DD151649A5 - ELASTIC SHAFT COUPLING - Google Patents

Abstract

Coupling halves (12, 14) comprise plane oblique surfaces (16 and 24), 18 and 26, 20 and 28) which delimit intermediate spaces (34) which open, in wedge-like formation, in the radial direction. Sliding elements (42, 44, 46) are arranged in the spaces (34) and comprise plane sliding surfaces (52, 54, 56, 58, 60, 62) lying with surface- to-surface contact on the oblique surfaces (16, 24, 18, 26, 20, 28) and held in contact by a surrounding, resiliently deformable holding ring (98). When torque is applied the coupling halves (12, 14) turn relative to each other, the intermediate spaces (34) become narrower, and press the sliding elements (42, 44, 46) outwards to deform the holding ring (98) to non-circular shape. The oblique surfaces and/or the sliding surfaces (52, 54, 56, 58, 60, 62) are arranged on hemispherical compensating elements (74, 76, 78, 82, 84, 86), mounted in bearing sockets (96) in the coupling halves (12, 14) and/or in the sliding elements (42, 44, 46) in such a way as to be pivotable in all directions to ensure that the associated surfaces remain in complete mutual contact when the opening angle of the spaces (34) is altered. <IMAGE>

Description

Applicant: Balcke-Dürr AG, 4030 Ratingen

Elastic shaft coupling

The invention relates to a flexible shaft coupling, the coupling halves each carry at least two oriented transversely to the force transmission direction flat inclined surfaces, wherein each two inclined surfaces of the one and the other coupling half facing each other in pairs and define a radially opening gap, wherein in a radial resilient bearing at least one sliding body is arranged, which engages in .Zwischenraum and carries two mutually remote planar sliding surfaces, each flat inclined surface bears against a sliding surface.

Such a flexible shaft coupling is proposed in German Offenlegungsschrift 27 42 442. In this elastic shaft coupling, the coupling halves are formed as externally toothed central wheels, which are surrounded by an internally toothed planetary gear. The plane inclined surfaces. The teeth of the central wheels are facing each other in pairs and define radially outwardly opening spaces. In these spaces, the wedge-shaped teeth of the planet gear engage.

transmits this elastic shaft coupling torques, so rotate the two coupling halves (central gears) relative to each other ^ Here, the spaces narrow and the engaging wedge-shaped teeth of the planet are pressed against an elastically inwardly urging spring force outward "This elastic force acting eeche _$ that can be realized in different ways _? the elasticity of the shaft coupling of the DB-OS 2742442 "Because dea sliding of the wedge-shaped teeth of the planet gear on the flanks of the interstices is this flexible shaft coupling ale ⁿ Gleitk @ ilkupplung designated"""

When the coupling halves (central gears) against each other \ xm twisted a certain angle of rotation, the Sohrägflächen be moved not parallel, but tilted to the same angle of twist "This entails that the two mutually facing oblique Plächen enclosed opening angle of the space around the The larger the angle of rotation, the smaller (sharper) is thus the opening angle · In the various constructions of DE-OS 2,742,442, the teeth of the planetary gear are adapted to this change in angle of the gap characterized in that the individual teeth of the Planet wheels are deformable in that they consist of flank parts which are hinged together at the Zahnspitae «Hereby a federation pushes anft the plank parts elastically auseinanderο Are the tooth flanks flat, the inclined and sliding surfaces are always exactly parallel j through the flat Plant kö high torques can be transmitted without impermissibly high surface pressures occurring,

To compensate for an inaccurate plush of the waves to be coupled in the constructions of DE-OS 2,742,442 provided the teeth of the planetary gear and / or the teeth of the central wheels perform crowned; the tooth flanks are not eberij in this case, so that the slanting

and sliding surfaces abut each other only in lines and the

  *

 transmissible torque is limited by the fact that a certain surface pressure must not be exceeded. Aim of the invention:

The invention has for its object to ensure in any operating condition of an elastic coupling that the abutting and sliding sliding and inclined surfaces are exactly parallel.

With respect to the compensation of a non-exact curse Tens of to be coupled WeIIe iS _n- understand this task in such a way that a convex profile of the inclined surfaces or sliding surfaces, which prevents surface contact should be avoided.

With regard to the problem of balancing the changing opening angle of the intermediate space, this is to be understood that the exact flat concerns despite "changing opening angle of the gap to be achieved without elastically Verfofmbare teeth of the type described above to use.

The problem underlying the invention can also be formulated to the effect that the proposed in German Patent Application 27 42 442 coupling is to be formed as all-metal coupling, in which in each operating state, the sliding and inclined surfaces are exactly parallel and lie flat against each other.

Moreover, the coupling should be simple in construction and therefore inexpensive to manufacture and their elasticity should be easily adapted to the particular application.

_ 4 -

This object is, starting from a clutch of the type described, according to the invention achieved in that at least one of the associated planar surfaces of an intermediate space is formed on a kugelkalottenförmigen compensating body, which is mounted on all sides pivotably in a hollow spherical bearing cup, that the number Interspaces, in each of which a sliding body is arranged, is 2 to 12 * and that the sliding bodies are pressed into their assigned intermediate spaces by a retaining ring, which is formed by non-round deformability radially resilient.

A "spherical cap-shaped compensating body" is to be understood as a body which

a) is pivotally mounted with a spherical cap surface in the hollow spherical bearing cup,

b) carries a flat surface (sliding surface or inclined surface) of the intermediate space.

By pivotable about a pivot bearing a sliding surface and / or an opposite inclined surface ensures that the pivotally mounted surface is always parallel to the other surface. Without the use of deformable teeth of the type described above, ie in particular with a completely inelastic, hard, metallic slider, inaccurate alignment of the waves and / or a change in the opening angle of the gap is compensated in this way.

By selecting a corresponding number of spaces or sliding bodies, the coupling can be easily adapted to the particular application.

The retaining ring is elastically deformed by the radially (outwardly or inwardly) pushing sliding bodies, whereby it is deformed (inwards or outwards) between the areas in which it bears against the sliding bodies.

Therefore, "the elasticity of the coupling can be influenced by the structural design of the elastically deformable retaining ring." If the wall thickness of the retaining ring is very small in relation to the diameter and thus the retaining ring is easily deformable, this means greater elasticity of the retaining ring

Fri.

Coupling to an embodiment with a retaining ring of greater wall thickness. In this case, the elasticity of the coupling can be additionally influenced by the opening angle derr spaces. With a small opening angle of the interspaces, for example 30 ° to 60 ° with an unloaded coupling, the radial force acting on the sliding body is lower for a given torque to be transmitted than for a larger opening angle. As a result, the influence of the elastic retaining ring on the elasticity of the coupling is lower than at a larger opening angle of the interstices.

Overall, therefore, the elastic shaft coupling according to the present invention fulfills the demands to be placed on such a coupling with respect to design, adaptability to given operating conditions, simple and secure transmission of torque and easy influencing of the torsional elasticity.

To the opening angle of the spaces is still to be noted that this must be at least so great that a good sliding of the sliding surfaces on the inclined surfaces is possible so that upon rotation of the coupling halves against each other, the friction of the abutting surfaces is overcome and a Radial movement of the slider is possible.

In order to be able to change the damping characteristic optionally also subsequently, at least one radial stop for the retaining ring, which is preferably adjustable or elastic in the radial direction, is advantageously arranged in each case between zv / ei adjacent intermediate spaces on the periphery of at least one coupling half.

r J? [«« Η

A particularly preferred development of the invention may consist in that an even number of sliding bodies is provided and that in each case two adjacent in the peripheral direction oblique surfaces, which are formed on different sliding bodies, are arranged on the same coupling half.

In this way, the elastic shaft coupling can be based on the principle of a dog clutch, which is elastic in both directions of rotation, · wherein the gaps between the individual jaws are formed.

In most applications, the retaining ring advantageously surrounds the sliding bodies, and the spaces expand radially outward. For couplings. circulating at high speed, .... It is recommended that the retaining ring surrounded by the sliding bodies, so it is internal and the spaces expand radially inward.

Another advantageous embodiment of the invention may consist in that the compensation body are mounted in the coupling halves and that the sliding bodies consist of sliding wedges which have the sliding surfaces. This embodiment is particularly intended for clutches that have a small torque to transmit, for example less than 100 kpm. Because in such couplings, the items are designed to be correspondingly small, and a sufficient storage possibility for the slider is usually possible only in the coupling halves.

However, if a coupling is provided for the transmission of larger torques, for example greater than 100 kpm, and thus the individual components have larger dimensions, then it is recommended that the balancing bodies in the sliding bodies

are stored and have the sliding surfaces.

With regard to the oblique surfaces, different embodiments are possible here. Is the offset of the waves to be coupled low, for example, at most 1/100 to 1/75 of the shaft diameter, and / or is the angular displacement of the waves

low> for example, not more than 2 °, it is sufficient in most cases, the inclined surfaces form directly on the coupling halves, when the compensation body are stored in the sliding bodies.

In other cases, where the aforementioned conditions are not met, the inclined surfaces are advantageously formed on v / eitaler kugelkalötefönnigen compensation bodies which are mounted in the coupling halves, i. Compensating bodies are mounted both in the sliding bodies and in the coupling halves. Further advantages and features as well as the mode of action of the various shaft couplings according to the invention are explained below with reference to the exemplary embodiments with reference to the drawings. It shows:

Ausführun ^ sbeisniele:

1 shows a view in the direction of the axis of a torque converter according to the invention, twisted by no torque,

2 shows the section II-II through the subject of FIG. 1,

3 and 4 different pivot bearings of compensation bodies in coupling halves and / or Gleitkör pe rn , _;

5 is a view in the direction of the axis, of the coupling of Fig. 1, the coupling halves are rotated by a torque load against each other, wherein the retaining ring is shown in section,

6 shows the section VI-VI through the subject matter of FIG. 5,

7 to explain the sequence of movements, the schematic representation of the section VII-VII through the subject of FIG. 6 and the details VII of FIGS. 1 and 5,

8 shows a section along the section line VIII-VIII through the subject matter of FIG. 1 _}

9 shows the view in the direction of the axis (section IX-IX through FIG. 10) of a further inventive _{r r} twisted by no torque and designed as a claw clutch coupling

10 is the top view X on the subject of FIG. 9, with cut retaining ring,

11 shows the section XI-XI through the subject of FIG. 10, wherein the sliding body is shown offset from the intermediate space, FIG.

FIG. 12 shows the two coupling halves of FIG. 9 in a view (unwound over the region XII-XII of FIG. 9) viewed radially from the outside, FIG.

13 is a view in the direction of the axis, of a coupling half, which carries four balancing body on special plug-in parts, which plug into slots of the coupling half,

14 shows the section XIV-XIV through the subject of FIG. 13, wherein parts lying behind the cutting plane are not shown, FIG.

15 shows a section through a coupling according to the invention _/ not twisted in torque, which is designed as a claw coupling with four intermediate spaces according to the section line XV-XV of FIG. 16.

_Q_

16 shows the section XVI-XVI through the subject of Fig. 15,

17, the entire developed view of the two coupling halves of FIG. 15, viewed radially from the outside, on a different scale,

18 is a section perpendicular to the axis, through the coupling of FIG. 15, the coupling halves are rotated by a torque load to each other, wherein the section according to the Schnittlinie XV-XV is guided,

19 to 22, the arrangement of a Nadelflachkäfigs between a sloping surface and a sliding surface,

23 is a variant of embodiment of the coupling according to the invention with internal retaining ring in section along the section line XXIII-XXIII of Figure 24 in the unloaded state.

FIG. 24 shows a section XXIV-XXIV through the coupling according to FIG. 23, FIG.

Fig. 25 is a longitudinal section along the section line XXV-XXV of Fig. 24 through the upper half of the coupling

and FIG. 26 shows a section through the coupling of FIG. 2 3 in the loaded state corresponding to the section line XXIII-XXIII

Fig. 1 shows a coupling according to the invention, the two halves of the hitch be twisted by no torque, so unloaded in view: -.

2 shows the section II-II through the subject matter of FIG. 1. In FIG. 2, the arrow I shows the direction in which FIG. 1 is seen.

Of the two coupling halves 12 and 14 shown in FIG. 2, the front coupling half 12 can be seen in FIG. This front coupling lurags half te 12 is provided with a central bore 102, whereas the rear coupling half 14 has a central bore 104. The bore 102 is provided for receiving a drive shaft, the bore 104 for the output shaft. The determination of the waves via feather keys. Each of the coupling halves has a circular clutch disc with a central hub.

The visible in Fig. 1 front coupling half 12 carries three angularly distributed over the circumference hollow spherical Lagerpfannenge, which are arranged in planes perpendicular to the plane of Fig. 1. In these three hollow spherical bearing pans 96

kugelk alottenf örmige, z.B

 three hemispherical compensating bodies 74, 76 and 78 are mounted. These three Auscjleichskörper each carry a flat inclined surface 16, 18 and 2O, These three planar Schr.äg surfaces extending transversely to K. Kraftübertragungsrichtung at an angle. In Fig. 2, the hollow spherical bearing cup 96 "of the compensation body 74 and its flat inclined surface 16 are in section in the front half of the coupling 12 recognizable. For simplicity. here is talk of "hemispherical" compensation bodies. However, these balancing bodies need not be exactly designed as "half" balls, as can be seen from the drawings. The Aususgleichskörper can also be smaller or, if necessary, larger than Haibkugelni is essential only that they

store with a spherical surface in the hollow spherical pan and therefore are allsexticr swivel. - ·

9P 13 8 6

Gleicherη same V7eise, but oppositely oriented, carries the rear coupling half 14 in hollow spherical bearing cups 96 balancing body 82, 84 and 86, each having an inclined surface. 24, 26 and 28, respectively. Between the inclined surfaces 16, 18, 20 of the front coupling half 12 and the inclined surfaces 24, 26, 28 of the rear coupling half 14, a respective sliding body 42, 44, 46 is arranged. This arrangement can be seen in particular from FIG. The sliding bodies extend in the axial direction over the two coupling halves 12, 14.

Respectively in pairs are shown in FIG. 1 opposite:

a) the flat inclined surfaces 16 and 24 of the balancing body

74 and 82, which are mounted in hollow spherical bearing cups 96 of the front coupling half 12 and the rear coupling half 14, so that the surfaces 16 and 24 offset from each other (see Fig. 2),

b) the flat inclined surfaces 18 and 26 of the balancing body 76 and 84, which are mounted in hollow spherical bearing cups 96 of the front coupling half 12 and the rear coupling half 14, as well as

c) the flat inclined surfaces 20 and 28 of the balancing body 78 and 86, which are mounted in hollow spherical position pans 96 of the front coupling half 12 and the rear coupling half 14.

In each case a flat oblique surface of the front coupling half 12 encloses a radially outwardly opening intermediate space 34 (see FIG. In each space a sliding body in the form of a sliding wedge 42, 44 and 46 is arranged. Each slider 42, 44 and 46 carries flat sliding surfaces 52, 54 and 56, 58 and 60, 62, each of a flat inclined surface of one of the six balancing body 74, 76, 78, 82, 84 and 86 abut , The cross-sections of Gleitkorp ">" are triangular.

- 12 - ^ g, <& I «3 w u

The three sliding bodies 42, 44 and 46 are held by a surrounding retaining ring 98 in the position shown and act similar to the elastic shaft coupling, - the aforementioned German Patent Application 27 42 442, as the teeth of a two central wheels (comparable to the coupling halves 12th and 14) surrounding planetary gear. The retaining ring 9 8 surrounds the coupling halves with a distance a, so that an annular gap 122 is formed.

If the front coupling half 12, which is rotationally fixed to the drive shaft, rotates in the direction of rotation 100, the flat inclined surfaces 16, 18 and 20 press against the flat sliding surfaces 52, 56 and 60 of the three sliding bodies 42, 44 and 46. A force component acts in this case in the radial direction outward on the slider. These are based on the outside of. Retaining ring 98 and transmit the torque on the flat inclined surfaces 24, 26, 28 of the three balancing body 82, 84 and 86, which are mounted in hollow spherical bearing cups 96 of the rear coupling half 14. In this transmission of a torque, the individual, substantially wedge-shaped sliding bodies 42, and 46 are subjected to pressure and shear. In order to prevent that they tilt at this shear stress between the two coupling halves, the retaining ring inside two circumferential guide beads 99, 101 on. The sliding bodies lie between the radially inwardly extending, mutually facing guide surfaces 103, 105 of the guide beads and can move in the circumferential direction, but not in the axial direction (see sliding body 46 in Fig. 2, left).

Each of the coupling halves 12, 14 has in its circular clutch disc on three V-shaped recesses, which are distributed uniformly on the periphery. The recesses are radially aligned and expand outward. These recesses are used for receiving the wedge-shaped sliding body 42, 44-, 46. For this purpose, each recess of the front coupling half of a V-surface 111, 113, 115 and a counter surface

112, 114, 116 limited; both surfaces intersect each other in the bottom of the recess. The rear coupling half 14 has. corresponding V-shaped recesses. In Fig. 2, the V-surface 311 and the counter surface 312 of the rear coupling half 14 can be seen. In each V ~ surface of the two coupling halves, one of the hollow spherical bearing cups 96 is arranged. Each of the mating surfaces 112, 114, 116, 312 is tuned in inclination to the inclination of the sliding surface of the associated slider. In the "unloaded position" of Fig. 1, in which the clutch is loaded by no torque, are the three sliding bodies 42, 44 and 46 with their two flat sliding surfaces 52, 54, 56, 58, 60, 62 at each of a flat inclined surface 16, 18, 20 and in each case a counter surface 112, 114, 116 of the front coupling half. The same applies to the rear coupling half 14 (see Fig. 2).

1 and 2 three hollow spherical bearing cups 9 6 are provided in each coupling half, in each of which a compensation body about a pivot point 72 (see Fig. 7) is rotatably mounted. The compensation body is in each case in the form of a spherical cap formed with a concentric to the fulcrum 72 rotational surface 94 which is mounted in a concentric to the pivot point hollow spherical bearing cup 96 (see Fig .. 2). The compensation body is therefore pivotable on all sides. Since the balancing bodies mounted in hollow-spherical bearing cups 96 are usually less high than hemispheres, the pivot point 72 is usually located inside the slider body 1, as shown in FIGS.

The design of the compensating body as a spherical cap allows the use of the coupling according to the invention even if the axis 70 of the coupling forms an angle in the region of the drive shaft with the axis 70 of the coupling in the region of the output. The pivoting in the compensation bodies allows the compensation of such an angular offset.

Referring to Figures' 1 and 2, the planar oblique faces of the coupling halves 12 and 14 are angeordnetg on rotatable balancing bodies which are mounted in hollow spherical bearing sockets 96 of the V ~ space "Other arrangements of balancing bodies are # 3 and 4 shown ₉ in FIGS which each »wils illustrations similar to Fig» 2 show ₉ in which, however, only the area around the slider 42 is shown *

Thereafter, it is possible ^ anzuord- the flat sliding surfaces of the three sliders on pivotable balancing bodies "SEN _g which are mounted in hollow spherical Lagerpfaanen _s which are arranged in the sliding body © FIG _e 3 shows such an embodiment ₉ wherein the compensating body held in the slide body 42 74 »82 the corresponding flat SGhräg surfaces sitsen in hollow spherical bearing cups _o 16 and 24 of the coupling halves 12 and 14 are in this case the coupling halves 12 ₉ 14 directly attached in this case, it is not erforderlichs the sliding bodies 42 _s 44 ₉ 46» 48 train in the form of sliding wedges triangular cross section _s the shape of the sliding body can be arbitrary, much is just * that the compensation body Vierden held by the sliding bodies in the correct position ₀ in most cases v ^ ill one but also the sliding bodies a wedge-like shape give _s as this is the simplest constructive Ausfü leadership is «

Another possibility is Fig _ft 4 * Compared with the above-described embodiment (Fig _e 3) here are the flat inclined surfaces l6 _s 24 of the two coupling halves 274 and 282 arranged on other compensation bodies "These compensation body 274 $ 282 are also approximately hemispherical in design and pivot arranged in bearing cups of the coupling halves ₉ as this is very clearly sue Fig. 4 su seen. The arrangement shown in Fig _e 4-shows the Vorteil.einer pivoting *

If the clutch shown in FIG. 1 transmits a torque from the front coupling half 12 to the rear coupling half 14 _S, then the three sliding bodies 42 j 44 and 46 pressed radially outwardly against the surrounding retaining ring 98 will cause a non-circular deformation of the retaining ring 98 _g as shown in Pig *, 5 The abutment surfaces of the three sliders 42 ₈ 44 and on the retaining ring 98 (which is shown in section and without Pühriralste 99g 101) act as radially resilient bearings 50 * Against this radial suspension on the non-circular Deformation of the retaining ring 98 is based _? are shown in FIG _e 5, the three sliding body 42 _s 44 and 46 pressed radially outward, • wherein their flat sliding surfaces on the voltage applied to them planar inclined planes of the two coupling halves ©

The sectional figure taken along the line VI-VI of Figo 5 shown in Figure "6 is substantially similar to Pig _e 2 _e One difference is _s that according to Pig, 6 ebe" nen (! Guide surfaces 52 and 54 radially outwardly pressed slider 42 In this loaded position, the sliding body 42 is in contact with the front half of a flat sliding surface 52 on the flat sloping surfaces 16 of the compensation body 74 of the front coupling half 12 on $, whereas the rear half These two acted halves of the planar sliding surfaces 42 and 54 are against each other so "offset that the sliding bodies are subjected to shear", has already been set forth _9th its flat sliding surface 5 $ on the flat inclined surfaces 24 of the balancing body 82 of the rear coupling half that circumferential guide beads 99 »101

- 16

2e% ³ S Ci fj, fi if \ M SiS j * .. € t »S * wf ifciP S ^

on the retaining ring 9 8 are provided to prevent tilting of the three Gleitkörper- between the coupling halves. For this purpose, the end faces 73 of the sliding bodies are guided on the guide surfaces 103, 105 (FIG. 2).

The retaining ring 98 deforms elastically until it rests against the clutch disks in the three areas between the three sliding bodies. The torque / at which this concern occurs _t . is adjustable, if between the three sliding bodies /! adjustable or spring-loaded stops are provided. 1 and 5, these adjustable stops are designed as radial screws 127, 128, 130 or (right upper quadrant of FIG. 1) as bolts 132, which are arranged on the circumference of at least one coupling half, wherein the bolts 132 by springs, For example, plate springs 205 are acted upon radially outward. The damping characteristic of the elastic shaft coupling according to the invention can be adjusted by adjusting the screws or by appropriate selection of the springs before the retaining ring 9 8 is pushed. Also, the damping characteristic can be additionally or solely influenced by the selection of the elasticity of the retaining ring 9 8. Of course, you will use only one type of attacks in a clutch, so either Schrsuben 127, 128, 130 or spring-loaded pin 132nd

Out. It can be seen from the comparison of FIGS. 1 and 5 that the elastic deformation of the retaining ring 98 permits a radial displacement of the three sliding bodies 42, 44 and 46. To explain the occurring during this radial displacement of a slider pivotal movements of the balancing body 7, the detail VII of Fig. 1 and 5 and the section VII-VII is shown by Fig. 6 greatly vergörßert. In this case, fully drawn lines refer to the unloaded position of FIG. 1 and dashed lines to the loaded position of Fig. 5. Furthermore, in the right half der.Fig. 7 a part of

front coupling half 12 along the break line 140 broken away · This is visible from the mating surface 112 of the front half of the coupling 12 only a short bit of sight bar? the subsequent line denotes the V-surface 311 of the V-shaped recess of the rear coupling half 14 "in this W surface 311 iat the hollow spherical bearing pan 96 is provided in which the spherical cap-shaped Auegleichskörper 82 is pivotally mounted.

The V «surface 111 of the front coupling half 12 has the hollow spherical bearing cup 96, in which the compensating body 74 is pivotally mounted

The VvFlächen 111 and 311 ₉ in each of which a compensating body is pivotally mounted _s close to each other an angle oO a «,

The planar sliding surfaces 52 and 54 of the wedge-shaped slider 42 close together the same angle _s the V-Pläohen 111 and 311 of the coupling halves 12 and 14 include «, In the fully sucked position of Fig * 7s corresponding to the loaded position of any torque Pig © 1, thus also include the flat inclined surfaces 16 and 24 of the balancing body 74 and 82 this angle vl> together ©

When Drehmomentbelastung.der elastic shaft coupling according to the invention, as already stated, the sliding body 42 against the elastic force of the surrounding retaining ring 98, not shown in Fig * 7 pressed radially outward «In this position it is shown in Pig _e 7 ge chained * This dashed loaded position, as well as the extended unloaded position, symmetrically a radial plane 134 drawn _f although this radial plane has already described during the application of torque a rotational movement that may amount to several revolutions around the Kupplangsachse «The representation of Ulg« 7 wins

- ie - ι d ι y ob

however, for clarity, when drawing the unloaded position and the loaded position symmetrically to a single radial plane 134, which is perpendicular to the plane and depicts itself as a line.

The planar sliding surfaces 52 and 54 close after applying a torque unchanged with each other the angle oC, since the slider 42 is undeformable in itself. Since the slider 42 maintains its symmetrical position to the radial plane 134, causes a rotation of the two coupling halves by the angle ψ against each other:

1.) a pivoting of the V-surface 111 of the front coupling half 12 by an angle

2.) a pivoting of the V-surface 311 of the rear coupling half 14 by y / 2.

These two swivel angles * -f / 2 are entered on the right and left. Since they are pivots, the V-faces 111 and 311 are not translated in parallel, but also pivoted in relation to each other, so that the angle included by them decreases from ei to eC- y> . This angle t * c ~ U> is entered in Fig. 7 above.

If the flat sliding surfaces 52 and 54 (according to the prior art) are directly adjacent to the V-surfaces 111 and 311, then the two coupling halves would not be flatly abutted by the angle jf of the planar sliding surfaces 52 and 54 on the V-surfaces 111 and 311 more given. For this reason, the compensation body 74 and 82 are provided according to the invention, which pivot in the hollow spherical bearing cups 96 such that their flat inclined surfaces 16 and 24 in each position of the slider 42 whose planar sliding surfaces 52 and 54 abut completely flat. In the illustrated embodiment, the flat inclined surfaces 16 and 24 at an angle

ψ / 2 panned.

In Fig. 7 the case is shown that the two balancing bodies are mounted in hochkugeligen bearing cups 96. In general, however, it will be preferable to make the compensating bodies flatter, ie not hemispherical, so that the pivots 72 come to rest within the slider 42.

The two coupling halves 12, 14 can support opposing radial surfaces 133, 135, which extend radially and inwardly against each other from V-surfaces and / or mating surfaces. When these radial surfaces abut each other, the maximum possible angle of rotation tp is reached. At even higher torque load, the clutch acts as a rigid, inelastic coupling without the risk of damage or overload.

An embodiment of such a limitation of the angle of rotation y is shown in Fig. 8, which shows a section along the section line VIII-VIII through Fig. 1. Thereafter, an axial projection 240 is disposed on the front KupplungshäLfte 12, which has the radial surface 133. This projection 240 engages a recess 242 which is mounted in the rear coupling half 14 and which has the radial surface 135. The arrangement is now made so that when unloaded clutch, the two radial surfaces 133, facing each other with distance. In the case of a load, that is, in a rotation of the two Kupplüngshälften against each other, approach the two radial surfaces 133, 135 and are at a maximum angle of rotation ty ⁷ max to each other. The coupling now acts as a rigid coupling, the radial surfaces 133, 135 limit the elasticity range of the coupling. The projection 240 may optionally be screwed by a

Bolt and the recess 242 be formed by a hole * Also, eo is advantageous if multiple radial surfaces 133? 135 are distributed around the circumference *

In the radial displacement of the slider 42 shown in FIG. 7, the inner tip 142 of the guide body 42 moves from the radius ri to the radius e. The difference a-r. ^ = Δr changes the width a of the ring epalt 122 between the outer periphery 144 ₉₁₄₆ of the clutch plates and the retaining ring 98 is not shown * in the area of the sliding body, the width "r gap 122 by this value a to, whereas the three intermediate points of the outer periphery 144 'takes a of the ring 146 a decrease in the Width a of the annular gap was made The screws 127, 128, 130 and Bolzen.132 of Figures 1 and 5 are set ₅ so that the damping characteristic of the Kupplungs'dem'gewünochten course receives ι from the moment on s in the retaining ring 98, the attacks 127, 128j 13Oj 132, this characteristic becomes steeper (forgive Fig. 5).

FIGS. 9 to 12 show an elastic shaft coupling according to the invention which differs from FIGS. 1 and 5 in that it is designed as a claw coupling.

Figure "9 is a view corresponding to FIG _e I ₉ precisely ge ~ sagti a section along the line IX-IX by the subject matter of the Fige 10" FIG _e 10 is a view in the direction X of the object of Figure "9 _S with the upper half of the retaining ring is omitted 98 shows * Further, FIG _e 11 schematically shows the section XI-XI through FIG _e 10 and _e 12 is a developed view XII-XIIc In Figure "10 are swisehen the retaining ring 98 and the Kupllungshälften resilient seals 124 _$ 126 arranged *

The development shown in FIG. 12 as well as FIG. 9 are removed _? that the rear half of the coupling 14 has three equi-angularly distributed claws 166 (Pig "12 unrecognizable").

· »21

bar) j, l68 and ISO, which protrude perpendicularly from the plane of the coupling half 14 and reach close to the front coupling half 12. This front coupling half 12 in turn carries three equally distributed claws UOp 172 and 174s which project perpendicularly from the front coupling half 12 and close to the rear coupling half 14 protrude® The facing surfaces

a) the claw 172, ISO

b) the claws 174 _S I66 and 0) of the claws 17O ₈ 168

correspond to the V-surfaces 111, 113, 115 and 311 discussed with reference to FIGS. 1 to 8 and carry in hollow-spherical bearing pans the compensating body pivotable about a pivot point. These compensating bodies carry flat oblique surfaces which act in the same way as in FIG 1 to 8 concern FIGS _e on flat (rleit-Fläohen the sliding body 42, 44 and 46 * are as sliding body sliding wedges formed with dreiecki'öriüigem cross-sectional "

As with the coupling of Figure _e 1 to 8 produces a torque that the sliding bodies are _f shifted 42 44 and 46 to the outside but © Here act on these sliding bodies 42, 44 and 46 no shearing forces, since the facing V-faces of the Claws, which have the hollow spherical bearing pans, face directly, and support the flat sliding surfaces of the sliding bodies over the entire axial extent. This design of the elastic shaft coupling according to the invention as a claw coupling thus makes the use of the guide groove te 99 101 on the retaining ring 98 superfluous and enables the transmission of particularly high torques ₉ since compensating bodies with larger sliding surfaces can be used _e

The balancing body of the FIg ₆ 9 to 12 are spherical caps, as can be seen particularly well in Fig _e 11 su «one recognizes

22

There, a slider 42 with its two flat sliding surfaces 52 and 54. Parallel to these two flat sliding surfaces are the flat inclined surfaces 16 and 24 of the spherical cap balancing body 74 and 82 which pivotable in hollow spherical bearing cups 96 of the jaws 172 and 180 are stored.

In order to be able to depict separately the sliding surfaces 52 and 54 on the one hand and the flat inclined surfaces 16 and 24 on the other hand, the sliding body 42 is shown slightly offset radially outwards in FIG. 11; in the actual operation of the clutch, such a position of course never occurs because the retaining ring 98 always pushes the slider radially inward.

9 to 12, the dog clutch is formed in a conventional manner, characterized in that the angular claws are welded or screwed with its long leg to the respective clutch disc and protrude with its short leg in the space zv / ischen the coupling halves. In the construction of Figs. 13 and 14, the long leg becomes unnecessary

Fig. 13 shows the view of a rear coupling half 14 in the axial direction, from the drive shaft in the direction of the output shaft. The associated front coupling half is formed corresponding to the rear coupling half 14.

According to FIG. 13, axially distributed slots 194, 196, 197 and 198 distributed in the same direction are provided in the coupling half 14. Inserted parts 200 are stuck in these slots. These insertion parts are similarly oriented as the claws of the claw coupling of FIGS. 9 to 12; the orientation of the slots 194, 196, 197 and 198 is thus determined. After inserting the plug-in parts in the associated slots can

- 23 - 24iyöÖ

a lock by means of locking screws 204 done, which are arranged in bores extending from the interior of the coupling half 14 to the slot. The plug-in parts carry the spherical cap-shaped in hollow-spherical bearing pans. The advantage of the arrangement of FIGS. 13 and 14 in relation to the jaw clutch of FIGS. 9 to 12 is the ease of manufacture and uncomplicated assembly. In Fig. 14 lying behind the cutting plane parts are not shown. The plug-in parts are cuboid.

Figure 15 ₀ shows a section through a further inventive jaw clutch in Fig. 9 claw coupling shown differs from that four sliding bodies are provided instead of only three sliders. The section is shown in FIG. 16 along section line XV-XV.

FIG. 16 shows the section XVI-XVI through the subject matter of FIG. 15. FIG.

Furthermore, Fig. 17 shows a similar development as in Fig. 12, but the development of Fig. 17 extends over the entire circumference of the two coupling halves, without showing the surrounding retaining ring 98. Here, the length of the transaction is not to scale.

Figures 15, 16 and 17 show the dog clutch in a position where no torque causes mutual rotation of the coupling halves.

Fig. 18 shows a Fig. 15 corresponding section with a rotation of the coupling halves by the angle of rotation tj> against each other.

, - 24 - d ζ ι a ob

Fig. 15 denotes, with the indication XVIIA-XVHB, the assignment of the lower half of Fig. 17 to the left peripheral part of Fig. 15 and the upper half of Fig. 17 to the right peripheral part of Fig. 15.

The arrangement of an even number of sliders makes it possible to alternately arrange two flat slanted surfaces on a claw of a coupling half and two-plane slanted surfaces on a claw of the other coupling half, whereas in the arrangement of Figs. 9 to 12 only possible was to arrange alternately a flat inclined surface on a claw of a coupling half and a flat inclined surface on a claw of the other coupling half.

Referring to FIG. 17, the two jaws 166, 168 on the rear coupling half 14 and the two jaws 178, 180 on the. front coupling half 12 attached. The arrangement is now made such that between the jaws

1) 166 and 180 the sliding body 42 is located,

2.) 180 and 168 the sliding body 48 is located,

3.) 168 and 178 the sliding body 46 is located,

4.) 178 and 166, the sliding body 44 is located (see Fig.15 and 17).

Acts on the drive shaft and thus on the front coupling half 12 a torque, so the two coupling halves 12 and 14 rotate against each other in the direction of the arrows 220 and 222 of FIG. 17. This causes:

1.) an approach of the claws 166 and 180th

2.) an increase in the distance between the jaws 180 and 168,

3.) An approximation of the claws 168 and 178 as well

4.) an increase in the distance between the jaws 178 and 16 6.

_25- <e <& r a υ q

The effects of these reductions or enlargements of the. Distances between the four jaws on the four sliders are shown in FIG. 18:

a) The diametrically opposite sliding bodies 42 and 46 are displaced radially outwards, wherein they deform the retaining ring 59 out of round.

b) The non-circularly deforming retaining ring pushes the two other opposing sliding bodies 44 and 48 radially inwardly; this inward radial displacement becomes possible by the increase in the distance of the associated jaws.

The jaw clutches shown in Figs. 1 and 9 act damping only in one direction of rotation, in contrast, rigid and inelastic in the other direction of rotation. The construction of FIGS. 15 to 18 has a damping effect in both directions of rotation, in that 9 additional sliding bodies (44) are disposed on the two radially outwardly moving points of the retaining ring between two outwardly pressing sliding bodies (42 and 46 in FIG And 48 in Fig. 18) are arranged, which can be moved according to radially inward. The retaining ring is thus in each position between the two outwardly moving sliding bodies (in Fig. 18, 42 and 46) on the one hand and the two inwardly moving sliding bodies (in Fig. 18, 44 and 48) on the other hand safely and backlash clamped.

If the direction of the arrows 220 and 222 (FIG. 17) is reversed, this means a reversal of the direction of the torque. The two sliding bodies 44 and 48 are then pressed radially outwards and accordingly the two other sliding bodies 42 and 46 are pressed radially inwards. Since the coupling of FIGS. 15 to 18 has no play, this reversal of the

'- 26 - 2 2 1986

Torque without the so-called "speed shock" occurs, i. without the sliding surfaces of the sloping surfaces stand out. As can be seen in particular from FIG. 17, the claws in the present example are each formed from pairwise protrusions of the coupling halves. However, it is also possible to form the claws angularly, as in FIGS. 9 to 12. The sliding bodies consist of sliding wedges with a triangular cross-section and are distributed at the circumference at the same angle.

In the case of the non-circular deformation of the retaining ring by the sliding outwardly pushed sliding bodies (in Figures 1 and 5: sliding bodies 42, 44 and 46; in Figures 15 and 18: sliding bodies 42 and 46) the radius of curvature of the retaining ring 98 in the pressure points, in which the sliding body press on him from the inside, reduced. If the radius of curvature of the outer contact surfaces 182, 184, 186 and 187 of the sliding bodies 42, 48, 46 and 44 of FIG. 15 coincides with the radius of curvature of the unloaded retaining ring 9 8, then these contact surfaces of the sliding bodies in the loaded position are only in two lateral edge regions on the retaining ring; in the middle of the slider is formed between the retaining ring 9 and the slider a cavity. This brings with it the danger that between the edges of the contact surfaces of the sliding body and the retaining ring, a high surface pressure occurs, which can lead to wear.

In the jaw clutch of FIGS. 15 to 18, in which only two sliding bodies are displaced radially outwards, the change in the radius of curvature of the retaining ring 98 in the pressure points is far more significant than in the previously described constructions which have three pressure points. For this reason, only in the embodiment of FIGS. 15 to 18 are the radii of curvature of the contact surfaces 182, 184, 186, 187 chosen such that in the loaded position shown in FIG. 18 (maximum predetermined angle of rotation w).

- 27 - 3 9 1 QP

in the pressure points, the contact surfaces of the contact surface n of the sliding bodies 42 and 46 largely coincide with the radius of curvature of the retaining ring 98 in the pressure points. In these pressure points, in which the greatest radial forces are transmitted, there is a surface contact between the contact surfaces 182, 186 and the inner surface of the retaining ring ensured, which have a matching radius of curvature in the case of the maximum Verarehwinkels © Correspondingly lower is the kraftubertr.agec.de surface between the sliders and the retaining ring on the one hand in the rest position (Fig, 15) and on the other hand in between where the sliders 44 and 48 deformed flat under load. Retaining ring 98 »

In order to be able to influence the characteristic of the coupling, it is possible to attach radially projecting screws or spring-loaded bolts to the claws (see "screws or bolts 127, 128, 130, 132 of FIG. 1)".

FIGS. 19 to 22 show the arrangement of two needle · "flat cages between one oblique surface and one sliding surface«,

19 shows only the sliding body 42 in whose hollow spherical bearing cups 96 with the concentric rotating surfaces 94 the compensating bodies 74, 82 are pivotably mounted. In FIG. 20 the sliding body and the plane sliding surface 54 are shown in plan view.

According to Figo 21 is the planar slide face 54 of the compensation body 82, the planar inclined surface 24 with respect to. "According to FIG _e 21, however, are those areas not directly adjacent to each other, but between them there is a needle retainer 206. _e In Fig. 22 this is needle cage 206 shown in plan One recognizes that the axes of the individual rollers 224 _? 226 _? 228 _f 230 and 232 of the ITadelkäfigs in the plane of the opposite

- 28 - £ -6 ϊ 3 öö

Sliding surfaces lie and are oriented so that they are perpendicular to the direction of the axis 70 of the clutch, this arrangement of a needle cage 206 has the following meaning:

If the drive shaft and the output shaft, which are interconnected by the coupling according to the invention, have a greater angular displacement, that is, when the axes of the coupling halves intersect, move during the circulation, the coupling halves in the axial direction to each other. This shift occurs between the abutting flat sliding surfaces and inclined surfaces. The shifts may be a few millimeters. The inventive arrangement of a needle cage between the sliding surfaces and inclined surfaces reduces the force effects (longitudinal forces, shear forces) on the shaft and facilitates the displacement of the coupling halves to each other.

If a radial offset of the shafts is to be compensated for by means of a needle cage arranged between the sliding and oblique surfaces, then this needle cage is rotated 90 ° relative to the arrangement of FIG. He can then radial displacements of the waves to each other, which occur during the circulation, compensate and possibly also facilitate the radial movement of the sliding body.

The embodiments described in FIGS. 1 to 22 show couplings in which the intermediate spaces 34 expand radially outwards and in which the sliding bodies arranged in the space are supported on an outer retaining ring 9 8. However, in the context of the inventive concept, a reverse arrangement is possible, i. the interspaces widen radially inwardly and the sliding bodies arranged in the interspaces are supported on a retaining ring arranged inside the coupling.

An embodiment of such a coupling is shown in Figs. 23 to 25.

As can be seen in particular from the vertical section according to FIG. 23 (section line XXIII-XXIII of FIG. 24) and the horizontal section according to the section line XXIV-XXIV, the front coupling half 12 has on its circular clutch disc three equally circumferentially distributed claws 370, 372, 374 projecting axially, leaving gaps between the jaws. In these gaps corresponding claws 366, 368, 380 of the rear coupling half 14 engage. Opposing force-transmitting portions of the jaws widen radially inwardly to form the spaces 334 and have the planar slanted surfaces 316, 318, 320 of the front coupling half 12 and the planar slanted surfaces 324, 326 and 328 of the rear coupling half 14 on, as can be seen very clearly from Fig. 23. However, these inclined surfaces do not extend to the outer periphery 144, 146 of the coupling halves, but go into radial surfaces 333 and 335, which face each other at a peripheral distance and which serve to limit the elasticity range of the coupling. The radial length of the radial surfaces 333, 335 is about 1/3 to 1/5 of the radial thickness of the claws respectively.

As can be seen further from Fig. 2 3, the claws are formed in the form of circular ring sectors. Here, between those portions of the jaws having no inclined surfaces, there is respectively disposed a radially extending gap 351 whose width is approximately equal to the peripheral distance of the radial surfaces 355.

In the intermediate spaces 334, the sliding body 342, 344 and 346 are arranged, whose cross-section may be formed approximately triangular. In peripherally adjacent surfaces of each of these sliding bodies each hollow spherical bearing cups 9 6 are provided,

O f \ βκ «» ί Vi # V ^ * &?

spherical cap-shaped, e.g.

in each of which ^v hemispherical compensation body 74, 76, 78, 82, 84, '86 are mounted on all sides pivotally. Here, the compensation body 74, 76, 78 each have a flat sliding surface 352, 356 and 360, which abuts in each case on a flat inclined surface 316, 318 and 320. The balancing bodies 82, 84, 86 oriented in peripherally opposite direction each have a flat sliding surface 354, 358 and 362, which bears against a flat oblique surface 324, 326 and 328, respectively. In this case, the compensation body protrude so far out of the sliding bodies, that during the pivoting movement of the compensation body, a contact between the jaws and the sliding bodies is excluded.

Within the claws of the elastically deformable, annular cylindrical retaining ring 398 is arranged and forms the radially resilient bearing for the sliding body. At this, the sliding body 342, 344 and 346 are based on a triangle side, wherein the outer diameter of the retaining ring 39 8 is selected so that when unloaded clutch, the sliding bodies are pressed into the spaces 33 ^ - that the sliding surfaces abut the sloping surfaces.

The radii r. The contact surfaces 182, 184, 186, with which the sliding body 342, 344, 346 abut the retaining ring 398 with unloaded clutch are each greater than üer ^v radius r ~ of the retaining ring. Agreement of these radii r. ~, R. is only available with a loaded coupling in the region of the sliding body, in which the retaining ring 398 is elastically deformed (compare Fig. 25). In this way it is achieved that the surface pressure between the retaining ring and sliding bodies in the loaded state is low.

The retaining ring 39 8 is guided in the axial direction between the two clutch plates, as can be clearly seen from Fig.'25.

In order to be able to adjust the damping characteristic of the present coupling, one respective radially extending screw 327, 328 or 330 on a respective claw 366, 368 or 380 (and / or 370, 372, 374) in the area between the sliding bodies in the vicinity of Gaps 351 arranged. These screws 327, 328, 330 protrude in the radial direction into the interior of the coupling and thus form a stop for the retaining ring in its elastic deformation. By adjusting the screws, the characteristics of the coupling can be influenced. Instead of the screws and spring-loaded bolts can be used.

If a torque is transmitted from the front coupling half 12 in the direction of arrow 32 to the rear coupling half 14 during operation, the sliding body 342, 344, 346 are pressed against the elastic resistance of the retaining ring 398 inwardly, wherein the retaining ring elastically deformed ( See Fig. 26). At this time, the peripheral distance between the claws 366 and 370 and 368 and 372 and 380 and 374 becomes smaller, whereas the peripheral distance between the claws 370 and 368 or 372 and 380 or 374 and 366 is increased, i.e. increased. the two coupling halves are twisted against each other. This rotation can continue until the radial surfaces 333 and 335 abut. The coupling is then djcehsteif .. .... .._., .... ·, · · · ..

22 198

In the present embodiment, the compensation body are mounted in the sliding bodies and the flat sliding surfaces are formed on the compensation bodies- In this case, it is not necessary that the sliding bodies each have a triangular-shaped profile. It is only essential that each slider has a sufficient contact surface on the retaining ring and a sufficient storage possibility for the hemispherical compensation body. For simplicity

you will usually form the slider with triangular profile.

  Instead of arranging the Aususgleichskörper in the sliders, they can also be provided in the claws. The sliding bodies are then provided with the flat sliding surfaces. Also, an arrangement as shown in Fig. 4 is possible in which both the sliders and the claws are provided with pouring bodies.

Finally, couplings having a construction according to FIGS. 1 to 22 can also be provided with an inner retaining ring, if the formation of the intermediate spaces 34 is modified in accordance with the above explanations.

In Fig. 25 is still shown a way how the interior of the coupling can be sealed to keep dust and dirt from the sliding surfaces and sloping surfaces. For this purpose, the two coupling halves 12, 14 of a ring-cylindrical bellows 246 of an elastic material, such as rubber or Kunststoff.umgeben. At the ends of this bellows has radially extending flanges 248, which are each secured by a clamping ring 2 50 to the hubs of the coupling. This type of seal can also be used in the other above-described couplings.

The dimensioning of the couplings according to the invention is subject to the following guide values: The size of the sliding surfaces and thus the size of the hemispherical compensating bodies is determined by

"" ball-kettled, e.g.

set the torque to be transmitted and the permissible surface pressure between the sliding surfaces and the inclined surfaces. If the sliding surfaces and the inclined surfaces are made of hardened steel, the surface pressure is up to

2 10 000 kgf / cm. allowed ,. -. The

Thickness of the clutch discs or the axial length of the claw is chosen so that the bearing cups 96 can be incorporated for the balancing body. The same applies to a storage of the balancing body in the sliders.

The cross sections of the sliding bodies are to be chosen so that sufficient shear strength or compressive strength is given. The number of sliding body is matched to the particular application of the coupling. So you will use the highest possible number of sliders for the construction of a compact coupling high transmission capacity; The same applies to couplings that have to compensate for a large angular misalignment or shaft misalignment.

The opening angle of the intermediate space between mutually associated oblique surfaces of the two coupling halves with unloaded coupling is to be chosen so that a radial movement of the slider is possible with a mutual rotation of the two coupling halves. This can be influenced by the choice of this opening angle, the elasticity of the coupling. At a small opening angle (about 30 °), the elasticity of the coupling is low, at a large opening angle (about 130 °), the elasticity is very large. For the usual requirements of mechanical engineering, a mean opening angle between 60 ° and 90 ° is sufficient.

The retaining rings are preferably made of steel with a wall thickness that allows the required elastic deformation. If necessary, a retaining ring can also be constructed of several rings with different diameters. For this purpose, the rings are concentric, fixed or loose, pushed together,

Claims (1)

Invent. ungsanspruch: le Elastic shaft coupling, the coupling halves (12, 14) each at least two transverse ssur power transmission direction (32) oriented planar inclined surfaces (16, 18, 20, 22 _S 24, 26 ₉ 28, 30, 316, 318, 320, 324 , 326, 328), wherein in each case two inclined surfaces (16 and 24 "18 and 26, and 28 _" 22 and 30, 316 and 324, 318 and 326, 320 and 328) of the one and the other coupling half (12, 14) facing each other in pairs and defining a radially opening gap (34, 334), wherein in a radially resilient bearing (50) at least one sliding body (42, 44, 46, 48 _? 342, 344, 346) is arranged, which in the intermediate space (34, 334) engages and two mutually facing planar sliding surfaces (52, 54, 56, 58, 60, 62, 64, 66, 352, 356, 360, 354, 358, 362) carries, wherein each plane inclined -Bläche (16, 18, 20, 22, 24, 26, 28, 30, 316, 318 _S 320, 324, 326 _S 328) on a sliding surface (52, % t 56, 58, 60, 62, 64, 66 _S 352, 356, 36Ο, 358, 362) is marked characterized in that at least one of the mutually associated flat surfaces of a gap (34, 334) on a kugelkalottenförmigen compensating body (74, 76, 78, 80, 82, 84, 86, 88) is formed in a hollow spherical bearing cup (96). Is mounted pivotably on all sides, that the number of intermediate spaces (34, 134), in each of which a sliding body (42, 44, 46, 48, 342, 344, 346) is arranged ^ 2 to 12 and that the sliding body (42, 44, 46, 342, 344, 346) are pressed into their trays "arranged intermediate spaces (34, 334) of a retaining ring (98, 398), which is formed by non-circular deformability radially resilient _e 2 * Elastic shaft coupling according to item 1, characterized in that between at least two intermediate spaces (34, 334) at least one coupling half (12, 14) at least one radial stop (127, 128 ₅ 130, 132, 327, 330) a-ngeor & net is _? which limits the deformation of the retaining ring 3® Elastic shaft coupling according to item 2, characterized in that »the stop (127, 128, 130, 327, 328, 330) is adjustable in the radial direction« 4c flexible shaft coupling according to Funct 2 or 3 »characterized • _p that the stop (132) in the radial direction is elastically" Elastic shaft coupling according to item 1 or below, characterized in that an even number of sliding bodies (42 _S 44, 46, 48) is provided and that in each case two adjacent oblique Plächen-associated with different sliding bodies, at the same Coupling half are arranged « Elastic shaft coupling according to one of the items 1 to 5, characterized in that the retaining ring (98) surrounds the sliding bodies (42 _S 44 $, 46, 48) and widen the gaps (34) radially outwards (Pig 22) _e 7e Elastic shaft coupling according to one of the items 1 to 5 $ characterized in that the retaining ring (398) of the sliding bodies (342 _S 344 346) is surrounded and the intermediate spaces (334) extend radially inwardly (Pig _ß 23 to 26K 8 «Elastic shaft coupling according to one of the items 1 to 7, characterized in that the compensation body (74, 76, 78, SO ₂ 82, 84, 86, 88) in the coupling halves (12, 14) are mounted * and that the sliding body (42, 44, .46, 48) consist of sliding wedge which the slide Plächen (52g 54 * .56, 58, _60? 62 _S 64, 66) (Figure "I, 2 and 5 to 22)" A flexible shaft coupling according to one of items 1 to 7, characterized _s that the compensating body (74 "76 ₉ 78 80 _g 82, 84) in the sliding bodies (42, 342, 344, 346) are mounted and the sliding surface η (52, 54 «352, j 354 * 35β _$ 360, 3β2) (Fig _e 3 and 22 feis 26) _β Elast »Elastic shaft coupling according to item 9» characterized in that the oblique projections (16, 24, 316, 318, 320, 324g 3265 328) are formed directly on the coupling halves (12, 14) _e Elastic shaft coupling according to item 9j> characterized in that the oblique faces (16, 24) are formed on many spherical cap-shaped compensating bodies (274 ₉ 282) which are mounted in the coupling halves (12, 14) (Pig * 4) «