claw coupling according to a seventh embodiment

  sation of the invention; - Figure 19 is a partial section showing an alternative embodiment with respect to Figure 18; - Figure 20 is a partial plan view

  of the ring carrying an eighth embodiment of the delivery

  plement according to the invention, in which the transmission elements are supported individually; - Figure 21 is a section along the line XXI-XXI of Figure 20; and - Figure 22 is a partial plan view

  with tears of a ninth embodiment of the delivery

  clamping according to the invention.

  In the example of Figures 1 to 3, a part

  leading 3 in the form of a plate is formed on a drive shaft

  1 and a driven part 4 also in the form of a plate is formed on a driven shaft 2. Five wedge claws 5 are arranged with a uniform distribution, that is to say with an angle at the center of 72, at the periphery of the leading part 3. Five wedge-shaped claws 6 are arranged in the same way on the driven part 4 in the form of a tray. Ten cylindrical rollers 7, against which an elastic ring 8 is applied externally, are arranged between the faces 5a and 6a - forming corners - of the claws 5 on the drive side and of the claws 6 on the driven side. The ring 8 keeps the rollers applied elastically against the faces 5a and 6a of the claws by radial forces. When transmitting a torque from the claws 5 to the claws 6, the rollers 7, subjected to compression during this transmission, are pushed outwards against the elastic force of the ring 8, while the rollers 7 which are not compressive stresses are pressed further between the claws 5, 6 by the elastic force of the ring 8. The embodiment of Figures 4 to 6 differs from that of Figures 1 to 3, in addition by the lower number of claws, by the fact that the spaces between the claws 5 c8té drive and the claws 6 driven side narrow radially outward and by the fact that, by way of

  Consequently, the elastic ring 8 is applied against the inner side.

  laughing of the rollers 7. During the transmission of a torque, the rollers 7 subjected to compression are in this case pushed inwards against the radial forces of the ring 8, while the rollers not subjected to compression may deviate

  outwards under the radial forces of the ring 8.

  Figure 7 shows an embodiment where the claws 5 and 6 have faces 5a respectively 6a which are parallel on each claw, instead of delimiting wedge claws as in Figure 2 for example. Nevertheless, the faces 5a and 6a delimit cuneiform spaces between the claws 5 cSté

  drive and the claws 6 on the driven side, the spaces narrowed

  sant in this example in the form of corners inward, so that one obtains essentially the same conditions as in the embodiment according to Figures 1 to 3. The elastic ring 8

  is surrounded by a rigid outer ring 9 which limits the deformation

  mation of the ring 8 and excludes its overload.

  The example in Figure 9 corresponds substantially

  To that of Figure 5, except that the number of claws is lower.

  Another difference is that a cylindrical limiting piece is placed at a distance from it inside the elastic ring 8, in order to prevent it from being excessively deformed inwards.

  Figures 9 to 12 show an embodiment

  tion o the driving part and the driven part each carry four claws whose lateral faces 5a, 6a are inclined not only with respect to a radius, but also with respect to a plane parallel to the axis. As is apparent in particular from FIGS. 10 and 12, the two lateral faces 5a or 6a of a claw 5 or 6 are inclined in opposite directions relative to the axis; the tilt angle is 10 in this example. The axial inclination has the consequence, during the transmission of a torque, that the transmission balls 7 are stressed by axial forces which have alternately opposite directions, due to the alternating inclinations of the faces 5a and 6a. As these axial forces cancel each other out due to the even number of balls 7, the profiled ring 11 which guides the balls 7 axially can adjust in the bisector plane in the case of a bending of the coupling. For the axial guidance of the balls 7, the rigid ring 11 has a U-shaped profile and the centers of the balls 7 are located inside this profile. In this example, a flexible rubber ring 10 is interposed between the elastic ring 8 and the profiled ring 11. Damping in the coupling of torsional vibrations and jolts in the transmitted torque

is thus increased.

  The embodiment according to FIGS. 13 to 16 is essentially distinguished from that of FIGS. 9 to 12

  only by the fact that the spaces between the claws 5 and 6

  radiate outwardly and the elastic ring 8 is applied internally against the transmission balls 7. As in the example in FIGS. 9 to 12, the faces 5a and the faces 6a of the claws have opposite inclinations with respect to the axis and the balls 7 are guided in a rigid inner ring 11 having a U-shaped profile. A flexible rubber ring 10 is again

  provided in the profiled ring 11 to increase the damping.

  The operation of this coupling is essentially the same

  than in the example in Figures 9 to 12.

  Figure 17 shows a double roller used

  transmission element 7. It comprises a central cylinder

  drique 7a with axial trunnions 7b at the ends. Two rollers 7d are rotatably mounted by needle bearings 7c on the pins 7b. The cylindrical central part 7a and the cylindrical rollers 7d have the same outside diameter. The face 5a of the leading claw 5 has a projecting central zone, while the central zone on the face 6a of the driven claw 6 is arranged in withdrawal. On the marginal zones corresponding to the rollers 7d of the faces 5a and 6a, the arrangement is reversed: the face 5a is arranged in withdrawal in the two marginal zones,

  while the marginal zones on the face 6a are protruding.

  The central part 7a of the transmission element can therefore roll over the central zone of the face 5a while the rollers 7d

  roll on the marginal areas of the face 6a of the led claw.

  Thus, the transmission element performs rolling movements.

  pure on both sides; increased friction and wear which

  occur when sliding movements are avoided.

  The embodiment shown in Figure 18 differs from that of Figure 5 - besides by the lower number

  claws - by the nature of the elastic support of the rollers 7.

  Instead of an elastic ring 8 applied internally against the rollers 7, an elastic ring 8a is provided in this case on each side of the rollers 7. These are rotatably mounted on

  axes 12 between the rings 8a, as shown in the representation

  tion of Figure 19. The latter shows an example in which the two elastic rings 8a have close areas 8b between the rollers 7. The close areas are provided with stops 13 intended to limit the radial deformation of the rings 8a by the

claws.

  Figures 20 and 21 show yet another

  embodiment for the elastic support of the transmission elements

  sion 7, formed here by balls. Each of the balls 7 rests radially on the outside on a helical spring 17 which acts radially and is itself supported on a plate 15 disposed between

  two rigid and parallel bearing rings 14, which are assembled

  bolted by bolts 16 with spacers. This support

  individual transmission elements allows you to choose alterna-

  springs of different strengths, which gives a coupling

  plement having distinct torsional elasticities in the two directions of rotation. The embodiment according to FIG. 22 differs essentially from that of FIGS. 20 and 21 in that the coil springs 17 are replaced by leaf springs 18. The individual support thus obtained also offers the possibility of acting on different elastic forces. on the transmission elements 7. For this purpose, two leaf springs 18 acting on two neighboring transmission elements 7 are joined

  and mounted with the possibility of tilting on an axial post 19.

  The tilting of the leaf springs 18 on this tenon makes it possible to vary, in a dependent manner from one another, the thrust forces exerted on the transmission elements 7. Furthermore, the spacers 14a of the carrier rings 14 can be produced from so that they provide sliding guidance of the transmission elements 7

between them in the radial direction.

  List of references 1. Drive shaft 2. Drive shaft 3. Driving piece 4. Driving piece 5. Driving claws a. Lateral faces of the leading claws 6. Claws carried 6a. Side faces of the driven claws 7. Transmission elements 7a. Central part 7b. Trunnions 7c. Needle roller bearings 7d. Rollers 8. Elastic ring 8a. Side elastic ring 8b. Close areas of the rings 9. Rigid outer ring 9a. Rigid limiting piece - 10. Soft rubber ring 11. Profiled ring 12. Axles 13. Stops 14. Carrier ring 14a. Carrier ring spacers 15. Support plate 16. Bolts 17. Coil springs 18. Leaf springs 19 Axial pin

Claims (10)

  1. Claw coupling for compensating for radial, angular and / or axial shaft offsets, comprising a driving part at the end of the drive shaft, a part driven at the end of the driven shaft, at least three claws on the driving part, the same number of claws on the driven part and mobile torque transmission elements between the driving claws and the driven claws, characterized in that the spaces receiving the transmission elements (7) between the claws   leading (5) and. the claws driven (6) narrow inward   laughing or outward and are delimited by faces forming   corners (Sa, 6a) of the claws, and in that the elements of trans-   mission (7) are spherical, barrel-shaped or cylindrical elements and are resiliently supported and kept applied against the claws (5, 6) by forces directed inwards   narrowing and produced in particular by an elastic ring-   tick (8) which applies externally or internally, in   in the radial direction, against the transmission elements (7).   2. Coupling according to claim I, characterized in that the transmission element (7) consists of a cylindrical central part (7a) with an axial pin (7b) at each end and of rollers (7d) rotatably mounted on the pins (7b), and that the lateral face (Sa) of one of the claws (5) is raised in its central zone applied against the transmission element (7), while the face (6a) of the other claw (6) with which the transmission element is in contact present   an elevation in the two marginal zones.   3. Coupling according to claim 1 or 2, characterized in that the transmission elements (7) are   balls and the faces of the claws (5a, 6a) against which apply   swell the balls having alternating inclinations, of a   claw to another, relative to a plane parallel to the axis.   4. Coupling according to claim 3, characterized in that the balls are guided axially by a rigid profiled ring (11). 6359Z   5. Coupling according to any one of   Claims 1 to 4, characterized in that the elastic ring (8)   applied externally against transmission elements   is surrounded by a rigid limiting ring (9).   6. Coupling according to any one of   Claims 1 to 4, characterized in that a limiting piece   rigid tion (9a) is arranged inside the elastic ring-   tick (8) applied internally against the transmission elements. 7. Coupling according to any one of   Claims 1 to 4, characterized in that the transfer elements   mission (7) are rotatably mounted between two elastic rings (8a) only deformable.   8. Coupling according to claim 7, characterized in that the rings (8a) are axially brought towards one another between the transmission elements (7) and that the   close areas (8b) of the rings are provided with stops (13).   9. Coupling according to any one of   Claims 1 to 4, characterized in that the elements of   transmission (7) are individually resiliently supported on a rigid ring (14).   10. Coupling according to claim 9, characterized in that the transmission elements (7) are supported by helical springs (17) or springs with blades (18).