EP0046778A1 - Hooke's coupling - Google Patents

Abstract

The constant velocity coupling allows the two shafts to be coupled to be articulated and, if necessary, to perform a radial and / or axial displacement. For this purpose, at least one intermediate member (22, 24) is arranged in a radial plane between the two coupling parts (10, 12) and is connected to them, at two diametrically opposed ends, by the intermediate guides (68 - 78) performing an essentially planetary movement. These guides are fixed on each side, in an articulated manner, to the two coupling pieces (10, 12) as well as to the intermediate member (22, 24) using pivots (40 to 64) extending axially, and are arranged aligned in the axial direction. In the event that two or more intermediate bodies (22, 24) are provided, they can be linked together by a central articulation (300, figure 8), movable in all directions, in order to allow their mutual centering.

Description

 Shaft coupling

The invention relates to a shaft coupling, which allows an articulation angle between the parts to be coupled, comprising: a first coupling half, a second coupling half, an intermediate link between the first and the second coupling half, a first link arrangement with movably articulated links which share the first coupling half connects the intermediate link, and a second link arrangement with links articulated on all sides, which connects the second coupling half to the intermediate link.

Such a shaft coupling is known, for example, from US Pat. No. 4,040,270, FIGS. 12 and 13.

In the known shaft coupling, three intermediate members are provided in the form of rings which are concentric and rotatably mounted on one another. Each of these rings has a single handlebar with the first one Coupling half and another, the first

Handlebar diametrically opposite handlebar connected to the second coupling half. The handlebar pairs assigned to the three intermediate links are in the rest position, i.e. when the two shafts to be coupled are aligned with each other, offset by 120 from each other. The handlebars are articulated on all sides via ball joints on the coupling halves or on the intermediate links. In another embodiment of the coupling according to US Pat. No. 4,040,270 (FIG. 14), the articulation, which is movable on all sides, takes place via rubber bodies.

The coupling according to US Pat. No. 4,040,270 permits a radial displacement of the shafts in a kinematically correct manner with angular transmission of the rotary movement from one shaft to the other. The articulated linkage of the handlebars also allows a kink angle between the axes of the shafts to be coupled.

In the known clutch, the torque is transmitted from one coupling half via a link, the ring and the other link arranged on the other side of the ring to the other coupling half. It is essential for the kinematics and torque transmission that three rings are rotatably mounted on one another. In practice, this requires a relatively complex storage.

Another known shaft coupling with an intermediate member, which is connected to the drive-side and the output-side coupling half via a link arrangement, is the subject of FR-PS 1 475 431. In this known shaft coupling, each link arrangement consists of three links offset by 120 ° from each other. The coupling half on the drive side is a pot-shaped body, on the edge of which there are three Handlebars of a handlebar arrangement are articulated. The intermediate link is a ring that sits inside the pot-shaped body and is connected to it via the handlebars. The handlebars extend essentially in the circumferential direction. They are articulated on all sides with rubber pads. The ring forming the intermediate member is also connected to the disk-shaped, inside the ring arranged output-side coupling half via three to 120 against each other, essentially extending in the circumferential direction handlebar.

This known coupling does not allow radial misalignment. The transmission of a rotary movement at a kink angle between the input-side and output-side revolving axis is only approximately homokinetic.

The invention has for its object to provide a structurally simple shaft coupling which allows a kink angle between the axes of rotation of the parts to be coupled in a kinematically perfect manner with homokinetic transmission of the rotary movement.

According to the invention this object is achieved in that

(a) the first link arrangement is formed by a pair of diametrically opposed links,

(b) the second link arrangement is formed by a pair of diametrically opposed links and (c) one handlebar of one pair, viewed in the axial direction, is aligned with one handlebar of the other pair and

(d) the diametrically opposite links extend from the intermediate member in the same direction of rotation substantially in the circumferential direction.

The shaft coupling according to the invention allows a kinematically perfect, homokinetic transmission of the rotary movement even at an articulation angle between the axes of rotation of the parts to be coupled. With such an articulation angle, the coupling halves on one side move farther apart, while on the opposite side they move closer together. These deviations are compensated for in that the links with their ends articulated on the coupling halves move outward or inward from their radial plane. It occurs in the

Axial projection a shortening of the handlebars. This "shortening" is taken into account by a pivoting movement of the handlebars and the intermediate link. The angularly accurate transmission of the rotary movement is thus retained even when a kink angle occurs.

In contrast to the coupling according to US Pat. No. 4,040,270, in the shaft coupling according to the invention, a direct connection between the coupling halves is made on both sides of the intermediate link via the axially aligned links.

Each intermediate link has a torque transmission via two parallel links. No special precautions are required for storing rings on top of one another, as is the case with US Pat. No. 4,040270.

The coupling according to the invention also allows a homokinetic transmission of the rotary movement with a radial and axial displacement of the shafts that occurs in addition to a kink angle. With such an offset, a compensating movement of the intermediate member takes place in the form of a pivoting movement of the intermediate member about a transverse axis perpendicular to its longitudinal direction.

If small torques are transmitted, a single intermediate link is provided, which is not held in a form-fitting manner, but centered by means of springs. At low torques and high speeds, the intermediate link can therefore be pulled radially outwards by centrifugal force. In some embodiments, the invention therefore provides two intermediate links which are angularly offset from one another and which are connected to one another in a rotatable manner by a central axis. In this way, both intermediate links are centered. However, the intermediate links cannot be pivoted out of their radial plane. As a result, such a shaft coupling allows the compensation of a kink angle between the shaft axes, but not the compensation of a radial misalignment.

The invention is therefore also based on the object of designing the shaft coupling in such a way that, on the one hand, centering of each intermediate link is ensured and, on the other hand, both a bending angle and a radial and axial offset can be compensated for by the shaft coupling.

According to the invention this object is achieved in that the Intermediate link is secured against radial displacement in a manner that allows rotation both around the circumferential axis and an inclination of the intermediate link against a radial plane.

This development of the invention thus includes a positive centering of the intermediate member. This centering takes place via a joint that can be moved on all sides, so that the intermediate member can perform not only a rotary movement about the circumferential axis but also a pivoting movement out of its radial plane and thus can carry out both the compensating movements required for an articulation angle and for a radial offset.

The invention is also based on the object

To keep the intermediate link centered against gravity or centrifugal forces if the transmitted torque does not center.

The wear of the centering means should be kept low. Wear is to be compensated for by self-adjustment of the centered elements.

It should also be possible to use a continuous wave such as e.g. occurs with rail drives to pass through the shaft coupling.

This object is achieved in that

(a) the intermediate link is mounted on a tube via a ball joint,

(b) the tube is connected at both ends to the first and second coupling halves via articulated connections which can be moved on all sides, and (c) a continuous shaft is passed centrally through the tube.

Another solution to the latter task is that

(A) two Zwisbhenglieder connected to the coupling halves via handlebar arrangements are arranged offset from one another about the circumferential axis and have mutually facing and aligned recesses between which a bearing ball is held, and for the rotatable connection in their crossovers area

(b) The bearing ball is seen with friction-reducing agents.

An improvement in the handlebar arrangement can be achieved in that

(a) the handlebars are elastically articulated to the pin of the intermediate member via rubber domes, the rubber domes each having a bead seated on the pin of the intermediate member, an eye of the handlebar surrounding the bead at a distance and a space filling the space between the bead and the eye has rubber-elastic mass, and

(b) the rubber-elastic mass is prestressed in each case by annular pressure members arranged on both sides around the pin, which are in the eye below

Preload of the rubber-elastic mass is pressed in and reduced in the pretension position.

Some embodiments of the invention are described below with reference to the accompanying drawings clarified:

Fig. 1 shows a cross section of a shaft coupling along the line C-D of FIG. 2.

Fig. FIG. 2 shows a longitudinal section of the shaft coupling along the line A-B of FIG. 1.

Fig. 3 shows an end view of another embodiment of the shaft coupling suitable for high speeds, seen in the direction of arrow F of FIG. 4, and

Fig. 4 shows a longitudinal section of this shaft coupling along the line E-F of FIG. 3.

Fig. 5 shows a view of a simplified shaft coupling seen in the direction of arrow K of FIG. 6.

FIG. 6 shows a section along the line G -H of FIG. 5.

Fig. 7 shows an embodiment of the invention with two intermediate pieces and an intermediate bearing ball in a section along the line C-D in Fig. 8th

Fig. 8 shows a section along the line A-B in

Fig. 7.

FIG. 9 shows an intersection of the two intermediate pieces with the bearing ball lying in between in a converted embodiment in a section along the line G-H in FIG. 10.

Fig. 10 shows a section of the line E-F in Fig. 9. Fig. 11 shows the crossing of the two intermediate pieces in a further embodiment.

Fig. 12 shows an embodiment with a single intermediate piece that on the two couplings halves is centered, in a longitudinal section along the line KL in Fig. 13th

FIG. 13 shows a section along the line I-J in FIG. 12.

FIG. 14 shows an embodiment of one that can be used in particular in the arrangement according to FIG. 11

Rubber dome for articulating a handlebar on the intermediate piece, Fig. 15 shows a modified version of the

Rubber dome.

Fig. 16 shows another embodiment of a

Rubber dome to link the two-piece handlebar to the adapter.

Fig. 17 shows a modification of the embodiment.

Fig. 18 shows a section along the line M-N in Fig. 16. Fig. 19 shows an embodiment of a rubber

Calotte in which the rubber-elastic mass can be preloaded

2o shows another embodiment of a rubber dome with a pre-tensionable rubber-elastic mass.

FIG. 21 shows an arrangement in which two intermediate links arranged crosswise to one another are held centered by a bearing ball held between them and provided with friction-reducing means without hindering their compensatory movement.

Fig. 22 shows an arrangement with a bearing member which is held centered by a tube so that a continuous shaft can be passed centrally through the bore of the tube and thus through the shaft coupling. Fig. 23 shows partially sectioned along the

Line III-III of Fig. 24 is a shaft coupling with two intermediate links centered on each other, which allows the passage of a continuous shaft.

FIG. 24 shows a section along the line IV-IV of FIG. 23.

Fig. 25 shows in a longitudinal section on an enlarged scale a rubber dome, via which the links, for example the embodiment of Fig. 24, are connected to the pin of the intermediate member.

Fig. 26 shows a modification of the rubber dome.

1 and 2 contains a first coupling half 10 and a second coupling half 12. The first hitch be 10 in the illustrated embodiment includes a hub 14 with a flange 16. Likewise, the second coupling half 12 has a hub 18 and a flange 16 facing Flange 20. Between the coupling halves 10 and 12 there are two intermediate links 22 and 24. The intermediate link 22 is an elongated part which extends (in the rest position when the waves are aligned) perpendicular to the circumferential axis 26 and has a crank 28 in the middle. The intermediate member 24 is also an elongated part which extends crossed to the intermediate member 22 perpendicular to the axis of rotation 26 and has a crank 30 opposite to the crank 28 in the middle. The intermediate members 22 and 24 engage with the cranks 28 and 30 around each other, so that their ends, for example 32 and 34, lie in a common plane. On the flange 16 there are four pins, of which only two pins 36 and 38 can be seen in FIG. 2. The pins 36 and 38 lie behind the paper plane of FIG. 2, which is represented by the line AB in Fig. 1. Two other pins are symmetrical to pins 36 and 38 in front of the paper plane. The arrangement is practically the same as that shown in FIG. 1 for the second coupling half 12. The flange 20 of the second coupling half 12 carries four pins 40, 42, 44, 46 (FIG. 1), of which the pins 42 and 46 are visible in FIG. 2. The two further pins of the first coupling half 10 are aligned with the pins 40 and 44. Each of the pins 36, 38, the two further pins (not visible) and the pins 40, 42, 44, 46 has a spherical bead 48.

At the ends, e.g. 32 and 34, the intermediate members 22 and 24 sit on both sides pairs of aligned pins. In Fig. 2, the pair of pins 50,52 at the end 32 of the intermediate member 22 and the pair 54,56 are

End 34 of the intermediate link 24 visible. At the opposite ends of the intermediate members 22 and 24, the pairs of aligned pins 58, 60 and 62, 64 are seated in the same way, it being assumed that the pins 58 and 62 are directed towards the first coupling half 10. The pins 50, 52, 54, 56, 58, 60, 62 and 64 each have a spherical bead 66 at their ends, which lies in the same radial plane as the spherical bead 48 on the pin of the adjacent coupling half. The intermediate member 22 is with the first coupling half 10 by a link arrangement of two diametrically opposed, universally articulated links, namely the link 68 (Fig. 2) and one not visible in Fig. 2, aligned with the link 70 in Fig. 1 Handlebar connected. The diametrically opposite links extend from the intermediate member 22 in the same direction, namely counterclockwise, in the circumferential direction. The intermediate link 22 is still with the second

Coupling half 12 connected by a second link arrangement of two diametrically opposed links 70 and 72 articulated on all sides. Viewed in the axial direction, one handlebar of one pair is aligned with one handlebar of the other pair, i.e. for example, the link 68 is aligned with the link 72. Similarly, the second link 24 with the first coupling half 10 is connected via a link arrangement of two diametrically opposite links, namely the link 74 in FIG. 2 and one not visible in the figures the handlebar 76 of FIG. 1 aligned handlebar. The second intermediate member 24 is connected to the second coupling half 12 via a second link arrangement, which consists of the diametrically opposed links 76 and 78 articulated on all sides.

Here, too, the diametrically opposite links extend from the intermediate member 24 in the same direction, namely clockwise, in

Circumferential direction. Here, too, one link of one pair is aligned with one in the axial direction

Handlebars of the other couple, for example the

Handlebar 74 with handlebar 78. The two intermediate links 22 and 24 are by one

Bolt 80 about a central axis shown in the

Rest position coincides with the axis of rotation 26, rotatably connected to each other.

The links 68, 70, 72, 74, 76, 78, etc. are each connected to the coupling halves 10, 12 and the intermediate members 22, 24 so that they can move on all sides via rubber pads. The type of connection is described below with reference to the handlebar 72. The other handlebars are designed in the same way.

The handlebar 72 has a spectacle-shaped housing on, which forms two cylindrical chambers 82 and 84. The housing 8 forms on one side radially inwardly projecting edges 86, 88 which delimit the otherwise continuous chambers 82 and 84 while leaving openings 90 and 92 open. Through the opening 92, the pin 52 of the intermediate member 22 protrudes into the chamber 84, so that the spherical bead 66 sits centrally in the chamber 84. From the other side, the pin 42 of the second coupling half 12 projects into the chamber 82, so that the spherical 'bead 48 of the pin 42 sits centrally in the chamber 82 and in the same radial plane as the bead 66 of the pin 52. A rubber dome 94 sits in the chamber 82 in the annular space between the wall of the chamber 82 and the spherical

Bead 48. It is pressed into this annular space and lies on one side. on the edge 86, while it is held on the other side by a ring 96 which is secured by a snap ring 98.

Similarly, a rubber dome 100 is in the chamber 84 in the annulus between the wall of the

Chamber 84 and the spherical bead 66 provided.

Via these rubber caps 94 and 100 and the pins 42 and 52, the link 72 is articulated on the coupling half 12 and the intermediate member 22 in an elastic and movable manner.

The arrangement described works as follows:

When driving the first coupling half 10, the power transmission takes place e.g. Via the pin 36, the link 68, the pin 50, the pin 52 aligned therewith, the link 72 aligned with the link 68 in the axial direction and the pin 42 on the second coupling half 12. In a corresponding manner, the force at the opposite end of the Transfer link 22 directly to the second coupling half 12 via the pins 58, 60, link 70 and pin 44. The intermediate member 22 is subjected to torsion by a radius 102. In the same way, a direct power transmission takes place via the link connected to the intermediate member 24, e.g. 74 and 78.

The pin 80 prevents instability, which could occur due to the centrifugal force when the shaft coupling is not loaded when an intermediate member 22 or 24 moves out of its central position. At a kink angle between the circumferential axis of the first coupling half 10 and the circumferential axis of the second coupling half 12, through which the second coupling half 12 in FIG. 2 is pivoted somewhat clockwise, the flanges 16 and 20 in the upper part of FIG. 2 are somewhat wider pulled apart while in the lower part of Fig. 2 approach each other more than is the case in the rest position shown. This is compensated for by a pivoting movement of the handlebars in the paper plane of FIG. 2: upper arm 68 pivots counterclockwise, and arm 72 pivots clockwise. At the bottom, link 74 pivots counterclockwise and link 78 pivots clockwise, to the same extent as upper links 68, 72. To illustrate this process, it should be noted that FIG. 2 represents a "snapshot" and the pairs of links 68, 72 and 74, 78 after 180 degrees of rotation, their functions are switched. It should also be noted that the links do not extend radially, as can be seen from FIG. 1.

By pivoting the handlebars in the paper plane of FIG. 2, an apparent shortening of the handlebars would take place when viewed in the axial direction, ie in the representation of FIG. 1. This shortening is taken into account by a pivoting movement of the intermediate member 22 or 24 and the handlebar in FIG. 1. If, for example, the link 72 in FIG. 2 is pivoted clockwise and is thereby shortened in the longitudinal direction, that is to say in the illustration in FIG. 1, this apparent shortening is taken into account by a pivoting movement of the intermediate member 22 in the counterclockwise direction in FIG. 1 worn, ie the pin 52 approaches the pin 42 in the circumferential direction. The link 68 pivoted counterclockwise experiences the same apparent shortening, which is compensated in the same way by the pivoting movement of the intermediate member 22. The pin 50 approaches the pin 36 in the circumferential direction. The angular position of the pins 36 and 42 relative to one another remains unchanged.

In the same way, the compensation takes place at the opposite end of the intermediate link 22. There the link 70 is pivoted clockwise and the link axially aligned with it and articulated on the first coupling half 10 counter-clockwise, namely by the same angles as the links 68 and 72 There is an apparent shortening of the handlebars. This is taken into account in that the intermediate member 22 is rotated counterclockwise and, for example, the pin 60 of the intermediate member approaches the pin 44 of the second coupling half 12 in the circumferential direction. The mutual angular position of the pins provided on the two coupling halves 10, 12 remains unchanged.

So there is a homokinetic transmission of the rotary movement.

In the same way, the movement is transmitted by means of the articulated on the second intermediate member

Handlebars. The handlebars, e.g. 70 and 72 are hinged to the intermediate member 22 so that they both extend from this intermediate member counterclockwise approximately in the circumferential direction. All links, e.g. 76 and 78, articulated so that they extend from this intermediate member 24 in the clockwise direction of Fig. 1 approximately in the circumferential direction.

Similarly, the coupling also allows one with homo-kinetic transmission of the rotary movement Radial misalignment of the waves.

It is assumed that when the coupling half 10 is stationary, the coupling half 12 moves parallel downwards in FIG. 2. With such a movement e.g. the pin 42 of the handlebar 72 moves downward, while the pin 36 of the handlebar 68, which is aligned therewith in the rest position, remains in its place. The pins 50 and 52 remain in alignment, however, and the distances between the pins 36, 50 and 42, 52 remain predetermined by the links 68 and 72. There is a compensating movement once in the form of a pivoting movement of the links around the pins and on the other hand in the form of a pivoting movement of the intermediate member 22 about an axis perpendicular to its longitudinal direction and lying in the paper plane of FIG. 1. The downward movement of the pin 42 against the pin 52 is compensated for by the fact that the link 72 pivots counterclockwise in FIG. 1 about the pin 52 and also the intermediate member 22 and the link 72 and thus also the link 68 a compensating movement from them Levels, e.g. out of the paper plane of Fig. 1. The pins 36 and 42 remain in the paper plane of FIG. 2.

The behavior of the clutch in the event of a radial offset in the horizontal direction is similar in FIG. 1.

The coupling thus permits a rotationally offset or homokinetic transmission of the rotary movement even in the event of a radial offset.

In the embodiment according to FIGS. 3 and 4, a first coupling half is denoted by 104 and a second coupling half by 106. Between the two coupling halves a first intermediate member 108 and a second intermediate member 110 are arranged.

The first coupling half 104 contains a hub 112 with four radial arms, each offset by 90 from one another and of which only the arm 114 is visible in the section of FIG. 4. The second coupling half 106 contains a hub 116 with four radial arms 118, 120, 122 and 124, which can be seen in FIG. 3 and of which only the arm 118 is visible in the section of FIG. 4.

The intermediate members 108 and 110 contain rings 126 and 128, respectively. The ring 126 has a bearing boss 130 on one side and a similar bearing boss 132 on the diametrically opposite side, only the bearing boss 130 being visible in section EF of FIG. 3 . The ring 128 has a bearing boss 134 on one side and a similar bearing boss 136 on the diametrically opposite side. The bearing lugs 134 and 136, which are not visible in the section of FIG. 4, are constructed in the same way as the bearing lug 130 to be described.

The arm 114 ends in a cylindrical housing 138 which is open at both ends. On one side the housing 138 forms an inwardly projecting edge 140. An axis or a pin 142 with a bead 144 in the middle sits centrally in the housing 138. In the annular space between the inner wall of the housing

138 and the axis 142 a rubber dome 146 is arranged.

The Gumraikalotte.146 is pressed into the annular space until it comes to rest on the edge 140. On the opposite side, the rubber dome 146 is replaced by a ring 148 inserted into the housing 138 held, which is secured by a snap ring 150. In this way, the axis 142 is mounted in the housing 138 in an elastic and movable manner.

The ends of the axles 142 protrude from the housing 138 on both sides. Each of the ends has a flattened section 152, 154 with opposing flat surfaces and a threaded section 156, 158. On each of the flattened sections 152 and 154 sits a link-shaped link 160, 162, which is held in each case with an opening 163 between the shoulder formed by the flattened portion and a nut 164, 166 screwed onto the threaded section 156, 158. The openings 163 form straight edges which rest on the flat surfaces, as a result of which the links are non-rotatably connected to the axles 142. Each of the arms 114 and 118, 120, 122, 124 of the coupling halves 104, 106 carries a bearing arrangement constructed in this way, which is generally designated 168 in FIG. 4. 4 shows the bearing arrangement 168 of the coupling half 104. There are three further bearing arrangements of this type which are not visible in the figures on the other arms of the coupling half 104. In Fig. 3, the bearing arrangements 170, 172, 174 and 176 are visible, which on the arms

118, 120, 122 and 124 sit. The arms and bearing arrangements on the first coupling half 104 are aligned in the axial direction S behind the arms 118, 120, 122, 124 and bearing arrangements 170, 172, 174, 176.

The bearing lugs 130 and 132 of the first intermediate member 108, of which only the bearing lug 130 is described in detail, contain arms 178, 180 extending in the axial direction on both sides of the ring 126. The axial arms 178, 180 bear on them Each ends a bearing arrangement 182 or 184 in the manner of the bearing arrangement 168. The lengths of the arms 178 and 180 are chosen such that the bearing arrangements 182 and 184 of the bearing lugs 130, 132 and 134, 136 of the intermediate members 108 and 110 in the same Layers and on the same pitch circles as the bearing arrangements 168 and others 170 and 172, 174, 176 of the first and second coupling halves 104 and 106, respectively.

It is now, as can best be seen from Fig. 3, the axis 142 of a bearing arrangement, e.g. 168, the first coupling half 104 by a pair of tab-like links 160, 162 with the bearing arrangement in FIG. 4 on the left of the adjacent bearing approach of an intermediate link, in the example of the intermediate link 110. The handlebars are non-rotatably attached to the axis of this bearing assembly in the manner described.

in the same way, the right bearing arrangements in Fig. 4, e.g. 184, the bearing lugs 130, 132, 134, 136 of the intermediate links 108, 110 via pairs of strap-like links 186, 188 or 190, 192 or 194, 196 or 198, 200 with the adjacent bearing arrangements 172, 176, 170 or 174 connected.

The intermediate links 108, 110 are rotatably supported in the area of the bearing lugs 130, 132 and 134, 136 via arcuate sliding surfaces 202, 204 and 206, 208 on the ring 128 and 126 of the other intermediate link 110 and 108, respectively. The mode of operation of the arrangement described is in principle the same as in the embodiment according to FIGS. 1 and 2. However, the embodiment according to FIGS. 3 and 4 is particularly suitable for shaft couplings which have to work at high speeds.

In the embodiment according to FIGS. 1 and 2, the handlebars form the housing for the storage. This housing is mounted on pins which project from one side of the coupling half or the intermediate link. This gives the handlebars a relatively large mass, so that high centrifugal forces are effective at high speeds. These high centrifugal forces act on the cones on one side.

In the embodiment according to FIGS. 3 and 4, the conditions are considerably more favorable in this regard: the housings for the bearing arrangements are seated, firmly on the coupling halves or intermediate members. The handlebars are relatively light tabs. These tabs sit symmetrically on both sides of the bearing arrangements. The masses and thus the centrifugal forces are divided into two halves, each of which acts on one end of the axis protruding from the bearing arrangement. Only half the forces work on a shorter arm. As a result, the embodiment according to FIGS. 3 and 4 can also be used at speeds at which the centrifugal forces cause problems in other clutches. 3 and 4 should also allow a radial offset of the shafts, the sliding surfaces 202 and 204 must be omitted. 5 and 6 show a simplified version of the shaft coupling. In this simplified embodiment, only one intermediate member 210 is provided instead of two intermediate members with associated link arrangements. The intermediate link 210 forms a ring 212 with diametrically opposed, radially outwardly projecting arms 214 and 216. The arm 214 carries a pair of aligned axial pins 218, 220 on opposite sides with beads 222 and 224. The beads 222, 224 are each surrounded by a rubber dome 226, 228, which is seated in a cylindrical recess 230, 232 each of a link 234 or 236. The rubber cups 226 and 228 are each in two parts and are placed around the beads 222 and 224 - The ends of the rubber cups, for example the rubber cup 226, are covered by essentially conical sheet metal parts 238, 240 with angled edges 242 and 244, the edge 242 each having a radial flange and the rim 244 forms an axial collar. The sheet metal part 240 rests with the edge 242 on a radially inwardly projecting edge 246 of the link 234. The edge 242 of the sheet metal part 238 is held by a ring 248 which is inserted into the recess 230 and is secured by a snap ring 250.

In the same way, the links 234 and 236 are elastically articulated on pins 252 and 254 of the first and second coupling halves (not shown).

On the diametrically opposite side, pins 256 and 258 are attached to the arm 216, on which links 260 and 262 are articulated in the same manner as described above. These links 260, 262 are articulated in a manner not shown, similar to links 234 and 236, to the first and second coupling halves, respectively. It is expedient to keep the intermediate member 210 centered in order to prevent an outward movement under the influence of the centrifugal force when idling. When working under load, centering takes place through the transmitted torques.

If there is only a kink angle between the shaft axes but no radial misalignment, centering can take place by means of a fixed bearing arranged between the coupling halves. If radial displacement also occurs, the intermediate member 210 may be elastically tied to the central position. This is indicated in Fig. 5 by the springs 264 and 266.

The intermediate member 210 is formed with the ring 212 and the central opening 268 so that a shaft can extend through it. In the embodiment according to FIGS. 1 and 2, the intermediate links can be designed as rings which are mounted on or on top of one another and which allow the passage of a central axis or shaft.

7 and 8, 270 designates a first coupling half and 272 designates a second coupling half. Between the coupling halves, which are each formed by a cable 274 or 276 and four radial lugs, for example 278 or 280, two mutually crossed intermediate members 282 and 284 are arranged. The first coupling half 270 is connected via a first link arrangement to a pair of diametrically opposed links 286, 288 via the calotte pins 287, 289 and 291, 293 to the intermediate link 232. The second coupling half is 272 also connected to the intermediate link 282 via a second link arrangement with a pair of diametrically opposed links 290, 292. One handlebar, for example 286 of one pair, is aligned with a handlebar 290 of the other pair when viewed in the axial direction. Correspondingly, the link 282 is arranged in alignment with the link 292 when viewed in the axial direction. The diametrically opposed links 286, 290 and 288, 292 he extend from the intermediate member in each case in the same direction of rotation substantially in the circumferential direction.

Correspondingly, the intermediate member 284 is connected to the first coupling half 270 and the second coupling half 272. A link 294 at the end of the link 284 on the right in FIG. 7 connects it to the first coupling half and a link 296 aligned therewith connects the link 284 to the second coupling half 272. Another pair of aligned links between the link 284 and the first or The second coupling half 270 or 272 is provided on the left end in FIG. 7, which are not visible in FIG. 8 and of which a link 298 is shown in FIG. The links 294, 296 and 298 likewise extend from the intermediate member 254 in the same direction of rotation, essentially in the circumferential direction.

In contrast to the embodiment according to FIGS. 1 and 2, in which the links extend from the one link 22 counterclockwise and from the link 24 clockwise approximately in the circumferential direction, the links extend from all links in the present embodiment in the same direction, namely clockwise in FIG. 7. 1 and 2, the two

Intermediate members 22 and 24 are connected by a bolt 80 about a central axis, which coincides in the rest position with the circumferential axis, rotatably connected to each other, in the present embodiment, the intermediate members 282 and 284 are connected to one another via an articulated joint 300.

Specifically, the intermediate members 282, 284 have mutually facing and aligned depressions 302, 304 for rotatable connection in their intersection area. A bearing ball 306 is held between the depressions 302 and 304. As best seen in Fig. 7, each of the two intersecting links 282 and 284 has a pair of sector-shaped projections 310, 312 and 314, 316, respectively, 180 ° apart and centered with respect to the axis of rotation 308, each of which extends over an angle of less than

Extend 90 °, e.g. 80 °. In each such pair of approaches 310, 312 and 316, 314, a spherical depression 302 and 304 centered on the axis of rotation 308 is provided, so that spherical bearing surfaces of sector-shaped basic shape are formed on the projections. The projections 310, 312 of the one intermediate member 282 engage between the projections 314, 316, the bearing ball 306 being held between the pairs of bearing surfaces. Since the projections each extend over an angle of, for example, 80 °, an angular range of approximately 10 ° is free between the interlocking projections, which permits rotation of the intermediate members about the circumferential axis 308. The intermediate members 282 and 284 are held by the bearing ball 306 with their mutually facing surfaces at a distance from one another, so that around the bearing ball also a pivoting movement of the intermediate members 282 and 284 to one another and from their radial planes can be done as it is necessary to compensate for a radial offset. In the radial direction, however, the intermediate links are centered with respect to one another, so that none of the intermediate links can be pulled radially outward by centrifugal forces.

The intermediate members are formed by elongated radial bodies with a central offset 318 or 320 and on both sides of the same extending radial arms 322, 324 or 326, 328 carrying the links. The intersecting intermediate members 282, 284 engage with one another with their cranks 318, 320 such that the radial arms 322, 324, 326 and 328 lie essentially in a common plane. In order to reduce the axial dimensions of the shaft coupling, the intermediate members 282 and 284 can have transverse recesses 330 and 332 on the sides facing one another in the region of the cranks 318, 320. The projections 310, 312 and 314, 316 extend in the longitudinal direction of the intermediate members 282 and 284 into these recesses 330 and 332, respectively.

In the embodiment according to FIGS. 7 and 8, prestressed, elastic tension members 334, 336 are provided between the intermediate members 282 and 284, which are only indicated schematically in FIG. 8, so that the intermediate members 282 and 284 are held non-positively in contact with the bearing ball 306 become.

A modified version is shown in FIGS. 9 and 10. The construction of the embodiment according to FIGS. 9 and 10 is similar to the embodiment according to FIGS. 7 and 8, and corresponding parts are provided with the same reference numerals as there. As can be seen from FIG. 9, the surface 338 of each intermediate link, for example 282, lies on both sides of the depression 330 in the equatorial plane of the bearing ball 306. On this surface 338, retaining links 340 are aligned with the projections 310, 312 (cf. FIG. 7) , 342 attached by screws 344, 346. These holding members 340, 342 have spherical contact surfaces 348, 350. The holding members 340, 342 extend over the bearing ball 306 and bear against the bearing surfaces 348, 350. In a similar way as described in FIG. 9 for the intermediate member 282, the intermediate member 284 engages with holding members (not visible in FIGS. 9 and 10) around the left half of the bearing ball 306 in FIG. 9. In the section of 10 only the projections 314 and 316 and the cut screws 352, 354 for fastening these latter holding members can be seen.

In this way, both intermediate members are positively connected to the bearing ball 306 by the bearing and contact surfaces 302, 304 and 348, 350.

11 shows another embodiment of the joint 360 which is provided between the intermediate members 356, 358 and is movable on all sides.

In the embodiment according to FIG. 11, the intermediate pieces 356, 358 are formed by elongated straight bodies. One of the intermediate pieces, namely the intermediate piece 356, has a spherical bead 362 in the middle. The other intermediate piece has a cylindrical opening 364 in the middle, into which the bead 362 of one intermediate piece 356 is inserted. Both sides of the bead 362 are inserted into the opening 364 bearing parts 366, 368 with spherical bearing surfaces and secured by spacer rings 370, 372 and snap rings 374, 376, so that the bead 362 is positively held in the opening 364.

The intermediate piece 358 consists in this embodiment of a ring 378 forming the opening 364 and radial arms adjoining both sides of this ring, which the bearing pins, e.g. Wear 380.

In this arrangement, the journals 382, 384 and 386, 388 must not be made in one piece with the intermediate piece 356, since otherwise the intermediate piece 356 could not be put through the opening 364. The intermediate piece 356 therefore has transverse bores at its ends, through which a continuous pin forming the Laherzapfen 382, 384 or 386, 388 is inserted. The parts of the joints are then placed on these journals 382, 384, which in turn have to be straight, cylindrical journals for insertion.

In this arrangement, too, the two intermediate links 356 and 358, which are arranged perpendicular to one another in the idle state, are connected to one another in the middle by a joint which can be moved on all sides and are thus centered on one another.

An arrangement with only one intermediate member 390 between the coupling halves 392 and 394 is shown in FIGS. 12 and 13.

To center the single intermediate member 390, there is a bushing on each of the two coupling halves

396, 398 with a spherical outer surface and a cylindrical bearing bore in a spherical one

Storage area 400 or 402 stored. In the cylindrical

Bores of the two bushings 396 and 398, a pin 404 is rotatably and axially movable, the in the middle carries a spherical bead 406. The only intermediate member 390 is supported on this bead with an axial bore 408.

The spherical bearing surface 400 or 402 is formed by two bearing half-shells 410, 412 or 414, 416, which enclose the bushing 396 or 398. These half-shells are fixed by webs 418, 420 centrally to the coupling halves 392 and 394 formed as hubs.

Pairs of ring disks 422, 424 and 426, 428 are guided on both ends of the pin 404, one ring disk 422 and 428 of each pair being connected to a part of the adjacent coupling half 392 and 394, namely the bearing half-shell 412 and 414, and the other washer 424, 426 abuts the intermediate member 390 around the axial bore 408. Compression springs 430 and 432 are provided between the washers 422, 424 and 426, 428 of each pair, which surround the respective ends of the pin 404.

If the two shafts are offset radially, for example if the coupling half 394 moves downward in FIG. 13 with respect to the coupling half 392, the bearing ball 406 moves by half the shaft offset. The change in the distance between the centers of curvature caused by the shaft offset of the spherical bearing surfaces 400 and 402 is compensated for when the pin 404 is inclined by axially displacing the pin ends in the bushes 396, 398.

Joints are provided for articulating the links 434, 436, 338 and 440 to the pins 442, 444, 446 and 448 of the intermediate member 390. These consist of one on the journal, e.g. 442, seated roller bearing 450, which ensures free rotation about the journal axis, an inner ring 452 supported on the roller bearing with a spherical outer surface 454, in which longitudinal arcuate grooves 456 (FIG. 12) are formed, one in the outer ring 458 held by the handlebar 434 with a spherical inner surface 460 which concentrically defines the spherical outer surface 454 of the inner ring 454 at a distance from one another and in which longitudinal arcuate grooves 462 are aligned with the grooves 456 of the said outer surface 454. Balls are held between the grooves 456, 462 and a cage 464, which enable a pivoting movement between the link 434 and the pin 442 in a longitudinal plane. As can be seen from FIG. 6, both joints of each link, including roller bearings 450 and inner ring 452, are surrounded by a common rubber-plastic cover 466. The rubber-elastic jacket, which is elastically deformed when the joint is deflected, ensures that the angular movements of the handlebar are distributed evenly over both joints provided on the respective link.

The handlebars can, however, also be articulated elastically on the pins of the intermediate links via rubber pads. In the embodiment according to FIGS. 7 and 8, this is done in the same way as in FIG. 2

is shown.

The "rubber pads" used there, which are known per se (DE-OS 25 20 947, in particular Fig. 16 or DE-Gbm 71 33 899) are not very flexible. This is because when the joint is deflected, the A large part of the rubber-elastic mass is pressed against rigid parts of the joint and thus subjected to compression. The bead can be made spherical with a center at the kink point of the joint. Then, however, the bead becomes relatively thick, so that either the dimensions of the entire joint become undesirably large or the space available for the rubber-elastic mass is reduced.

The invention is based on the further object of creating an elastic joint ("rubber dome") which, with the same dimensions, has a higher degree of flexibility than the previously known joints mentioned. In particular, an elastic joint suitable for the embodiment according to FIG. 11 is to be created.

The hinge contains one on the pin, e.g. 382 of the intermediate member 356 seated bead 468 formed as a separate component (FIG. 14, an eye 470 of the handlebar surrounding the bead 468 at a distance and a rubber-elastic mass 472 filling the space between bead 468 and eye 470.

The outer surface of the bead 468 is in each longitudinal plane substantially about a point beyond the axis 474 of the pin 382, e.g. 476 curved.

In the embodiment of FIG. 14 (as well as in the embodiments according to FIGS. 15 to 17), the pin 382 or 384 is in each case weakly conical, and the bead 468 has a correspondingly conical opening with which the bead on the pin 382 or 384 is postponed. The bead is 468 secured by means of an annular washer 478 and a nut 480 screwed onto the end of the pin 382. This basic structure is the same in the embodiments according to FIGS. 14 to 17, and corresponding parts are provided with the same reference symbols in all figures.

In the various embodiments, the inner surface of the eye 470 is also preferably curved in each longitudinal plane essentially around a point lying beyond the axis of the pin 382.

In the embodiment according to FIG. 15, the outer surface 482 of the bead 468 is curved around a point 484 lying approximately on the outer surface of the pin 384. The generating de outer surface 482 is therefore a circle curved around this point 484. In the embodiment according to FIG. 17, the outer surface 486 of the bead 468 is curved around a point 488 lying approximately on the opposite side of the outer surface 486. Here, too, the generating surface 486 is a circle that is curved here around point 488.

However, the curvature of the outer surface of the bead can also result from a sequence of adjoining conical ring surfaces with different cone angles. Such designs are shown in FIGS. 14 and 16, the resulting “mean curvature” in the case of the embodiment of FIG. 14 being approximately that of the embodiment of FIG. 15 and in the case of the embodiment of FIG. Fg approximately that of the embodiment of FIG 17 corresponds to.

In the embodiment according to FIG. 14, the generating one of the outer surface of the bead 468 is a polygon, the sides of which correspond in each case to a central angle of 15 ° with respect to a central point lying on the axis 474 of the pin 382, with neighboring ones Include an angle of 15 on each side of the polygon. Here the resulting center of curvature 476 lies on the opposite lateral surface of the pin 382. With a rotary movement about the axis 474 lying on it. In spite of the flat design of the elastic joint, the rubber-elastic material is essentially stressed in the circumferential direction and is not pressed against rigid surfaces of the eye 470, as is the case with known elastic joints.

In the embodiment of FIG. 16, the generating surface 486 of the bead 468 is also a polygon. The sides of this polygon correspond symmetrically to the central plane center angle around the center point 488 of 15 °, 30 ° and again 15 °. This results in a central center of curvature 492, which is also on the opposite side of the outer surface 486, similar to the embodiment according to FIG. 17

In the embodiment according to FIG. 16, the bead 468 consists of two halves 468a and 468b, the half 468a being displaceable against the half 468b by the washer 478 and the nut 480 in the position shown in FIG. 16. The handlebar 469 shown in Fig. 15 also consists of two halves 469a and 469b, the rubber-elastic mass 472 in both halves 469a, 469b of the handlebar 469 with the associated bead halves 468a, 468b being vulcanized in such a way that when the handlebar halves 469a, 469b are pulled together the screws 471 generate a prestress in the σummelastic mass 472. A total of six screws 471 are provided, as shown in FIG. 18.

In the embodiment according to FIG. 19, the bead is in two parts and consists of two axially against one another closing parts 494 and 496. Means are provided for axially moving these two parts 494, 496 apart for the purpose of prestressing the rubber-elastic mass 498. Here, too, the two parts 494 and 496 in the initial state form a bead with an outer surface 500, the generatrix of which is curved around a point 502 lying on the lateral surface of the pin 382. The bead is surrounded at a distance by an eye 504 of the handlebar, which has a spherical inner surface 506. This inner surface 506 is curved around a central point 508 lying on the axis of the pin 382.

As a means for moving apart, a sleeve 510 is rotatably mounted on the pin 382, which on the outside has a right-hand thread on one half and a left-hand thread 512 or 514 on the other half. The two parts 494 and 496 of the bead are screwed onto the right-hand and left-hand threads 512 and 514, respectively, with corresponding threads. In the rubber-elastic mass 498, in the initial state, an annular disk 514 is provided which extends from the inside and is held between the parts 494 and 496.

Sleeve 510, bead 494, 496 and eye 504 are cast in the initial state with the rubber-elastic mass 498, as indicated in the upper part of FIG. 19. The sleeve 510 sits on a gravel mold core 518, which contains a channel 520 for the supply of rubber-elastic mass. The eye 504 sits on the one hand on the gravel mold core 518 and on the other hand on a sleeve-shaped end piece 522, which likewise contains a channel 524 for the supply of rubber-elastic mass. In this way, a closed annular space is formed between the eye 504 and the bead 594,496, into which the annular disc 514 protrudes. Then there will be rubber-elastic mass in these Annulus pressed and vulcanized via channels 520 and 524. The closure piece 522 can then be removed and the component consisting of the sleeve 510, the bead 494, 496, the rubber-elastic mass 498 and the eye 504 can be pulled off from the gravel mold core 518. This component is then placed on the pin 382 and secured by the washer 526 and nut 528. If the elastic mass 498 is to be preloaded, the sleeve 510 is rotated beforehand. The two parts 494 and 496 of the bead, as shown in the lower part of FIG. 13, are screwed apart and the rubber-elastic mass 498 is prestressed against the inner surface 506.

The washer 514 has the purpose in the area of

To ensure a defined gap between parts 494 and 496 and to prevent tearing of the rubber compound when parts 494 and 496 are pulled apart.

In the embodiment according to FIG. 20, which is constructed in many points similarly to the embodiment according to FIG. 19, a sleeve 530 provided with an external thread is rotatably mounted on the pin 384 as a means for moving the parts apart. One of the parts 532 of the bead consisting of two parts 532 and 534 sits on this sleeve with an internal thread. By rotating the sleeve, one part is then moved axially relative to the other part, which likewise prestresses the rubber-elastic mass 536.

As can be seen from the figures, the inner surface, like the inner surface 506 by a circle, can be defined as generating. The generatrix of the inner surface can, however, also, as shown for example in FIGS. 8 to 11 and 14 Be a polygon. The inner surface can be formed by a central cylindrical surface and adjoining conical surfaces.

Fig. 21 shows a bearing ball 540, which is arranged between two mutually crossed intermediate members 542 and 544 in a shaft coupling according to the type of Fig. 1 to 4 of German patent application P 30 16 267.5 from

April 24, 1980 is held. Each of the intermediate links 542 and 544 is connected to the two coupling halves via link arrangements (not shown) of the type explained above. The intermediate members 542 and 544 are arranged at 90 angles to one another around the circumferential axis 546. For the rotatable connection, so that they center on one another and on the other hand can perform their compensating movements independently of one another, the intermediate members 542 and 544 in their crossing area have mutually facing and aligned recesses 548, 550, between which the bearing ball 540 is held.

The bearing ball 540 is provided with friction-reducing agents. Although the bearing ball 540 is not used for the transmission of the torque in the present shaft coupling, for example radial forces can act on the bearing ball due to centrifugal forces. In addition, the intermediate members 542 and 544 make their compensatory movements to each other and to the bearing ball 540 when there is a shaft misalignment. The friction-reducing agents are intended to prevent wear on the bearing ball during the compensating movements and simultaneous action of the radial force. The friction-reducing means have a friction-reducing coating 552 on the surface of the depressions 548, 550. This covering 552 can be formed, for example, by a self-lubricating bearing material.

Furthermore, one of the friction-reducing means is that the bearing ball 540 is designed as a hollow ball and is filled with a lubricant, preferably grease. For this purpose, the bearing ball 540 is made from two hemispherical shells 554 and 556, which are welded together. The interior 558 of the bearing ball 540 is connected via radial channels 560 to the surface parts held in the depressions 548, 550.

Ring grooves 562 are formed on the surface of the bearing ball 540 and are connected to the interior 558 of the bearing ball 540 through the radial channels 560. On the surface parts of the recesses 548, 550 lying on the bearing ball 540, annular grooves 564 are formed, which are connected to the ring grooves 562 on the outer surface of the bearing ball and into each of which a lubricant channel 566 provided in the intermediate member 542 or 544 opens. Lubricants, e.g. Lubricating grease, via the lubricant channel 566, the annular groove 564, the annular groove 562 and the radial channels 560 are pressed into the interior 558 of the bearing ball 540.

It should be noted that even when the intermediate links 542, 544 are rotated relative to the bearing ball 540, the annular grooves 562 and 564 always overlap in two points, so that even if the annular grooves are not exactly aligned as in FIG. 11, the one described Way for the grease is given. It must of course be ensured that the annular grooves 562 are always covered by the intermediate members 542 and 544, so that the grease cannot be thrown outwards under the influence of the centrifugal force. To ensure this, the rotational movement of the bearing ball 540 relative to the intermediate members 542 and 544 is limited by stops 568 and 570, respectively.

The depressions 548, 550 can be made slightly shallower than the diameter of the bearing ball 540. As a result, rubber joints on the handlebars are pretensioned such that the intermediate members 542, 544 are pressed elastically against the bearing ball 540 and remain in contact with the bearing ball 540 in the event of any wear. Elastic tension members 571, 573 can also be provided between the intermediate members

FIG. 22 shows a shaft coupling which corresponds in the basic structure to the embodiment according to FIGS. 5 and 6.

Only a single intermediate member 572 is provided there, which has two arms 574 and 576. The arm 574 carries a continuous axial pin 577, which is provided with threads 578, 580 at its ends. The ends 582 and 584 of the pin 577, which protrude from the arm 574 on both sides, are surrounded by sleeves 586 and 588, respectively, which are tightened against the end faces of the arm 574 by nuts 590 and 592, which are screwed onto the threads 578, 580 become. The sleeves 586 and 588 have beads 594 and 596, respectively. The ridges 594 and 596 are each surrounded by a rubber dome 598 and 600, respectively, which is seated in a recess 602 and 604 of a link 606 and 608, respectively.

The links 606 and 608 extend parallel to one another in the idle state and are connected at their other ends in a similar manner to pins 610 and 612, respectively, which are connected to the first and second (not shown) Coupling halves are seated.

The construction of the rubber pads is described in detail below with reference to Figures 25 or 26.

In the same way, the arm 576 is connected via links 614 and 616, which are antiparallel to the links 606 and 608 in the idle state, with pins (not shown) of the coupling halves.

In order to center the intermediate member 572, in particular against centrifugal forces during rotation without torque transmission, the intermediate member 572 is mounted on a tube 62θ via a ball joint 618. The tube 620 is connected at both ends to the first and second coupling halves via articulated connections which are movable on all sides (not shown). The articulated connections can be designed, for example, in the manner of FIG. 7 of patent application P 30 16 267.5 from April 26, 1980. A continuous shaft 622 is passed centrally through the tube.

The ball joint 618 is constructed as follows:

The intermediate member 572 has a central, axial bore 619. A ring 624 with a spherical outer surface sits on the tube 620. Two rings 626 and 628 with concave-spherical inner surfaces are inserted into the bore 619 from both sides. The concave-spherical inner surfaces of the rings 626 and 628 complement one another to form a spherical bearing surface which is complementary to the outer surface of the ring 624 and closely surrounds it. The rings 626 and 628 are secured in the axial direction by snap rings 630, 632. They are made of a self-lubricating material.

23 and 24 show a shaft coupling with two

Intermediate members 634 and 636, which are arranged crossed to each other and centered on each other by a bearing ball 638. The link 634 is over a pair from diametrically opposite, in the

Rest position anti-parallel mutually articulated links 640, 642 with pins 644, 646 of the (not shown) first coupling half and a second pair of links 648, 650, which in the

In the rest position, seen in the axial direction, align with the links 640 and 642, connected with pins 652 and 654 of the second coupling half. In a similar way, the intermediate link 636 is connected on the one hand to the first coupling half and on the other hand to the second coupling half via two pairs 656, 658 of links aligned in the axial direction. The design of each individual intermediate link 634, 636 and the design and articulation of the handlebars essentially corresponds to the arrangement in FIG. 22 and is therefore not described again in detail.

The design of the bearing ball 638 and the friction-reducing means provided thereon is similar to that of FIG. 21. Such a bearing ball from FIG. 1 could also be used in connection with the intermediate members 634 and 636 from FIG. 24. In the embodiment according to FIGS. 23 and 24, however, the bearing ball 638 has a central opening 660 with a welded-in pipe section 662. A continuous shaft 664 is passed through the central opening 660.

Fig. 25 shows an embodiment of the rubber caps, by means of which the handlebars on the pins of the intermediate link, e.g. 572 are articulated in Fig. 22.

The rubber caps each contain a bead 668 seated on the pin 666, an eye 670 of the handlebar surrounding the bead 668 at a distance and a rubber-elastic mass 672 filling the space between the bead 668 and eye 670. The formation of the bead 668 corresponds approximately to FIG. 10 patent application P 30 16 267.5, ie the generatrix of the outer surface bead 668 is a polygon. The sides of this polygon, as indicated in Fig. 25, correspond symmetrically to the center plane center angles around the center 674 of 15 °, 30 ° and again 15 °. This results in a central center of curvature, which lies on the opposite side of the outer surface of the bead 668. This has the advantage that, when the elastic joint rotates about the center point 674, despite the narrow design of the elastic joint, the rubber-elastic material is essentially stressed in the circumferential direction and is not pressed against rigid surfaces of the eye 670 or by annular pressure members.

In the embodiment according to FIG. 25, the rubber-elastic mass is prestressed in each case by annular pressure members 676, 678 arranged on both sides around the pin 666, which are pressed inward in the eye 670 by prestressing the rubber mass 672 and secured in the prestressing position. The annular pressure members 676, 678 are each sheet metal parts with an axially outwardly tapering conical inner part 680 and a radially outwardly projecting flange 682 adjoining the further end. The radially outwardly projecting flanges 682 of the pressure members 676, 678 are in contact with the eye 670 on spacer rings 684, 686 inserted from both sides. The spacer rings 684, 686 are held by snap rings 688, 690 which snap into grooves on the inner surface of the eye. By selecting the thickness of the spacer rings 684, 686, the degree of prestressing of the rubber-elastic mass 672 can be selected according to the requirements.

Fig. 26 shows another embodiment of a rubber joint. A sleeve 694 with a bead 696 is seated on a pin. The sleeve 694 can be clamped onto the pin in the manner of FIG. 22. The bead 696 has the same shape as the bead 668 of Fig. 25. A rubber-elastic mass 698 sits on the bead 696. The outer surface of the rubber-elastic mass 698 has a cylindrical middle part 700, radial ring shoulders 702, 704 adjoining it on both sides and conical surfaces 706, 708 tapering towards the ends. The rubber-elastic mass 698 has on the cylindrical middle part 700 of its outer surface in the middle a cross-sectionally V-shaped groove 710. On the lateral surface are 710 sheet metal parts on both sides of the circumferential groove

712, 714 placed on the shape of the lateral surface adapted shape.

The circumferential groove 710 allows the rubber-elastic mass 698 to escape when this rubber joint is inserted into the eye of a handlebar in the manner of FIG. 25 and is held under axial prestress by spacer rings and snap rings.

Claims

Claims

1. Shaft coupling, which allows a kink angle between the parts to be coupled, containing:

a first coupling half,

a second coupling half,

an intermediate link between the first and the second coupling half,

a first link arrangement with articulated links, which connects the first coupling half with the intermediate link and

a second handlebar arrangement with arms which are articulated to move on all sides and which connects the second coupling half to the intermediate link,

characterized in that

(a) the first link arrangement is formed by a pair of diametrically opposite links (68 ...),

(b) the second link arrangement is formed by a pair of diametrically opposed links (70, 72) and (c) a handlebar (68) of one pair, viewed in the axial direction, is aligned with a handlebar (72) of the other pair and

(d) the diametrically opposite link (68 .., 70, 72) from the intermediate link

(22) extend in the same direction of rotation essentially in the circumferential direction.

2. Shaft coupling according to claim 1, characterized in that

(a) two intermediate links (22, 24) are arranged offset in relation to one another about the circumferential axis (26) and

(b) each intermediate link (22, 24) via a first pair of diametrically opposite links (68 ...; 74 ...) with the first

Coupling half (10) and via a second pair of diametrically opposite, axially aligned with the links of the first pair arranged links (70, 72; 76, 78) is connected to the second coupling half (12).

3. Shaft coupling according to claim 2, characterized in that the intermediate members (22, 24) are rotatably connected to one another about a central axis (26).

4. Shaft coupling according to one of claims 1 to 3, characterized in that the links are each movably connected to the coupling halves (10, 12) or the intermediate member (22, 24) via rubber pads (94, 100).

5. Shaft coupling according to claim 4, characterized in that

(a) each link (72) forms a housing (80) in which rubber pads (94, 100) are held,

(B) sit on the coupling halves (10, 12) or the intermediate members (22, 24) pins (42, 52) which protrude into the housing (81) of the relevant link (72) and in the rubber caps (94, 100 ) are held. 6. Shaft coupling according to claim 4, characterized in that

(a) housings (138) are formed on the coupling halves (104, 106) or the intermediate links (108, 110), in which rubber caps (146) are held,

(b) in the rubber cups (146) an axis or a pin (142) is elastically supported, which projects axially on both sides from the housing (138), and

(c) the projecting ends of the pins (142) on the coupling halves (104, 106) and intermediate members (108, 110) are connected to each other by a link-shaped link (160, 162).

7. Shaft coupling according to claim 6, characterized in that

(a) pairs of opposing plane surfaces are provided at the ends of the pins (142) and

(b) the tab-shaped handlebars

(160, 162) with openings (163) sit on the pins (142), these openings

(163) Form straight edges that lie against the flat surfaces.

8. Shaft coupling according to claim 1, characterized in that

the intermediate member (282 or 284) is secured against radial displacement via a joint (3oo) which can be moved on all sides in a manner permitting both a rotation about the circumferential axis and an inclination of the intermediate member (282 or 284) against a radial plane.

9. Shaft coupling according to claims 1 to 5 and 8, characterized in that

the intermediate links are connected to one another via the joint (300) which can be moved in all directions. 1o. Shaft coupling according to claim 9, characterized in that

(a) the intermediate members (282, 284) for the rotatably movable connection in their crossing area facing and aligned recesses (302, 304) and

(b) a bearing ball (306) is held between the recesses (302, 304).

11. Shaft coupling according to claim lo. characterized in that

(a) each of the two intersecting intermediate members (282, 284) has a pair of sector-shaped projections (310, 312, 314, 316) which are offset by 180 ° relative to one another and centered on the circumferential axis and which each extend over an angle of less than

90 °, e.g. 80 °, extend,

(b) in each such pair (310, 312; 314, 316) of approaches a spherical recess (302, 304) centered on the axis of rotation is provided, so that spherical bearing surfaces of sector on the projections (310, 312, 314, 316) shaped basic form, and

(c) the projections (310, 312) of the one link (282) engage between the projections (314, 316) of the other link (284), the bearing ball (306) being held between the pairs of bearing surfaces.

12. Shaft coupling according to claim 11, characterized in that

(a) the intermediate members (282, 284) are formed by elongated radial bodies with a central crank (318, 320) and on both sides of the same extending radial arms (322, 324; 326, 328) carrying the handlebars and

(b) the intersecting intermediate members (282, 284) engage with their cranks (318, 320) so that the radial arms (322, 324, 326, 328) lie essentially in a common plane.

13. Shaft coupling according to claim 1, 2, characterized in that

(a) the intermediate members (282, 284) have guer progressing depressions (330, 332) on the mutually facing sides in the region of the cranks (318, 320) and

(b) the projections (310, 312; 314, 316) extend in the longitudinal direction of the intermediate members (282, 284) into these recesses (330, 332).

14. Shaft coupling according to claim 13, characterized in that prestressed elastic tension members (334, 336) are provided between the intermediate members (282, 284), so that the intermediate members (282, 284) are non-positively held in contact with the bearing ball (306),

15. Shaft coupling according to claim 13, characterized in that

(a) the surface (338, ...) of each intermediate member (282, 284) on both sides of the recess (330, 332) lies in the equatorial plane of the bearing ball (306) and

(b) on this surface (338, ...) aligned with the projections (310, 312, 314, 316) holding members (340, 342; ...) are fixed with spherical contact surfaces (348, 350; ...) , which extend over the bearing ball (306) and bear against the bearing surfaces (348, 350; ...), whereby both intermediate members (282, 284) are positively connected to the bearing ball (306) through the bearing and bearing surfaces .

16. Shaft coupling according to claim 9, characterized in that

(a) the intermediate pieces (356, 358) are formed by elongated straight bodies, (b) one of the intermediate pieces (356) has a spherical bead (362) in the middle,

(c) the other intermediate piece (358) has a cylindrical opening (364) in the middle, into which the bead (362) of the one intermediate piece (356) is inserted, and

(d) bearing parts (366, 368) with spherical

Bearing surfaces on both sides of the bead (362) are inserted into the opening (364) and are secured by snap rings (374, 376) so that the bead (368) is held positively in the opening (364).

17. Shaft coupling according to claim 8, characterized in that

(a) a bushing (396, 398) with a spherical outer surface and a cylindrical bearing bore is mounted in a spherical bearing surface (400, 402) on each of the two coupling halves (392, 394),

(b) a pin (404) is rotatably and axially movably mounted in the cylindrical bearing bores of the two bushings (396, 398) and has a spherical bead (406) in the middle, and

(c) the only intermediate member (390) with an axial bore (408) is mounted on this bead (406).

18. Shaft coupling according to claim 17, characterized in that

(a) pairs of ring disks (422, 424; 426, 428) are guided on the two ends of the pin (404), each ring disk (422, 428) of each pair being connected to a part (412, 414) of the adjacent coupling half ( 392, 394) and the other washer (424, 426) on the intermediate member (390) around the axial bore (408), and

(b) are provided between the washers (422, 424; 426, 428) of each pair of compression springs (430, 432) surrounding the respective ends of the pin (404).

19. Shaft coupling according to one of claims 8 to 18, characterized in that the links are elastically articulated to the pins of the intermediate members via rubber pads.

20. A shaft coupling according to claim 19, wherein the rubber washers each

a bead sitting on the peg of the pontic,

an eye of the handlebar surrounding the bead at a distance and

has a rubber-elastic mass filling the space between the bead and the eye,

characterized in that the outer surface (482; 486) of the bead (468) is curved in each longitudinal plane essentially around a point (484; 488) lying beyond the axis of the pin.

21. Shaft coupling according to claim 20, characterized in that the inner surface of the eye (470) is curved in each longitudinal plane substantially around a point lying beyond the axis of the pin.

22. Shaft coupling according to claim 20 or 21, characterized in that the outer surface (482) of the bead (468) is curved in each longitudinal plane about a point (484) lying approximately on the lateral surface of the pin (384). 23. shaft coupling according to claim 20 or 21, characterized in that the outer surface (486) of the

Bead (468) is curved in each longitudinal plane around a point (488) lying approximately on the opposite side of the outer surface.

24. Shaft coupling according to one of claims 20 to 23, characterized in that the curvature of the outer surface of the bead (468) results from a sequence of adjoining conical ring surfaces with different cone angles (Fig. 16).

25. Shaft coupling according to one of claims 20 to 24, characterized in that (a) the bead is in two parts and consists of two axially adjoining parts (494, 496; 532, 534) and

(b) Means (510; 529) are provided for axially moving these two parts apart in order to pretension the rubber-elastic mass (498; 530).

26. Shaft coupling according to claim 25, characterized in that

(A) a sleeve (510) is rotatably supported as a means for moving apart on the pin, which has a right-hand thread on one side and a left-hand thread (512, 514) on the other half, and

(b) the two parts (494, 496) of the bead are screwed onto the right-hand or left-hand thread (512, 514) with corresponding threads.

27. Shaft coupling according to claim 25, characterized in that

(a) a sleeve (529) provided with an external thread is rotatably mounted as means for moving the parts apart on the pin (384) and

(b) one of the parts (532) with an internal thread sits on this sleeve (529). 28 shaft coupling according to one of claims 25 to 27, characterized in that the eye (504) the bead (494, 496) in the contracted state and the sleeve (510) with rubber-elastic mass (498) and thus cast on the pin (382) are attached (Fig. 19).

29. Shaft coupling according to claim 28, characterized in that an annular disk (515) is provided in the rubber-elastic mass which extends from the inside into the latter and is held between the parts (494, 496) of the bead.

30. Shaft coupling according to one of claims 8 to 18, characterized in that for the articulation of the

Handlebars provided on the pivot joints are composed of:

(a) a roller bearing (450) seated on the pin (442), which has a free

Guarantees rotatability around the pin axis

(b) an inner ring (452) mounted on the roller bearing (450) with a spherical outer surface

(454), in which longitudinal arcuate grooves (456) are formed.

(c) an outer ring held in the handlebar

(458) with a spherical inner surface, (460) which surrounds the spherical outer surface (454) of the inner ring (452) concentrically at a distance and in which longitudinal arcuate grooves (462) are aligned with the grooves (456) of said outer surface ( 454) are formed, and (d) balls (463) placed between the gutters

(456, 462) and a cage (464) are held and allow a pivoting movement between the handlebar and pin in a longitudinal plane.

31. Shaft coupling according to claim 30, characterized in that the two joints of each link including roller bearing and inner ring are surrounded by a common rubber-elastic jacket (466).

32. shaft coupling according to claim 1, characterized in that

(a) the intermediate member (572) is mounted on a tube (620) via a ball joint (618),

(b) the tube (620) is connected at both ends to the first and second coupling halves via articulated connections which can be moved on all sides, and

(c) a continuous shaft (622) is passed centrally through the tube (620).

33. shaft coupling according to claim 1, characterized in that

(a) Two intermediate links (542, 544) connected to the coupling halves via handlebar arrangements are arranged offset in relation to one another around the circumferential axis (546) and have mutually facing and aligned depressions (548, S5o) in their crossing area, between which a bearing ball (54o) is held, and

(b) the bearing ball (54o) is provided with friction-reducing agents.

34. shaft coupling according to claim 33, characterized in that the friction-reducing means have a friction-reducing coating (552) on the surface of the recesses (548, 550).

35. shaft coupling according to claim 33 or 34, characterized in that

(a) the bearing ball (540) forms out as a hollow ball and is filled with a lubricant and

(b) the interior (558) of the bearing ball is connected via radial channels (560) to the surface parts held in the recesses (548, 550).

36. shaft coupling according to claim 35, characterized in that

(a) annular grooves (562) are formed on the outer surface of the bearing ball (540) and are connected to the interior (558) of the bearing ball (540) by radial channels (560),

(b) on the one lying on the bearing ball (540). Surface parts of the depressions (548, 550) annular grooves (562) are formed, which are connected to the annular grooves (560) on the outer surface of the bearing ball (540) and in each of which one in the intermediate member

(542, 544) provided lubricant channel (566) opens, and (c) the rotational movement of the bearing ball (54o) relative to the intermediate members (542, 544) is limited by stops (568, 570).

37. shaft coupling according to one of claims 33 to 36, characterized in that

(a) the bearing ball (638) has a central opening (660) and

(b) a continuous shaft (664) is guided through this central opening (66o).

38. shaft coupling according to claim 1, characterized in that

(a) the handlebars are elastically articulated to the pin of the intermediate member via rubber pads, the rubber pads each having a bead seated on the pin of the intermediate member, an eye of the handlebar surrounding the bead at a distance and a rubber-elastic mass filling the space between the bead and the eye, and

(b) the rubber-elastic mass (672) is prestressed in each case by ring-shaped pressure members (676, 678) arranged on both sides around the pin, which are pressed inward in the eye (670) under pretension of the rubber-elastic mass and are secured in the pretension position.

39. shaft coupling according to claim 38, characterized in that

(a) the annular pressure members (676, 678) each have sheet metal parts with an axially outwardly tapering conical inner part (680) and a radially outwardly projecting part which adjoins the further end

Flange (682),

(b) the radially outwardly projecting flanges (682) of the pressure members (676, 678) into the eye

(670) of spacer rings (684, 686) inserted from both sides and

(c) the spacer rings (684, 686) are held by snap rings (688, 690) which snap into grooves on the inner surface of the eye (670).

4o. Shaft coupling according to claim 38, characterized in that

(a) the outer surface of the rubber-elastic mass (698) a cylindrical middle part (700), adjoining radial on both sides

Has annular shoulders (702, 704) and conical surfaces (706, 708) tapering towards the ends thereof,

(b) the rubber-elastic mass (698) on the cylindrical middle part (700) has in the middle a cross-sectionally V-shaped circumferential groove (710) and (c) sheet metal parts (712, 714) of the shape of the lateral surface are adapted to the lateral surface of the circumferential groove (710).