FR2459405A1 - ELASTIC COUPLING OF TREES - Google Patents

Abstract

THE INVENTION CONCERNS AN ELASTIC SHAFT COUPLING WITH TWO HALF-COUPLINGS 12, 14 FACING FACE TO FACE AND WHICH HAVE EACH OF THE OBLIQUE SURFACES 16, 18, 20, 24, 26, 28 ARRANGED IN CROSS-DIRECTION WITH RESPECT TO THE DIRECTION OF FORCE TRANSMISSION. THE OBLIQUE SURFACES 16 AND 24, 18 AND 26, 20 AND 28 OF THE ONE AND THE OTHER HALF-COUPLING 12, 14 ARE ARRANGED FACE TO FACE LIMITING AN INTERSTICE 34 OPENING RADIALLY AND IN WHICH IS A SLIDING BODY 42, 44, 46 WITH FLAT SLIDING SURFACES 52, 54, 56, 58, 60, 62 ADJACENT TO OBLIQUE SURFACES 16, 24, 18, 26, 20, 28. THIS ELASTIC COUPLING IS REMARKABLE BY THE FACT THAT AT LEAST ONE OF THE FLAT SLIDING OR OBLIQUE SURFACES OF AN INTERSTICE 34 IS LOCATED ON A COMPENSATION ELEMENT 74, 76, 78, 82, 84, 86 HAVING THE SHAPE OF A CAP-SHELL AND ITSELF HOUSING SO AS TO BE ABLE TO PIVOT IN ALL DIRECTIONS, IN A HOLLOW-SPHERE CRAPAUDINE 96 LOCATED IN THE HALF-COUPLINGS 12, 14 AND OR IN THE SLIDING BODIES 42, 44, 46. THE PIVOTING OF THESE COMPENSATION ELEMENTS ACCEPTS THE CORRESPONDING SURFACES OBLIQUE AND OF SLIDING REMAIN IN FULL CONTACT EVEN WHEN THE OPENING ANGLE OF THE INTERSTICES 34 CHANGES.

Description

The invention relates to an elastic coupling of shafts each of which

  half-couplings has at least two planar oblique surfaces oriented in a direction transverse to that of the transmission of force. The two oblique surfaces of one or the other half-coupling are arranged in pairs face to face and limit a gap opening radially. A

  sliding body at least disposed in a resilient bearing

  enter into the gap and carries for this purpose two plane sliding surfaces located back to back and adjacent to

the two flat oblique surfaces.

  Such an elastic coupling of trees has already been proposed

  in the first German publication 27.42.442. In this accou-

  The half-couplings are elastic and come in the form of planetary wheels with external teeth, which are surrounded by a central wheel with internal teeth. The flat oblique surfaces of the teeth of these planetary wheels are grouped in pairs facing each other and limit interstices which open radially outwards and in which these teeth mesh with each other.

keys of the central wheel.

  When this elastic coupling of trees transmits

  torque, the two half-couplings (planet wheels)

  res) rotate relative to each other. The interstices then shrink and the key-shaped teeth of the central wheel are pushed outwardly by working against an elastic force pushing inwards. This elastic force, which can be achieved in different forms, is responsible for the elasticity of the tree coupling described in the first German publication 27. 42.442. Due to the sliding of the wedge-shaped teeth of the central wheel on the flanks of the interstices, this elastic coupling is called

  coupling shafts with sliding keys ".

  When the half-couplings (planetary wheels) are rotated in the opposite direction according to a certain angle of rotation, the oblique surfaces do not move parallel, but have the same angle of rotation. This has the effect that the opening angle of the gap formed by two oblique surfaces facing each other

  opposite, decreases the angle of rotation of which we have just spoken.

  The higher the angle of rotation, the lower the opening angle.

  naked (becomes more acute). In the various constructions described by the first German publication 27.42.442, the teeth of the central wheel adapt to this angle modification of the gap by the fact that, taken separately, they can be deformed because they consist of flank portions which are articulately connected to the tips of the teeth. It is at this time that a spring force elastically separates the flank portions. If the flanks of the teeth are flat, then the oblique surfaces and the sliding surfaces are always exactly parallel; the adjacent plane arrangement makes it possible to transmit high torques without unacceptably high surface pressures occurring. To compensate for a misalignment of the trees to be coupled, it has been provided in the constructions described by the first German publication 27. 42.442 to give a convex shape to the

  teeth of the central wheel and / or planetary wheels.

  In this case, the flanks of the teeth are not flat,

  such that oblique surfaces and sliding surfaces

  only in line and that the torque is limited by the fact that a specific surface pressure

not be exceeded.

  The object of the invention is to ensure, for any exploitation of an elastic coupling, that the oblique surfaces and the

  adjacent sliding surfaces are strictly parallel.

  Regarding compensation for misalignment

  trees that we wish to mate, we must avoid the use of

  oblique surfaces of convex shape that prevent

adjacent plane position.

  With respect to the problem of changing the opening angle of the gap, the object of this invention is to achieve an adjacent planar disposition despite the fact that the opening angle of the gap varies and this without using elastically deformable teeth of the type described in

beginning of this memoir.

  The essential purpose of the invention can also be summarized

  the fact that mating proposed in the first publica-

  27.42.442 consists of an all-metal coupling in which, in all cases of use, the sliding surfaces and oblique surfaces are exactly parallel

  and are disposed adjacent.

  On the other hand, this coupling must be simple in its

  ception, therefore inexpensive, and its elasticity must

  Easily adapt to each type of application.

  Starting from a coupling of the type described at the beginning of this memorandum, this object is achieved, according to the invention, by the fact that at least one of the plane surfaces arranged face to face in a gap is on a compensation element having the shape of a shell shell which is arranged in a spherical hollow thrust and which can rotate in all directions, in that the number of interstices, in which is disposed each time a sliding body, varies between 2 and 12 and the fact that the sliding bodies are pushed by a locking ring in the interstices which are intended for them, ring which

  is characterized by a radial spring effect thanks to its deformation

non-spherical ability.

  The expression "compensating element" in the form of a shell "denotes a body which: is arranged, by a surface having the shape of a shell in cap and so as to be able to pivot, in a crapaudine hollow sphere,

  - is carried on a flat surface (slippery surface or over-

oblique face) of the interstice.

  It is ensured by the oscillating positioning with respect to a

  point of rotation of a sliding surface and / or the posi-

  tion of an opposite oblique surface, that the pivotable surface is always parallel to the other surface. Thus, without using deformable teeth of the type described above, but more particularly with the aid of a hard and totally inelastic metal sliding body, it is possible to compensate for

  this way tree misalignment and / or modification

  the opening angle of the gap.

  The choice of a determined number of interstices, namely of sliding body, makes it possible to easily adapt the coupling to

a given application.

  The locking ring is elastically deformed by the sliding bodies which exert a radial pressure (from the outside

  or from the inside) and it then deforms inversely (towards the

  inside or out) between the spaces in which it

adjoins the sliding bodies.

  As a result, the elasticity of the coupling depends on the constitution of the elastically deformable locking ring. If the wall strength of the locking ring is very small relative to the diameter, therefore the locking ring is

  easily deformable, this means that the elasticity of the

  It is superior to that of another embodiment having a locking ring of greater wall strength. The elasticity of the coupling can then also depend on

  the opening angle of the interstices. For a small angle of

  clearance of the interstices, for example, between 300 and 600 in the case of a coupling in the rest position, the radial force acting on the sliding body, for a given torque to be transmitted, is lower than that observed in FIG. the case of a larger opening angle. Therefore, the action of the locking ring on the elasticity of the coupling is lower than in the case of a larger opening angle between

the interstices.

  All considered, the elastic coupling of trees according to the

  present invention, meets the requirements for such an accu-

  from the point of view of both its constitution and its

  under given operating conditions, than its simple and safe torque transmission mechanism

  as well as the possibility of adjusting the elasticity of rota-

  tion. As for the angle of opening of the interstices, one can. add that the latter must be large enough to allow

  sliding surfaces to slide easily over

  that when rotating the half-couplings against each other, friction between adjacent surfaces

  be eliminated and allow radial movement of the

ment.

  In order to change the

  If necessary, it is necessary to have, between two adjacent gaps on the periphery of at least one half-coupling, at least one radial abutment intended for the locking ring which is preferably mobile or is elastic in the

radial direction.

  One of the interesting developments of this invention

  is that an even number of gliding bodies

  and two oblique surfaces, which correspond to different

  rents sliding body, being adjacent in one direction

  outside, are arranged on the same coupling half.

  In this way, it is possible to manufacture an elastic coupling of shafts according to the principle of a claw coupling, which is elastic in both directions of rotation and where interstices have been provided between each of the claws. For most applications, it is preferable that the locking ring surround the sliding bodies of such

  so that the interstices widen radially outwards.

  laughing. In the case of couplings which rotate at a very high speed of rotation, it is preferable that the locking ring be surrounded by the sliding bodies and thus be located inside so that the interstices widen.

radially inward.

  Another advantageous development of this invention,

  in that the compensating elements are arranged in

  half-couplings and sliding bodies are

  in the form of keys on which the sliding surfaces appear. In this form, such an embodiment applies more particularly to couplings intended for

  transmit a small torque, less than 100 T.P.M.

  for example. Indeed, in the case of such couplings, each of the elements is small to correspond to the needs requested, and in most cases, it is not possible to provide a sufficiently large location for the bodies of

  slip, except in the half-couplings.

  However, when it is a coupling intended for the transmission of larger torques, greater than 100 T.P.M. for example, and that spare parts have larger dimensions, it is preferable that

  compensation are housed in the sliding bodies and

slip surfaces.

  With regard to oblique surfaces, different shapes

  execution are possible. If the spacing of the trees to be accom-

  pler is low, for example equal to at most 1/100 to 1/75 of the diameter of the tree, and / or if the angle between the trees is small, for example at most equal to 2, then it is sufficient to In most cases, the oblique surfaces are provided directly on the half-couplings while the compensating elements are housed in the sliding bodies. In other cases where the conditions just mentioned are not fulfilled, it is preferable to fashion oblique surfaces on other compensating elements that have

  the shape of a shell in cap and which are housed in half

  couplings. As a result, the compensation elements are housed

  both in sliding bodies and in half-

  plements Other advantages and features as well as the mode

  action of different tree couplings according to the invention.

  will be described hereinafter in the exemplary embodiments and will be illustrated by diagrams. It is shown: in FIG. 1, a view in the direction of the axis of a coupling according to the invention not undergoing a torque;

  - in Figure 2, the section II-II through the object of the fi

  gure 1; in FIGS. 3 and 4, various positions where the compensation elements pivot in half-couplings and / or in sliding bodies;

  - in Figure 5, a view in the direction of the axis of the ac-

  coupling shown in Figure 1, whose half-couplings are subjected to a rotation torque which rotates in opposite directions, the locking ring being shown in section - in Figure 6, a section VI-VI across the object of Figure 5;

  - in Figure 7, in the illustration of the mode of action, a

  schematic presentation of the VII-VII section through the object of

  FIG. 6 and showing details according to sections VII of the FIGS.

  Figures 1 and 5; - In Figure 8, a section along the section line VIIIVIII through the object of Figure 1; - In Figure 9, a view in the direction of the axis (section IX-IX through Figure 10) of another coupling according to the invention undergoing no torque and presented in the form of a claw coupling; - In Figure 10, top view X on the object of Figure 9 with locking ring in section;

  - in FIG. 11, the XI-XI section through the object of the

  Figure 10 showing the sliding body spaced from the gap; in FIG. 12, the two half-couplings of FIG. 9 (above the plane XII-XII of FIG. 9) in developed view observed radially from the outside - in FIG. 13, a view in the direction of the axis of the half-coupling which carries four compensating elements which, according to particular modes of introduction, are driven into the slots of the half-couplings; in FIG. 14, the section XIV-XIV through the object of FIG. 13, the parts located behind the section plane being not shown; - In Figure 15, a section along line XV-XV of Figure 16 through a coupling according to the invention, undergoing no torque, and shown in the form of a claw coupling comprising four interstices; in FIG. 16, the XVI-XVI section through the object of FIG. 15;

  - in Figure 17, an overall developed view of the two half-

  couplings of Figure 15, observed radially from the outside

on another scale;

  - in Figure 18, a section perpendicular to the axis of the ac-

  coupling of FIG. 15, the half-couplings of which are

  trailed in the same direction by a rotation torque, the section being made along the section line XV-XV; - Figures 19 to 22, a disposition of a bearing cage

  needles between an oblique surface and a sliding surface

  is lying; - In Figure 23, an alternative embodiment of a coupling according to the invention with an inner locking ring in section along the section line XXIII-XXIII of Figure 24 in the state of rest;

  - in Figure 24, a section XXIV-XXIV through the coupling

  according to Figure 23; - in Figure 25, a longitudinal section along the line of

  section XXV-XXV of FIG. 24 through the half-coupling

  périeur; - In Figure 26, a section through the coupling of Figure 23 subjected to work and corresponding to the line of

cup XXIII-XXIII.

  Figure 1 shows a view of a coupling according to the pre-

  invention whose two half-couplings do not undergo a torque and which are therefore in the state of

rest.

  Figure 2 shows the section II-II through the object of the

  Figure 1. The arrow I shown in Figure 2 shows the di-

rection of the view of Figure 1.

  Of the two half-couplings 12 and 14 illustrated in FIG. 2, only the front half-coupling 12 is visible in FIG. 1. This front half-coupling 12 is provided with a central bore 102 while the rear half-coupling 14 has a central drilling 104. The drilling 102 is provided for the introduction of a transmission shaft, the bore 104 being provided for the output shaft. The fixing of the shafts is ensured by adjusting springs. Each of the half couplings has a disc

  circular coupling having a central hub.

  The front half-coupling 12 shown in FIG. 1 carries three hollow-sphere thrusters 96 distributed at angles that are equal to the periphery and which are arranged in vertical planes with respect to the plane of FIG. 1. In these three thrust bearings, with hollow spheres 96, are housed three compensating elements, 74, 76 and 78 having the shape of a shell in cap

  and being for example hemispherical. These three elements of

  Each of these three planar oblique surfaces extends at an angle transversely to the direction of transmission of the force. FIG. 2 is a sectional view of the hollow sphere thrust bearing 96 located in the front half-coupling 12, a compensating element 74 and its flat oblique surface 16. For

  simplifying, we are talking here about compensation elements "hemi

  However, these compensation elements need not be in the exact form of spheres cut in two, as is apparent from the accompanying figures. These compensating elements may be smaller or, if necessary, larger than hemispheres, but it is important that they be lodged by a spherical surface in the hollow sphere thrust and that they therefore

rotate in all directions.

  In the same way, but oriented in the opposite direction, elements

  82, 84, and 86 each having a required surface area.

  24, 26 and 28 are housed in hollow sphere thrust bearings 96 located in the rear half-coupling 14. A sliding body 42, 44 and 46 is arranged between the oblique surfaces 16, 18, 20 of the front half-coupling 12 and the oblique surfaces 24, 26, 28 of the rear half-coupling 14. This arrangement appears more clearly in the drawing of Figure 2. The sliding bodies elongate in the direction of the axis on both

half-couplings 12, 14.

  Are arranged in pairs facing each other, according to Figure 1 a) the flat oblique surfaces 16 and 24 of the compensation elements 74 and 82 which are housed in hollow sphere thrust bearings 96 of the front coupling half 12 and the coupling half-coupling back 14 so that the surfaces 16 and 24 are looking offset (see Fig. 2); b) the planar oblique surfaces 18 and 26 of the compensating elements 76 and 84 which are housed in hollow sphere thrusters 96 of the front half-coupling 12 and the rear coupling half 14, as well as c) the flat oblique surfaces 20 and 28 compensation elements 78 and 86 which are housed in hollow sphere thrust bearings 96 of the front coupling half 12 and the coupling half-coupling

back 14.

  Flat oblique surface of the front half coupling 12

  defines with a planar oblique surface of the half-coupling

  14, a gap 34 opening radially outward (see Fig.11). In each interstice is disposed a sliding body in the form of a key 42, 44 and 46. Each

  sliding body 42, 44 and 46 respectively carries surfaces

  these sliding planes 52, 54; 56, 58 and 60, 62 which abut a flat oblique surface of one of the six compensating elements 74, 76, 78, 82, 84 and 86. The cross sections of the sliding bodies are triangular. The three sliding bodies 42, 44 and 46 are held in the position marked by a locking ring 98 which surrounds them and operate in a manner similar to that described in the first German publication 27,42,442 cited at the beginning of this memoir and which relates to an elastic coupling of shafts, such as the teeth of a central wheel which

  surrounds two planetary wheels (comparable to half

  couplings 12 and 14). The locking ring 98 surrounds the half

  couplings at a distance "a" so that it forms

an annular slot 122.

  When the front coupling half 12, firmly connected to the transmission shaft, rotates in the direction of rotation 100, the flat oblique surfaces 16, 18 and 20 exert a pressure on

  the sliding surfaces 52, 56 and 60 of the three sliding bodies

  42, 44 and 46. A component of force, radial direction

  the outward, then acts on the sliding bodies. The latter rest on the outside of the locking ring 98 and transmit the rotation torque to the plane oblique surfaces

  24, 26 and 28 of the three compensating elements 82, 84 and 86

  In this transmission of a rotational torque, each of the substantially key-shaped sliding bodies 42, 44 and 46 is pressurized and sheared. To prevent them from getting caught between the two half-couplings, during this shear stress, the locking ring

  has two guide beads 99, 101

  nants. The sliding bodies are located between the guide surfaces 103, 105 of the guide beads, arranged facing each other and rotating radially inwards, and they can move outwardly but not in the direction of the axis.

  (see sliding body 46, fig.2 on the left).

  Each of the half-couplings 12, 14 has three V-shaped recesses located in its coupling disc and which are distributed at equal distances on the periphery. These hollows are aligned radially and widen outward. These recesses are intended to receive the sliding bodies 42, 44, 46 having

  the shape of keys. To this end, each hollow of the half-hinge

  the front is limited by a V-shaped surface 111, 113, and a counter-surface 112, 114, 116; the two surfaces intersect at the bottom of the hollow. The rear half-coupling 14 has corresponding V-shaped depressions. The V-shaped surface 311 and the counter-surface 312 of the rear half-coupling 14 are shown in FIG. 2. A hollow sphere truss 96 is

  disposed on each of the V-shaped surfaces of the two half-couplings.

  The inclination of each of the counter surfaces 112, 114, 116, 312

  corresponds to the inclination of the corresponding sliding body.

  In the "rest position" shown in FIG. 1, that is to say when the coupling undergoes no torque, the three sliding bodies 42, 44 and 46 abut by their two plane sliding surfaces 52, 54, 56, 58, 60, 62 a flat oblique surface 16, 18, 20 and a counter surface 112, 114, 116 of the front coupling half. This also occurs in the case of

  rear coupling half 14 (see fig.2).

he

  According to FIGS. 1 and 2, each of the half-couplings

  ments has three hollow sphere thrusts 96 in which

  is housed each time a pivoting compensation element

  around a center of rotation 72 (see fig.7).

  The shell-shaped shell design has a rotational surface 94 concentric with respect to the center of rotation 72 and is housed in a hollow sphere thrust block 96 which is also concentric with respect to the center of rotation (see FIG. 2). Therefore, this compensation element can rotate in all directions. Since the compensation elements housed in the hollow sphere thrusters are in most cases smaller than hemispheres, the center of rotation 72 is most often located within the sliding body, as is apparent from the invention. besides figures 1

and 2.

  The fact that the compensating element has a cap-like shell shape allows the use of the coupling according to the present invention, also in the case where the shaft 70 of the coupling connected to the transmission shaft forms an angle with the axis 70 of the coupling connected to the output shaft. The capacity

  pivoting compensating elements compensates for such

angle.

  In accordance with FIGS. 1 and 2, the planar oblique surfaces of the half-couplings 12 and 14 are arranged on pivotable compensating elements which are housed in hollow sphere thrusters 96 of the V-shaped surfaces. elements of compensation are shown schematically in Figures 3 and 4 similar to Figure 2, but showing only the area around the body of

sliding. 42.

  It is therefore possible to arrange sliding surfaces

  planes of the three sliding bodies on compensating elements

  are able to rotate and are themselves housed in craters

  hollow sphere paudines lying in the sliding body.

  FIG. 3 shows such an example embodiment in which the

  compensating elements 74, 78 held in the slide body

  42, are found in hollow spherical crapaudines. In

  this case, the flat oblique surfaces 16 and 24 corre-

  Half-couplings 12 and 14 are arranged directly on the coupling halves 12, 14. In this case, it is not necessary to give the sliding bodies 42, 44, 46 a shape of

  slip key having a triangular cross-section.

  The shape of the sliding body can be variable and it is important

  only that the compensating elements of the gliding bodies

  be kept in the correct position. In most cases, however, a key shape will be attributed to the body

  slip because it is the easiest to do.

  Figure 4 shows another possibility. Contrary to the realization that we have just described and which is illustrated in figure 3, in the present case, the plane oblique surfaces

  16, 24, half couplings are arranged on other elements.

  274 and 282. As is clear from

  4, these compensating elements 274, 282 are also hemispherical and house, while being able to pivot, in the trunnions of the half-couplings. The illustrated layout

  in Figure 4 provides greater ease of pivoting.

  When the coupling represented by FIG. 1 transmits a rotational torque of the front half coupling 12 to the half

  rear coupling 14, the three sliding bodies 42, 44 and 46 are compressed radially outwards against the ring of

  blocking 98 lying outside. This leads to deformity

  non-spherical locking ring 98, as is apparent

  of Figure 5. The adjacent surfaces of the three bodies of

  42, 44 and 46 on the locking ring 98 (shown in section and without guide beads 99, 101) correspond to the bearings 50 with radial elastic effect. According to Figure 5,

  the three sliding bodies 42, 44 and 46 are radially compressed

  outwardly against this radial elastic suspension due to the non-spherical deformation of the locking ring 98 and their sliding sliding surfaces slide on the surfaces.

  oblique planes adjacent to the two half-couplings.

  Fig. 6 shows a section along the line VI-VI of Fig. 5 which essentially resembles Fig. 2. The difference is characterized by the fact that, as shown in Fig. 6, the planar sliding surfaces 52 and 54 of the body of

  sliding 42 compressed radially outward have

  counter surfaces respectively 312 and 112. In this

  working position, the sliding body 42 abuts by me

  before its planar sliding surface 52, the oblique surface

  16 of the compensating element 74 of the front coupling half 12 while the rear half of its sliding surface

  plane 54 adjoins the flat oblique surface 24 of the

  The two halves of the planar sliding surfaces 52 and 54 are offset so that the sliding bodies act by shearing. We have already mentioned that the circular guide beads 99,

  101 have been provided on the locking ring 98 to prevent

  the three sliding bodies between the half-housings

  plements. For this purpose, the front faces 73 of the sliding bodies are directed on the guide surfaces 103, 105 (see FIG.

Figure 2).

  The locking ring 98 deforms elastically until

  that it touches the coupling discs in the three intervals

  between the three sliding bodies. Rotational torque can be applied while this positioning takes place when adjustable or spring loaded stops are provided between the three sliding bodies. As can be seen in FIGS. 1 and 5, these adjustable stops are in the form of radial screws 127, 128, 130 or (see top right quarter in FIG. 1) in the form of bolts 132 lying on the periphery of FIG. at least one half-coupling and these bolts 132 are subjected to a force

  radially outwards by means of springs 205. It is possible to obtain

  the damping effect of the elastic coupling of shafts according to the present invention by the adjustment of these screws and by a judicious choice of springs and this before inserting the ring of

  blocking 98. The choice of the modulus of elasticity of the ring of

  cage 98 can also act alone, or in addition, on the characteristic

  depreciation rate. It goes without saying that for a given coupling, only one kind of stop will be used, ie

  either screws 127, 128 130 or bolts 132 provided with springs.

  When comparing Figures 1 and 5, we see that the

  elastic deformation of the locking ring 98 allows a

  geometry of the three sliding bodies 42, 44 and 46. For illustrating

  trer the rotational movements of the compensation elements occurring during this radial shift of a sliding body, we have greatly enlarged, in Figure 7, the detail VII of Figures 1 and 5 and the section VII-VII of Figure 6. The solid lines refer to the rest position of Figure 1 and the dashed lines refer to the working position of Figure 5. On the other hand, in the right half of Figure 7,

  along the cut-off line 140, a part of the half-coupler

  before 12 was flayed. For this reason, we do not see

  a small fraction of the counter-surface 112 of the half-coupling

  before 12; the extension line characterizes the V-shaped surface 311 of the V-shaped recess of the rear half-coupling 14. In this V-shaped surface 311 is provided the hollow sphere truss 96 in which the compensating element 82 is housed.

  having the shape of a shell cap and pivotable.

  The V-shaped surface 111 of the front half-coupling 12 shows the hollow-sphere gear 96 in which the gear element 96 is housed.

  compensation 74 so as to be able to pivot.

  V-shaped surfaces 111 and 311 in which a compensating element 74 and 84 are respectively pivotable

together make an angle a.

* The sliding sliding surfaces 52 and 54 of the sliding body

  42 in the form of key together make the same angle a as the V-shaped surfaces 111 and 311 of the half-couplings 12 and 14. In the fully developed position of Figure 7, which corresponds to the rest position shown in FIG. 1

  flat oblique surfaces 16 and 24 of the compensating elements

  74 and 82 thus form this angle a.

  As already mentioned, when a rotational torque is applied to the elastic coupling of shafts according to the invention, the sliding body 42 is compressed radially outwards and opposes the force resilient of the outer locking ring 98 which is not shown in Figure 7. This body 42 is characterized in this position by dashes in Figure 7. This working position, as well as the rest position shown in FIG. solid line, is symmetrical to the radial plane 134 although, when the torque is applied, this radial plane has already made a rotational movement which

  can correspond to several rotations around the axis of accou-

  plement. The representation illustrated in FIG. 7 becomes clearer, since the rest position and the working position are indicated symmetrically to a single radial plane 134 situated perpendicular to the plane of the figure and presenting itself

  in the form of a line in phantom.

  After being subjected to a couple of rotations, the surfaces

  these flat slip 52 and 54 always form an angle α, since the sliding body 42 is dimensionally stable. As the sliding body 42 retains its symmetrical position relative to the radial plane 134, a rotation in opposite directions of the two half-couplings, at an angle i produces: 1. a rotation of the V-shaped surface 111 of the front half-coupling 12 of an angle p / 2; 2. a rotation of the V-shaped surface 311 of the half-coupling

rear 14 of an angle i / 2.

  These two angles of rotation p / 2 are indicated on the right and on the left. Since this is rotation, the V-shaped surfaces

  111 and 311 are not shifted in parallel but

  relative rotation so that the angle they form decreases from a to a -. This angle a - * is represented in

top of Figure 7.

  If the planar sliding surfaces 52 and 54 (according to the present state of the art) directly touched the V-shaped surfaces

  111 and 311, these flat sliding surfaces 52 and 54 do not

  would not see their adjacent positioning against V-shaped surfaces 111 and 311 when rotating the two half-couplings by an angle α. According to this invention, the compensating elements 74

  and 82 are provided for this purpose as they rotate in the cheeks

  hollow sphere 96 so that, for any position of the sliding body 42, their planar oblique surfaces 16 and 24 are in full contact with the

  plane sliding 52 and 54 of this sliding body. In the example

  embodiment described here, planar oblique surfaces 16 and

24 rotate by an angle p / 2.

  Figure 7 shows the case where the two elements of com-

  The center of rotation 72 is located exactly in the planar sliding surface respectively 52 and 54. In general, however, it is preferable to manufacture the compensation elements in planar and therefore non-hemispheric form. such that the centers of rotation 72 are within the body of

slip 42.

  The two half-couplings 12, 14 may carry surfaces

  these so-called radial radials 133, 135 located face to face which extend inwardly radially and axially in opposite directions by

  V-shaped surfaces and / or counter surfaces. When these two surfaces

  these radials are adjacent, the maximum angle of rotation p is

  achieved. Under the action of a higher torque, the ac-

  coupling therefore takes on a stiff and non-elastic character without

16 2459405

  however there is danger of damage or overload.

  An exemplary embodiment of such a limitation of the angle of rotation 4 is shown in FIG. 8 which shows a section along the section line VIII-VIII of FIG. 1. An axial projection 240 having the radial surface 133 is shaped. on the front coupling half 12. This projection 240 engages in a cavity 242 having the radial surface 135 and which is located in the rear half-coupling 14. The arrangement is such that for a coupling at rest, the two radial surfaces 133, 135 are located, apart, face to face. In the case of a

  during a reverse rotation of the two halves

  couplings, the two radial surfaces 133, 135 are approaching

  and touch with a maximum angle of rotation 4 max. The accou-

  now has a stiff character, the surfaces

  radial members 133, 135 limiting the elastic range of the coupling.

  If appropriate, the projection 240 may be formed by a bolt

  screwed and the cavity 242 may be due to a borehole. He is also

  It is preferable that several radial surfaces 133, 135 are

distributed on the periphery.

  At the radial offset of the slide body 42 shown in FIG. 7, the inner tip 142 of the sliding body 42 moves from the radius r1 to the radius r2. The width of the annular slot 122 of inner diameter "a", located between the perimeter 144, 146 of the coupling discs, and the locking ring 98 not shown, changes as a function of the difference r2 - r1 = Ar. near the sliding body 42, the width of the annular slot 122 increases by this value Ar, while a decrease in the width of the annular slot at the three intermediate points of the perimeter 144, 146. The screws 127, 128 and 130 or bolts 132 of Figures 1 and 5 are adjusted

  so that the damping benchmark of the accu-

  very much takes the desired pace; from the moment when the locking ring 98 touches the stops 127, 128, 130, this line of

  landmark becomes sharper (see Figure 5).

  FIGS. 9 to 12 show an elastic coupling of

  In accordance with the present invention, which is a claw coupling, it differs from that shown in FIGS. 1 to 5. FIG. 9 shows a view corresponding to FIG. 1, more specifically a longitudinal section along line IX-IX through FIG. Figure 10 is a view in the X direction of the object of Figure 9, the upper half of the locking ring 98 not being shown. On the other hand, FIG. 11 schematically shows the section XI-XI of FIG. 10 and FIG. 12 shows a development of the view XII-XII. In FIG. 10, elastic sealing joints 124, 126 are available.

  between the locking ring 98 and the half-couplings.

  It can be deduced from FIG. 9 as well as from the development represented by FIG. 12 that the rear half-coupling 14 has three claws distributed at equal angles 166 (not shown in FIG. 12), 168 and 180 which protrude vertically at

  plane of the half-coupling 14 and almost touch the half-hinge

  before 12. This coupling half 12 also has three

  claws 170, 172 and 174 distributed at equal angles projecting vertically

  at the front half-coupling 12 and almost touching the rear half-coupling 14. The facing surfaces a) of the claws 172, 180 b) of the claws 174, 166 as well as c) of the claws 170, 168 correspond to the V-shaped surfaces 111, 113, 115 and 311 described and illustrated in FIGS. 1 to 8 and comprise compensating elements that can pivot about a center of rotation and

  which are located in hollow spherical crapaudines. These

  The compensating elements comprise planar oblique surfaces which, similarly to those shown in FIGS. 1 to 8, are adjacent to plane sliding surfaces of the sliding bodies 42, 44 and 46. The sliding bodies are

  wedge shape having a triangular cross-section.

  As for the coupling illustrated in FIGS. 1 to 8, a rotation torque has the effect that the sliding bodies 42, 44 and 46 are shifted outwards. However, in this case, shear forces do not act on the sliding bodies 42, 44 and 46, since the V-shaped surfaces of the

  claws turned towards each other, and who carry the claws

  hollow sphere, lie directly opposite each other and support the flat sliding surfaces of

  sliding body in all their axial length. Transformation

  of the elastic coupling of trees, according to this invention.

  tion, to form a claw coupling, has the effect that

  the use of guide beads 99, 101 located on the

  The blocking water 98 becomes superfluous and, on the other hand, it allows the transmission of particularly high torques of rotation since compensation elements can be used.

  with larger sliding surfaces.

  The compensating elements of FIGS. 9 to 12 are cap-like caps, as is also quite clear from FIG. 11. It also shows a sliding body 42 having two planar sliding surfaces 52 and 54. these two planar sliding surfaces are the plane oblique surfaces 16 and 24 of the compensating elements 74 and 82 having the shape of a shell in cap and which house, so as to be able to pivot, in hollow sphere thrust bearings 96 of

claws 172 and 180.

  To be able to represent, in FIG. 11, separately the sliding surfaces 52 and 54 on the one hand and the flat oblique surfaces 16 and 24 on the other hand, we slightly shifted the sliding body 42 radially outwards. it is obvious that such an arrangement never appears during the actual operation of the coupling since the locking ring 98 always compresses the sliding body

radially inward.

  According to FIGS. 9 to 12, the claw coupling is characterized in a conventional manner by the fact that the angle-shaped claws are welded or screwed by their longer side to the corresponding coupling disk and that they mesh with each other. their shortest side in the gap between the half-couplings. In the case of the construction illustrated by

  Figures 13 and 14, the long side is superfluous.

  Figure 13 shows a view of the rear half coupling 14 in the axial direction from the drive shaft to the output shaft. The corresponding front half coupling is compliant

to the rear half coupling 14.

  As can be seen in FIG. 13, axially arranged slots 194, 196, 197 and 198 are distributed at equal angles on the coupling half 14.

  sunk in these slots. These driving elements have a

  similar to the claws of the claw coupling illustrated in Figures 9 to 12; the orientation of the slots 194, 196, 197 and 198 is thus determined. After the introduction of

  elements to be inserted into the corresponding slots, it is

  This lock is caused by stop screws 204 disposed in boreholes which extend from the inside of the coupling half 14 to the slot. The driving elements 200 comprise the compensating elements having the shape of a shell in cap and which are housed in the hollow sphere thrust bearings, as is the case for the claws of the claw coupling illustrated in FIGS. to 12. The advantage of the provision according to the

  FIGS. 13 and 14 with respect to the claw coupling

  FIGS. 9 to 12 are characterized by a simpler design and an easier method of manufacture. The parts behind the cutting plane are not shown in the figure

  14. The elements to be inserted have a rectangular shape.

  Figure 15 illustrates a section made through another

  coupling according to this invention, and which differs

  characterized by the fact that it comprises four sliding bodies instead of three. The section corresponds to the section line XV-XV of Figure 16. Figure 16 illustrates the XVI-XVI section made through

the object of figure 15.

  On the other hand, Figure 17 illustrates a similar development

  ble to that of Figure 12; nevertheless the development of the

  figure 17 extends over the entire perimeter of the two half

  couplings without however representing the outer locking ring 98. In this case, the length of development is

not to scale.

  FIGS. 15, 16 and 17 illustrate a coupling with grif-

  in a position where no torque produces a

  reverse rotation of the half-couplings.

  FIG. 18 shows a section corresponding to FIG. 15 illustrating an opposite rotation of the half-couplings of an angle

rotation t.

  In FIG. 15, the indication XVIIA-XVIIB shows that the lower half of FIG. 17 corresponds to the left-hand part of the perimeter of FIG. 15 and that the upper half of FIG. 17 corresponds to the right-hand part of the perimeter of FIG. 15. The arrangement of an even number of sliding bodies makes it possible to alternately place two plane oblique surfaces on a claw of one of the half-couplings and two oblique planar surfaces on a claw of the other half-coupling while the arrangement according to Figures 9 to 12 allowed to place alternately a plane oblique surface on a claw of one of the half-couplings and an oblique surface flat on a claw of the other half-coupling. According to FIG. 17, the two claws 166, 168 are

  arranged on the rear half-coupling 14, and the two grif-

  178, 180 on the front coupling half 12. This arrangement has been made in such a way that between the claws: 1) 166 and 180 is the sliding body 42, 2) 180 and 168 is the sliding body 48, 3) 168 and 178 is the sliding body 46, 4) 178 and 166 is the sliding body 44 (see fig.

and 17).

  When a rotating torque acts on the transmission shaft

  therefore, on the front half-coupling 12, the two half-couplings 12 and 14 rotate in opposite directions towards the arrows 220 and 222 indicated in FIG. 17. This has the effect of: 1) bringing the claws 166 and 180 closer together, 2) a widening of the gap between the claws 180 and 168, 3) a reconciliation of the claws 168 and 178 and 4) a widening of the gap between the claws 178 and 166. The effects of such approximations and of such spacings between the four claws, on the four sliding bodies are illustrated in Figure 18: a) The sliding bodies 42 and 46 located diametrically facing each other are displaced radially outwardly causing

  thus a non-spherical deformation of the locking ring 98.

  b) The locking ring, taking a non-spherical shape, then compresses, radially inwards, the other two

  sliding body 44 and 48 facing each other; it is the

  the gap between the corresponding claws which

  puts this radial displacement inwards.

  The claw couplings illustrated in FIGS. 1 to 9 produce a damping effect only in a direction of

  while in the other direction of rotation, they remain

  are fixed and non-elastic. The construction illustrated in FIGS. 15 to 18 is characterized by a damping effect in both directions of rotation since other sliding bodies (44 and 48 in FIG. 18) can be moved accordingly radially towards the center of the housing. inside, are disposed on the locations of the locking ring 98 which are located between two sliding bodies (42 and 46 in Fig. 18) exerting pressure towards the outside and moving accordingly.

  radially inward. In this way, in all

  the two sliding bodies (42 and 46 in FIG. 18) moving outwards on the one hand and that of the two sliding bodies (44 and 48 in FIG. on the other hand, the locking ring is fixed

safe and without play

  The reversal of the direction of the arrows 220 and 222 (FIG. 17)

  corresponds to the inversion of the direction of the torque.

  The two sliding bodies 44 and 48 are then radia-

  outwardly while the other two bodies of

  42 and 46 are compressed radially inward accordingly. Since the coupling illustrated in FIGS. 15 to 18 has no clearance, this inversion of the rotation torque takes place without producing a "jerk of speed".

  to say, without the sliding surfaces separating from

  these obliques. As is more particularly apparent from FIG. 17, the claws in this example are paired in the form of projecting half-couplings. However, one can also give an angular shape to the claws, as appears in Figures 9 to 12. The sliding bodies are then in the form of keys, cross-section

  triangular, and are distributed, at equal angles, on the perimeter.

  During the non-spherical deformation of the locking ring, due to the sliding bodies moved outwards (Fig.1 and 5: sliding body 42, 44 and 46; Fig.15 and 18: sliding body 42 and 46), the radius of curvature of the locking ring 98 decreases at locations where the sliding bodies internally exert pressure thereon. If the radius of curvature of the outer ajacent surfaces 182, 184, 186 and 187 of the sliding bodies 42, 48, 46 and 44 of FIG. 15 corresponds to the radius of curvature of the locking ring 98 in the rest position, these adjacent surfaces of the sliding bodies, in working position, are adjacent to the locking ring only in two lateral regions; it then forms a hollow in the middle of

22 2459405

  sliding body between the locking ring 98 and the sliding body. There is the danger that a high surface pressure is exerted between the edges of the adjacent surfaces of the sliding bodies and the locking ring, which can produce a wear effect. In the case of the claw coupling illustrated by the

  Figures 15 to 18 o only two sliding bodies are moved

  radially outwardly, the change in the radius of curvature of the locking ring 98 at the places where the pressure is exerted is much greater than in the case of the embodiments previously described and having three places where the pressure occurs. For this reason, in the exemplary embodiments illustrated in FIGS. 15 to 18 alone, the radii of curvature of the adjacent surfaces 182, 184, 186, 187 have been chosen so that in the working position, given by FIG. 18 (given rotation angle *) and at the compression locations, the radii of curvature of the adjacent surfaces of the sliding bodies 42 and 46 are in agreement

  perfect with the radius of curvature of the locking ring 98.

  Thus, at these compression locations where the strongest radial forces are exerted, contact is ensured between adjacent surfaces 182, 186 and the inner surface of the ring.

  blocking surfaces which have an identical radius of curvature

  only in the case of a maxi.mal rotation angle ip. Even smaller then is the force transmitting surface located between the sliding bodies and the locking ring in the position of

  rest (fig.15) on the one hand and on the other hand in

  between the compression locations in which the sliding bodies 44 and 48 are arranged, in working position, adjacent to the locking ring 98 deformed in a plane manner. We can change the characteristic of the coupling in

  fixing on the claws of the screws projecting radially or

  lons with springs (see screws 127, 128, 130 and bolts 132 of

Figure 1).

  Figures 19 to 22 show the arrangement of two cages of

  needle bearing located between an oblique surface and an

sliding face.

  FIG. 19 represents only the sliding body 42 comprising the hollow sphere truss 96 in which

  are accommodated, so as to be able to pivot, the compensating elements

  74, 82 with the concentric rotating surfaces 94. FIG. 20 illustrates a view from above of the sliding body and

the plane sliding surface 54.

  According to FIG. 21, the plane sliding surface 54 of the compensation element 82 is located opposite the flat oblique surface 24. It also appears from FIG. 21 that these surfaces do not completely abut and that a cage to palliate needles 206 is placed between them. FIG. 22 illustrates a view of this needle bearing cage 206. It will be noted that the axes of each of the cylinders 224, 226, 228, 230 and 232 of the needle bearing cage 206 are situated in the plane of the sliding surfaces. and oblique surfaces lying face to face, and its oriented so that they are

  perpendicular to the direction of the axis 70 of the coupling.

  This arrangement of a needle bearing cage 206 is justified by

as follows:

  When the driveshaft and the output shaft, engres-

  Coupled by the present invention, have a greater angle shift, ie when the axes of the half-couplings are cut, the half-couplings are offset in the axial direction during rotation. This shift occurs between planar slip surfaces adjacent to planar oblique surfaces. Where appropriate, these offsets may correspond to

  to a few millimeters. Having, according to the present invention, a needle bearing cage between the sliding surfaces and the oblique surfaces, reduces the effects of force (longitudinal forces, transverse forces).

  on the shaft and facilitates the shifting of the half-couplings

relative to each other.

  If it is a question of compensating a radial shift of the trees to

  using a needle bearing cage placed between the surfaces

  these sliding and oblique surfaces, is rotated this needle bearing cage of 900 compared to the provision

  shown in Figure 22. It can then compensate for

  tree stages, one with respect to the other, that occur

  during the rotation and may also, where appropriate, facilitate

  the radial movement of the sliding bodies.

  The exemplary embodiments illustrated in FIGS. 1 to 22 show couplings where the interstices 34 widen.

  radially outwards and o the sliding bodies

  in the interstices are based on a locking ring 98

  outside. In the context of this invention, a provision

  pour is nevertheless possible, that is to say the interstices rise

  radially inwards and the sliding bodies located in the interstices are supported by a locking ring

  disposed within the coupling.

  An embodiment of such a coupling is shown in FIG.

23 to 25.

  As is more particularly apparent from the vertical section according to FIG. 23 (section line XXIII-XIII of FIG. 24) and from the horizontal section along the section line XXIV-XXIV, the front coupling half 12 has three claws 370, 372, 374

  distributed at equal distance on the perimeter of his

  coupling and which overflow axially leaving gaps between

  claws. The corresponding claws 366, 368, 380 of the half

  rear coupling 14 mesh in these voids. Zones, face

  face-to-face, force transmitters of the claws widen in

  radially inward recess, thereby forming the interstices 334, and have the plane oblique surfaces 316, 318, 320 of the front half-coupling 12 and the planar oblique surfaces 324,

  326, 328 of the rear coupling half 14, as shown elsewhere.

  Figure 23. However, these surfaces are

  do not extend to the perimeter 144, 146 of the half-acces-

  couplings but give on the radial surfaces 333 and 335

  arranged face to face with a peripheral deviation and which delimits

  try the modulus of elasticity of the coupling. The radial length

  the each of the radial surfaces 333, 335 is approximately

  1/3 or 1/5 of the radial thickness of the claws.

  As is also apparent from Figure 23, the claws are in the form of circular sectors. Each time, a vacuum 351 is then created radially between the regions of the claws which do not have oblique, empty surfaces the width of which corresponds approximately to the external distance

  between the radial surfaces 333 and 335.

  In the interstices 334 are the sliding bodies 342, 344 and 346 whose cross section may have a roughly triangular shape. The outer surfaces adjacent to each of these sliding bodies have crapaudines to

  hollow sphere 96 in which compensating elements

  74, 76, 78, 82, 84 and 86 being rotatable in all directions and having the shape of a shell shell or being, for example,

  hiémisphériques. The compensating elements 74, 76, 78 present

  then a planar sliding surface respectively 352, 356, 360 which abuts a planar oblique surface respectively 316, 318, 320. The compensation elements 82, 84, 86 oriented in the opposite peripheral direction have, each time, a sliding surface. respectively plane 354, 358, 362 which adjoins a planar oblique surface respectively 324, 326, 328. Thus the compensation elements protrude from the sliding bodies in such a way that it is excluded that the claws and

  the sliding bodies touch each other during the oscillating movement.

  the compensation elements.

  The locking ring 398 having the shape of an annular cylinder

  and being elastically deformable, is disposed inside the claws and is the radial suspension bearing for sliding bodies. The sliding bodies 342, 344 and 346 rest on the latter by one side of the triangle, the outer diameter of the locking ring 398 being chosen such that in the case of a coupling in the rest state, the sliding bodies are compressed in interstices 334 in such a way that the

  sliding surfaces are adjacent to oblique surfaces.

  In the case of a coupling in rest position, the r4 rays of the adjacent surfaces 182, 184, 186 through which

  the sliding bodies 342, 344, 346 abut the blocking ring

  ge 398 are greater than the outer radius r3 of the locking ring. It is only in the case of a coupling in working position that, in the field of sliding bodies, these

  radii r3, r4 coincide, the locking ring 398 being elastically

  distorted (see fig.25). In this way, it is possible that in the working state, the surface pressure between the ring of

  blocking and sliding bodies is weak.

  As clearly shown in Figure 25, the locking ring

  398 is axially disposed between the two drive disks.

couplement.

  In order to be able to adjust the damping characteristic of the present coupling, a radial screw 32, 328 and 330 are respectively provided on a claw respectively 366, 368 and 380 (and / or 370, 372, 374) in the space between the bodies. slip and near the gaps 351. These screws 327, 328, 330

2459405

  fit radially in the interior space of the coupling thus forming a stop for the locking ring during the elastic deformation of the latter. The setting of

  screw affects the characteristic of the coupling. Of course

  Instead of screws, bolts can also be used. When during operation, a torque is transmitted from the front coupling half 12 in the direction of the arrow 32 on the rear half coupling 14, the sliding bodies

  342, 344, 346 are compressed inwards against the resistance

  elastically of the locking ring 398 and the locking ring then deforms elastically (see Fig.26). It is then that the external distance between the claws 366 and 370, 368 and 372, 380 and 374 decreases while the external gap between the claws 370 and 368, 372 and 380, 374 and 366 increases, that is, that is, the two half-couplings rotate in opposite directions. This rotation can continue until the radial surfaces 333 and

  335 touch each other. At this point, the coupling becomes stiff.

  In this embodiment, the elements of

  thought are housed in sliding bodies and surfaces

  flat slip are found on the compensating elements

  tion. In this case, it is not necessary that the sliding bodies have a triangular profile. What is important is that each sliding body has a large enough surface adjacent to the locking ring and that it offers a sufficiently large housing possibility for the compensating elements in the form of a shell shell or being , for example hemispherical. For reasons of simplicity, a triangular profile is most often given to the sliding bodies. We can also arrange the compensation elements on

  the claws instead of placing them on the sliding bodies.

  The sliding bodies then comprise the sliding surfaces

  flat. It is also possible to make a provision

  in accordance with Figure 4 o not only the gliding bodies

  but also the claws have compensating elements.

  In the end, it is also possible to equip the

  plements designed according to Figures 1 to 22 of a locking ring located inside, provided however to change the shape

  interstices 34 in accordance with the previous designs.

  FIG. 25 illustrates another possibility of sealing the interior space of the coupling to prevent the penetration of dust and dirt on the sliding surfaces and the oblique surfaces. For this purpose, the two half-couplings 12, 14 are surrounded by a cylindrical bellows 246 of plastic material such as natural rubber or

  synthetic. At the ends of this cylindrical bellows are

  radially arranged flanges 248 which are fastened to the hub of the coupling by a clamp 250.

  sealing can also be applied to other couplings

previously described.

  As regards the dimensions of the following couplings

  the invention, the following indicative values should be applied:

  the size of the sliding surfaces and therefore the size of the hemispherical or shell-shaped shell elements are determined by the torque to be transmitted and the permissible surface pressure between the sliding surfaces and oblique surfaces. If sliding surfaces and oblique surfaces are made of hardened steel, a surface pressure of up to 10000 Kgf / cm 2 can be assumed. The thickness of the coupling discs and the axial length of the claws is chosen from so that one can have there the thrusters 96 for the accommodation of the compensating elements. This also applies when you want

  have compensating elements in the sliding bodies

  is lying. The cross sections of the sliding bodies should be chosen according to sufficient shear or pressure fastness. The number of sliding bodies depends on the use of the coupling. So, for example, in the case

  the realization of a compact coupling with trans-

  mission, we will use a maximum number of gliding bodies

  This also applies to couplings with compensa-

  be a large offset angle or offset trees.

  In the case of a coupling in the rest position, the opening angle of the gap between the oblique surfaces situated

  face-to-face of the two half-couplings must allow a movement

  radial position of the sliding body during a reverse rotation of the two half-couplings. The elasticity of the coupling can then depend on the choice of this opening angle. When the angle

  opening is small (about 300), the elasticity of the coupling

  is low, whereas in the case of a wide opening angle

  ture (about 1300) the elasticity is very high. Nevertheless, an average opening angle between 600 and 900 is sufficient to meet the usual requirements of

mechanical construction.

* It is preferable to manufacture the blocking rings

  steel construction with a wall strength which allows deformation

  elastic demand. If necessary, it is also possible to provide a locking ring composed of several

  rings- of different diameters. The children are then

  concentric, tight or flexible.

INDICATIVE REFERENCES.

  front and rear coupling half planar oblique surface (of 12) flat oblique surface (of 14) direction of force transmission gap sliding body radial spring bearing flat sliding surface coupling axis center of rotation front surface compensating element concentric surface of rotation hollow spherical ring locking ring guide bead direction of rotation drilling hollow guide surface V-shaped surface counter-surface annular slit gasket radial adjusting screw resilient bolt radial plane radial surface cutting line spike inner perimeter ridges resp. 12 and 14

16, 18, 20, 22, 316, 318

24, 26, 28, 30, 324, 326,

34, 334

42, 44, 46, 48, 342, 344,

52, 54, 56, 58, 60, 62,

64, 66, 352, 356, 360,

354, 358, 362

74, 76, 78, 80, 82, 84,

86, 88, 274, 282

98, 398

99, 101

resp.102 and 104

103, 105

111, 113, 115.311

112, 114, 116, 312

124, 126

127, 128, 130, 327, 328,

133, 135, 333, 335

144, 146

148, 150

  claws of 14 claws 12 adjoining surface double-arrow slit slit insertion element to depress stop screw suspension disc needle bearing housing arrow cylinder axial projection cavity bellows cylindrical flange vacuum clamp 166, 368,, 374, 182,, 194, 220, 224, 168, 172,

, 178, 366

174, 370, 372,

184, 186, 187

196

197, 198

226, 228, 230, 232

REV E N D I C A T I 0 N S

  1. Elastic coupling of shafts with half couplings

  (12, 14) carry at least two planar oblique surfaces (16, 18, 20, 22, 24, 26, 28, 30, 32, 31, 38, 32, 32, 32, 32, 32, 32) oriented in a direction transverse to the force transmission direction (32), coupling in which two oblique surfaces (16 and 24, 18 and 26, 20 and 28,22 and 30, 316 and 324, 318 and 326, 320 and 328) of one or the other half-coupling (12,14) are arranged in pairs facing each other and limit a radially opening gap (34, 334) in which at least one slip body (42, 44, 46, 38, 424, 344, 346) is housed in a spring-loaded bearing (50) radial, sliding body which meshes in the gap (34,334) and which carries two planar sliding surfaces (52,54,56,58,60,62,64,66,352,356,360,354,358,362) turning the back and o each plane oblique surfaces (16,18, 20,22,24,26,28,30, 316,318,320,324,326,328) adjoins a sliding surface (52,54,56,58,60, 62,64,66,352,356,360,354,358,362) CHARACTERIZED BY THE FACT THAT at least one of the flat surfaces, being intended for each other, of a gap (34, 334) is on a compensating element (74, 76, 78, 80, 84, 86, 88) having the shape of a shell in cap, itself housed so as to be able to pivot in all directions in a spherical hollow thrust (96), BY THE FACT that the number of interstices (34,334) in which is disposed each time a body (42,44,46,48,342,344,346), is between 2 and 12, and the slip bodies (42,44,46,342, 344,346) are compressed in the interstices intended for them (34, 334). by a

  locking ring (98,398) which, by its non-spherical deformability

  that, produces a radial effect of spring.

  2. elastic shaft coupling according to claim 1, CHARACTERIZED BY THE FACT THAT at least one radial abutment (127,128, 132,327,328,330) is disposed between two interstices (34,334)

  at least one half-coupling (12,14), thereby limiting the

formation of the locking ring.

  3. elastic shaft coupling according to claim 2, CHARACTERIZED BY THE FACT THAT the stop (127,128,130,327,328,330)

  is adjustable in a radial direction.

  4. elastic shaft coupling according to claim 2 or 3, CHARACTERIZED BY THE FACT THAT the stop (132) is elastic

in a radial direction.

  5. Elastic shaft coupling according to any one of

  claims 1, 2, 3 and 4, CHARACTERIZED BY THE FACT THAT

  even number of sliding bodies (42,44,46,48) is expected and that

  two adjacent oblique surfaces intended for sliding bodies

  are placed in the same coupling half. 6. Elastic shaft coupling according to any one of

  Claims 1 to 5, CHARACTERIZED BY THE FACT THAT the ring of

  blocking (98) surrounds the sliding bodies (42,44, 46, 48) and

  THAT the interstices (34) widen radially towards the ex-

TER AL.

  7. Elastic shaft coupling according to any one of

  Claims 1 to 5, CHARACTERIZED BY THE FACT THAT the ring of

  blocking (398) is surrounded by the sliding bodies (342, 344, 346) and that the interstices (334) widen radially

towards the inside.

  8. Elastic shaft coupling according to any one of

  Claims 1 to 7, CHARACTERIZED BY THE FACT THAT the elements

  of compensation (74,76,78,80,82,84,86,88) are housed in the half-couplings (12,14) and that the sliding bodies (42,

  44, 46, 46, 48) consist of keys which present the

  sliding faces (52,54,56,58,60,62,64,66).

  9. Elastic shaft coupling according to any one of

  Claims 1 to 7, CHARACTERIZED BY THE FACT THAT the elements

  compensation (74,76,78,80,82,84) are housed in the

  slip (42,342,344,346) and show the sliding surfaces

  (52,54,352,354,356,358,360,362).

  10. Elastic shaft coupling according to claim 9, CHARACTERIZED BY THE FACT THAT the oblique surfaces (16,24,

  316, 318,320,324,326,328) are directly on the half

couplings (12,14).

  The elastic shaft coupling according to claim 9, CHARACTERIZED BY the fact that the oblique surfaces (16, 24) are on other compensating elements (274, 282) having the

  form of a shell in cap which lodge in the half-couplings

ments (12,14).

BALCKE-DURR AKTIENGESELLSCHAFT

Vicarious

CABINET SCOPI.