WO2001063134A1

WO2001063134A1 - Roller bearing joint

Info

Publication number: WO2001063134A1
Application number: PCT/DE2001/000685
Authority: WO
Inventors: Lutz Scheffer
Original assignee: Rad-Sport-Arnold Gmbh
Priority date: 2000-02-24
Filing date: 2001-02-22
Publication date: 2001-08-30
Also published as: DE20003398U1; TW477872B; DE10190621D2; EP1257745A1; AU4227101A

Abstract

The invention relates to a roller bearing joint, comprising a first joint piece (1) and a second joint piece (2), which may be rotated, at least to a limited extent, about an axis, relative to the first joint piece (1), two coaxial roller bearings (4, 5) arranged between the first and the second joint pieces (1, 2), with an axial separation from each other. Said roller bearings (4, 5) each comprise an inner and an outer track, whereby the outer tracks of both bearings are connected to the first joint piece (1) and the inner tracks of both roller bearings (4, 5) are connected to the second joint piece. According to the invention, a roller bearing joint, with the properties mentioned in the introduction, which is easily and quickly assembled and guarantees an exact bearing mount without fine adjustment may be achieved, whereby two inner and two outer bearing shells (6', 7'), which are at least partly tightly fitted to the components forming the bearing tracks, or, optionally, are formed in one piece with the bearing tracks. The two outer bearing shells (6, 6') are fixed to the first joint piece (1) and the two inner bearing shells (7, 7') are fixed to the second joint piece (2). The bearing tracks of one of the bearings (4) are fixed to the corresponding outer bearing shell (6') and also to the corresponding inner bearing shell (7') in an axial direction, while the other of the bearings (5) is only axially fixed to one of the corresponding outer or inner bearing shells (6, 7) and may move axially relative to the remaining bearing shells (7, 6) with a preferably tight sliding fit.

Description

Rolling joint

The present invention relates to a roller bearing joint with a first joint part and a second joint part, which is at least limitedly rotatable about an axis with respect to the first joint part, with two coaxial and axially spaced roller bearings, which are provided between the first and the second joint part are, the roller bearings each having an inner and an outer raceway, the outer raceways of the two roller bearings being assigned to the first joint part and the inner raceways of both roller bearings being assigned to the second joint part.

As far as concrete examples are described in the following, for the sake of simplicity reference is made to ball bearings as roller bearings and the corresponding raceways are ball raceways without any intention to restrict them. The invention is of course generally applicable to joints with roller bearings according to the wording of the claims, whether the roller bearings are now ball bearings, needle bearings or the like. Furthermore, the terms "first joint part" and "second joint part" can also be interchanged and only for the sake of simplicity, the first joint part is referred to here as that which is connected to the outer raceways of the roller bearings. Furthermore, in principle it would also be possible, at least if the joint parts only have to be rotatable relative to one another to a limited extent, to connect the first joint part to the outer raceway in one of the roller bearings and to the inner raceway in the other roller bearing and the second joint part accordingly to the inner raceway to connect the first rolling bearing and the outer raceway of the second rolling bearing. However, this would lead to relatively cumbersome constructions of the first and second joint parts, which are not preferred for this reason, but should not be excluded from the scope of the present invention.

A special area of application for corresponding roller bearing joints are bicycle frames in which the so-called rear frame can be pivoted to a limited extent about a horizontal axis relative to the main frame. Such bicycles are, for example, relatively high-quality mountain bikes with a so-called resilient rear triangle, in which the rotational movement of the rear triangle relative to the main frame can be pivoted to a limited extent in the event of hard impacts by a roller bearing joint and against the force of an elastic return element, optionally with integrated damping. It goes without saying that the present invention can also be used in other areas of mechanical engineering, wherever a first machine part should be able to rotate to a limited extent with respect to a second machine part, and the swivel joint should be as stable as possible with a precisely defined axis and at the same time with little friction. Two precisely spaced axially spaced and coaxially arranged roller bearings, which define the desired axis of rotation due to their relative arrangement and alignment, ensure a precisely defined axis and little play with low friction.

In the previously known roller bearing joints of this type, however, the assembly and adjustment of the roller bearings is relatively complex and difficult. Since the two joint parts are mutually movable and are only connected to one another via the roller bearings, adjustable bearing shells with integrated raceways are often used, which must be installed and adjusted together with the roller bearing elements (e.g. balls) when installing the roller bearing joint. The setting of these bearings is a relatively complex process in which errors can easily occur. If the raceways or bearing shells are set with too much play, the bearing can deflect very easily, i.e., in the case of shock loads due to the existing play in motion, also lead to shock loads on individual roller bearing elements, which then press locally into the raceway or damage the running surface , so that a low-friction and precise joint movement in the bearings is no longer possible.

In the other extreme case, the bearing can be set too tight, which also leads to damage to the raceway, since then the individual roller bearing elements as well as the raceways are subject to very large loads in continuous operation, which also causes indentations and depressions in the raceway surface or non-roundness in the Rolling bearing elements result.

Compared to this prior art, the present invention has for its object to provide a rolling bearing joint with the features mentioned above, which is quick and easy to install and ensures an exact bearing fit without fine adjustment.

This object is achieved by two inner and two outer bearing shells, which are at least partially in close engagement with the parts forming the raceways and are otherwise optionally formed in one piece with the raceways, the two outer bearing shells being fixed to the first joint part and the two inner bearing shells are fixedly connected to the second joint part and the raceways of one of the bearings are fixed in the axial direction both on the associated outer bearing shell and on the associated inner bearing shell, while the other of the bearings is axially fixed to only one of the associated outer or inner bearing shells is fixed and is axially movable relative to the remaining bearing shell in a preferably narrow sliding fit. The bearing shells are thus at least partially in close engagement with the parts forming the raceways, that is to say at least partially bearing elements are separated from the raceways or the parts forming the raceways. At least one of the bearing shells must not be identical or integral with one of the raceways. The other bearing shells could, however, optionally also be directly the parts forming the raceways, that is to say be formed in one piece with the raceways. However, the bearing shells are preferably only components, and as precise as possible components which are in close engagement with races or similar parts forming the raceways and thus define their position and represent the connection between the raceway or raceway and the first or second joint part. The bearing shells could in principle and at least partially also be formed in one piece with the first and second joint parts, but in the preferred embodiment of the invention they are also elements separate from the first and second joint parts.

The ball bearings are preferably pre-assembled bearings, preferably encapsulated bearings, which have seals which prevent the running surfaces of the bearing rings and the balls from becoming dirty.

The term "bearing shells" is interpreted in a relatively broad sense within the scope of the present invention. In particular, an outer cylindrical surface on which a ball bearing race is placed is also viewed and interpreted as a "bearing shell".

However, these bearing shells are firmly connected to one of the first or second joint parts in such a way that the two outer bearing shells are firmly connected to the first joint part and the two inner bearing shells are firmly connected to the second joint part. One of the bearings is then fixed in the axial direction both on the outer bearing shell and on the associated inner bearing shell in the axial direction. Specifically, the outer or inner bearing races are fixed to the outer or inner bearing shell, which in turn are connected to the first or second joint part. In this way, the axial position of the two joint parts is fixed relative to one another via the intermediate bearing and the axial fixation of the outer and inner bearing races on the bearing shells and thus also on the joint parts. The second bearing, which is arranged at an axial distance from the first bearing, is then only fixed to one of the bearing shells, that is to say either the inner bearing race is axially fixed to the inner bearing shell or the outer race is attached to the outer bearing shell and thus fixed to the first joint part. Compared to the remaining bearing shell, for example, the outer bearing race then remains axially movable, albeit with the closest possible sliding fit. Since the relative axial position of the first joint part relative to the second is already fixed by the axial fixation of the two races of the first bearing, the fixation of the second bearing on both parts would mean an overdetermination of the axial position of these two parts and it would lead to bearing tension with the smallest tolerances. Although one could eliminate or minimize these bearing tensions by means of axially adjustable bearing shells, this requires an adjustment process, in which errors which occur from time to time are inevitable, so that bearing tensions nevertheless occur. In addition, such an adjustable bearing shell could, under certain circumstances, also lead to automatic adjustments, so that the bearings would then be tightened again and are correspondingly stiff and may even be damaged or destroyed, but in any case quickly wear out.

However, by designing one of the bearing shells so that the associated bearing race rests on this bearing shell in a tight sliding fit, that is to say inside the cylindrical bearing shell as an outer ball race or as a ring-shaped inner bearing shell as the inner bearing race, corresponding tensions can occur do not occur in advance and no bearing adjustment is required at all. Accordingly, completely prefabricated bearings are expediently used, which consist of an outer and an inner race with intermediate rolling elements, such as e.g. Balls, exist.

In the preferred embodiment of the invention, the bearings or their raceways or races are axially fixed to the associated bearing shells on the axially one side by a projecting collar and on the axially other side by a retaining ring. Accordingly, the roller bearings are placed with an inner roller bearing race on the bearing shell in the form of a cylindrical pin or the like until they strike a collar of the pin, and / or are inserted into a hollow cylindrical bearing shell until the outer bearing race strikes a collar. A locking ring is then provided for the axial length or width of the bearings or bearing races, which is preferably inserted into a circumferential groove of the bearing shells in question, the groove being positioned such that the bearing or the corresponding bearing race between the as a stop acting collar and the locking ring is axially fixed largely without play. As was already apparent from the above description, the term "bearing shell" is understood in a broad sense in the context of the present description in that it does not only include more or less hollow cylindrical parts which receive a bearing, specifically an outer bearing race , but also pins or other parts with a cylindrical outer surface on which an inner bearing race fits properly.

The projecting collar is expediently provided on the bearing shells on the side of a roller bearing facing the respective other roller bearing, since then access to the other side of the bearing, where the securing ring is to be attached, is not hindered by the respective other bearing.

In the preferred embodiment, the inner bearing shells are formed in one piece with two cone pins, which have a central bore for the passage of a clamping screw and which engage in two corresponding hollow conical ends of a tubular part and are braced with this. The tubular part, the two tube ends of which have a conical inner surface, corresponds to the second joint part. The two so-called cone pins have correspondingly conical outer surfaces which engage with the conical inner surfaces at the ends of the tubular part opposite one another, the central bore of these two cone pins being penetrated by a tension screw or a tension screw being pushed through one pin and into the other is screwed in, so that the conical pins are moved towards one another, thereby being pulled firmly into the hollow-conical ends of the tubular part and being braced with the tubular part. The remaining part of the cone pin, which still protrudes from the tubular part, is cylindrical and has a cylindrical outer diameter which corresponds to the inner diameter of the associated inner races of the roller bearings, so that these cylindrical ends of the cone pins are the inner bearing shells for the roller bearings form.

In the preferred embodiment, the tubular part with two hollow conical ends is part of a bicycle frame, in particular part of a so-called bicycle main frame. This part of the bicycle frame, which is designed as a tube with conical inner surfaces at both tube ends, is preferably part of a bicycle main frame, which is arranged directly above a bottom bracket housing and in the same orientation as the bottom bracket housing and is integrally connected to the bottom bracket housing.

In the preferred embodiment of the invention, the outer bearing shells have external threads and are screwed into two preferably rigidly interconnected eyelets or short pipe sections with a corresponding internal thread. These rigidly interconnected eyelets or pipe sections represent the first joint part or a part thereof.

Again in the preferred embodiment of the invention, these eyelets are part of a bicycle rear triangle, which essentially consists of two interconnected tubular triangles, one of which is arranged on one side of a rear wheel and forms the so-called "rear wheel gait" and these have a clear distance , which corresponds at least to the axial length of the double hollow conical, tubular part of the bicycle frame.

Since the eyelets of the bicycle rear structure have a clear distance which corresponds at least to the axial length of the double hollow conical, tubular part of the bicycle frame, this tubular part can be guided between the two eyelets and aligned axially with the eyelets. In this position, the cone pins can be inserted and clamped through the eyelets into the ends of the tubular part, and the bearings can also be seated on the cylindrical ends of the cone pins. Then or even beforehand, the bearing shells are screwed into the eyes in the form of rings with an external thread, which also simultaneously on the cylindrical Grip the ends of the tapered ball bearings from the outside. As already mentioned, the races of one of the bearings are then fixed in the axial direction both on the inner bearing shell of the conical journal and on the outer bearing shell, unless this has already happened (e.g. when the ball bearings are placed on the inner bearing shells) while on the on the other hand, only one of the bearing races, for example the bearing race seated on the cone journal, is fixed in the axial direction, but is guided so as to be axially movable in the outer bearing shell. The range of motion for the outer bearing race in the outer bearing shell only has to compensate for the manufacturing tolerances that arise during the manufacture of the individual joint parts, i.e. the axial length of the bearing shell in which the outer bearing race is axially movable does not have to be, or only slightly larger than, the one axial length of a bearing race, e.g. by 2-3 mm.

Accordingly, the inner surface of one of the outer bearing shells has a substantially smooth, cylindrical inner wall without radially inwardly projecting parts, while the inner surface of the other outer bearing shell has a radially inwardly projecting collar, which serves as a stop for a rolling bearing race, as well as at a distance and parallel to it the collar has a circumferential groove for receiving a locking ring such that the outer rolling bearing race between the collar and the locking ring is axially fixed in the bearing shell. The inner bearing shells in turn also each have a collar, in this case a radially outwardly projecting collar, which serves as a stop for an inner rolling bearing race, and they have a circumferential groove at a distance and parallel to the collar for receiving a Circlip in such a way that the inner rolling bearing races are axially fixed between the collar and the circlip each of one bearing shell. The bearings are expediently encapsulated rolling bearings, that is to say pre-assembled bearings. In a particularly simple and inexpensive embodiment of the invention, the roller bearings are designed as ball bearings.

In the preferred embodiment of the invention, the two cone pins, which have already been described above, have a central bore, in the case of a first of these cone pins the bore is provided with an internal thread, whereas the second cone pin has only one through bore for the passage of the bolt, which can be screwed into the internal thread of the other cone pin. The bolt is supported with a bolt head on a matching collar or edge of the cone that only has the through hole. The open ends of the through bores of both cone pins can preferably be closed by a cover or the like. These can be plastic lids, which are simply snapped into suitably designed openings at the ends of the cone pins.

With regard to the outer bearing shells, an embodiment of the invention is preferred in which one bearing shell has a right-hand thread and the other has a left-hand thread. An embodiment in which the threads have the standard dimensions which are also suitable for pedaling is particularly preferred. bearing threads are used. In this way it is possible to produce or rework the threads in the eyelets of the bicycle rear end in the same way as is also the case with bottom bracket threads. Exactly the same tools can be used, which considerably simplifies and speeds up the assembly and manufacturing process.

Further advantages, features and possible uses of the present invention will become clear from the following description of a preferred embodiment and the associated figures. Show it:

FIG. 1 shows the side view of a bicycle (mountain bike) with a roller bearing joint 100,

2 shows a perspective exploded view of the roller bearing joint according to the invention with the adjacent joint parts and FIG. 3 shows an axial section through the roller bearing element shown in FIGS. 1 and 2.

A bicycle (mountain bike) can be seen in FIG. 1, which has a frame 20 and a rear structure 10 articulated thereto at 100. This rear end consists essentially of a tube 15, which also carries a roller bearing housing 1, the rear wheel fork 16 and the struts 17, the tubes and struts 15, 16, 17 being welded or soldered together to form a double triangular connection, so that a The rear wheel of a bicycle can be received between the rear fork 16 and the struts 17, the upper triangle point of this tube assembly being connected to a suspension and damping element 18 which is articulated on the frame 20 at its other end. A bottom bracket housing 22, which is firmly connected to the frame 20, can also be seen below the roller bearing joint 100.

In Figure 2, the roller bearing 100 and also the immediately adjacent elements of the frame of the rear frame are shown again in a perspective exploded view (and reversed with respect to Figure 1). In particular, one recognizes again the tube 15 and the fork 16 of the rear triangle, which are firmly connected to a roller bearing housing 1, which has two lateral eyelets 11. In the space that is left between the eyes 11 formed by the roller bearing housing 1, a tubular sleeve 2 is inserted, which is rigidly connected to the bottom bracket 22 and the other parts of the frame 20, as can also be seen in FIG.

The roller bearing housing 1 and the tubular sleeve 2 form the first and second joint part, which are articulated to one another by the other elements shown in Figure 2, so that the rear frame 10 can be pivoted relative to the frame about the axis defined by the roller bearing. It can be seen from FIG. 1 that a force exerted, for example, essentially vertically in the direction of the roller bearing joint 100 via the saddle leads to the bottom bracket 22 with the roller bearing joint 100 lowering somewhat, while the axes of the two ratchets which are fixed when the bicycle stands on the ground, so that as a result opposite rotational movements of the frame 20 and the rear frame 10 take place around the roller bearing joint 100, whereby the spring 18 is compressed. However, since the spring 18 is relatively strong, the rotational movement in the joint 100 when the bicycle is under normal load is still only very slight due to the weight of a person. During fast driving over uneven routes, however, very violent impacts can be exerted on the wheels, whereby impacts on the front wheel are intercepted primarily via the front fork, which is likewise provided with a suspension, while the impacts exerted on the rear wheel can be absorbed by the spring system 18, whereby the rear triangle is pivoted relative to the frame around the roller bearing joint 100. However, as can be seen, the swiveling range is greatly limited by the maximum stroke of the spring and is in any case significantly below 30 ° without the rolling bearing joint according to the invention in principle being limited to small swiveling angles.

The connection of the two joint parts, namely the roller bearing housing 1 and the tubular sleeve 2, takes place via the elements which can be seen in detail in FIG. 2. These are initially two outer bearing shells 6 and 6 ', which are screwed into threads in the eyelets 11 of the roller bearing housing 1. For the description of the mounting positions of the individual elements, reference is made to FIG. 3, which shows the roller bearing in the assembled state in an axial section.

The two axially pierced cones 7, which also serve as inner "bearing shells", are inserted into the tubular sleeve 2 from both sides, the inner ends of which are conical to match the conical surfaces of the conical pins 7, 7 ', as can be seen in FIG recognizes. The cone pin 7 only has a simple through hole, while the cone pin 7 'has a threaded hole. A screw bolt 13 is passed through the bore of the conical pin 7 and screwed into the opposite threaded bore of the conical pin 7 ', whereby the conical pins 7, 7' are drawn into the tubular sleeve 2 from opposite sides and their conical surfaces are firmly attached to the conical inner surfaces of the tubular sleeve 2 until an end position of the two conical pins in the tubular sleeve results at a specific, preferably fixed tightening torque.

The two outer ends of the conical pins 7, 7 'are designed as cylindrical bearing shells for receiving the inner bearing ring of a ball bearing 5 or 5'. Before their transition into the conical surfaces of the conical pins, these cylindrical ends also have an outwardly projecting, annular circumferential collar 12 or 12 ', which in each case serves as a stop surface for the inner race of the ball bearings 5 or 5'. Furthermore, these bearing shell surfaces of the conical pins 7, 7 'have a circumferential groove at a distance from the collar 12 or 12' which corresponds exactly to the axial length of the inner ball races of the ball bearing 5. A retaining ring 3 or 4 is inserted into this groove after the ball bearings 5, 5 'have been pushed onto the inner bearing shells of the conical pins 7. Before the ball bearings 5, 5 'are pushed on, at least the bearing shell 6' shown on the right in FIG. 3 must be screwed into the bottom bracket housing 1 or the eyelet 11. This bearing sleeve 6 'has an inwardly projecting collar 14 which serves as a stop for an outer bearing race. If the bearing 5 'which can be seen on the right in FIG. 3 is then pushed onto the cylindrical end of the conical pin 7' and at the same time into the bearing shell 6 ', the dimensions of which are closely matched to one another, the inner locking ring 4 and the outer locking ring 9 can then be used become.

As can be seen, a circumferential groove is also provided in the outer bearing shell 6 ', the distance from the inner collar 14 of the bearing shell 6' corresponds to the axial length of the outer ball bearing race. For the rest, it can also be expedient if the ball bearing is first inserted into the bearing shell 6 'and then assembled together with the bearing shell, that is to say the bearing shell is screwed into the housing 1 with the ball bearing arranged therein, whereby the inner ball bearing race slides onto the cylindrical end portion of the taper pin 7 '. It should be noted that the tubular sleeve 2, which can be seen in FIG. 3, is connected to the bottom bracket housing 22 according to FIG. 2, so that the tubular sleeve 2 is only axially displaceable to a limited extent in the space between the two eyelets 11 and thus forms an abutment when the ball bearing 5 'is pushed onto the conical pin 7' which is firmly connected to the tubular sleeve 2.

If the bearing sleeve recognizable on the right in FIG. 3 is screwed in and the bearing 5 'is fixed by the two retaining rings 4, 9 and the respective opposite collars 12' and 14, the conical pin 7 'and thus the tubular sleeve 2 and the opposite cone pin 5 is axially clearly fixed. Then the tubular sleeve 2 is axially fixed with respect to the housing 1 of the roller bearing joint.

The ball bearing 5 can then be mounted on the left-hand side in FIG. 3, but this can also be placed on the cylindrical section of the conical pin 7 beforehand and secured with the locking ring 3. The left outer bearing shell 6 has no annoying collar or other stop for the bearing 5, since its position would otherwise be overdetermined, which would require precise adjustment of the contact surfaces on the bearing shell 6. Instead, the position of the bearing 5 is determined solely by the position of the bearing 5 'which can be seen on the right, since this bearing 5' is fixed to the bearing shell 6 'by the collar 14 and the locking ring 9, which in turn has a fixed end stop position after being screwed into it Has thread of the housing 1. About the ball tracks and balls of the bearing 5 ', the inner bearing race is also axially fixed with respect to the outer one and is via the connection of the inner bearing race to the cylindrical portion of the conical pin 7' and the contact of the inner ball bearing race with the collar 12 'and the locking ring 4 also the position of the opposite ball bearing in the axial direction. This is obviously because the two - ¬

the cone pins 7, 7 'are firmly and rigidly connected to one another via the screw bolt 13 and the bracing on the tubular sleeve 2. The ball bearing 5 is in turn fixed on the locking ring 3 and the collar 12 on the taper pin 7, while the outer bearing race ring of the ball bearing 5 in the outer bearing shell 6 is axially freely movable.

In this way, tolerances that arise, e.g. by the production of the conical pins and the sleeve 2 with conical inner surfaces when the parts are pulled together, can be compensated in a simple manner without any adjustment work. The dimensions of the housing 1 and / or the bearing shells and the position of the collars 12 ', 14 can also vary due to tolerance deviations and are automatically compensated for by the roller bearing 5, which is freely displaceable either in the outer bearing shell 6 or on the inner bearing shell 7.

With the axial fixation of a bearing on both joint parts according to the invention with only partial fixation of the other bearing on only one of the remaining bearing shells, it is thus achieved that no bearing adjustment work is necessary and that ready-made bearings can be used. In particular, encapsulated bearings can be used that are largely sealed against the ingress of dirt. The ends of the cone pins 7, 7 'can also be provided with appropriate covers and, moreover, the outer ends of the bearing shells 6, 6' or the roller bearing housing 1 can be completely covered, so that the bearing is secured against the ingress of dirt.

It is understood that the corresponding roller bearing joint and its assembly is not limited to use on bicycles, but can be used in many areas of technology wherever parts have to be pivoted relative to one another.

Claims

Patent claims

1. Rolling bearing joint with

a first joint part (1) and a second joint part (2), which is at least limitedly rotatable about an axis relative to the first joint part (1), two coaxial and axially spaced roller bearings (4, 5), which between the first and the second joint part (1, 2) are provided, - the roller bearings (4, 5) each having an inner and an outer raceway, the outer raceways of the two roller bearings (4, 5) being assigned to the first joint part (1) and the inner raceways of both roller bearings (4, 5) are assigned to the second joint part,

characterized by the following features:

two inner and two outer bearing shells (6 ', 7') which at least partially engage in a tight fit with the parts forming the raceways and are otherwise optionally formed in one piece with the raceways, - the two outer bearing shells (6, 6 ' ) are firmly connected to the first joint part (1) and the two inner bearing shells (7, 7 ') are firmly connected to the second joint part (2), and the raceways of one of the bearings (4) both on the associated outer bearing shell (6' ) and on the associated inner bearing shell (7 ') are fixed in the axial direction, while the other of the bearings (5) is axially fixed only on one of the associated outer or inner bearing shells (6, 7) and opposite the remaining bearing shell ( 7, 6) is axially movable in a preferably narrow sliding fit.

2. Rolling bearing joint according to claim 1, characterized in that the axial fixation of the bearings (4, 5) or raceways on the associated bearing shells (6, 6 ', 7, 7') on the axial one side by a projecting collar and on the axially other side is done by a locking ring.

3. Rolling bearing joint according to claim 2, characterized in that the projecting collar (12, 12 ', 14) on the other rolling bearing (5, 5') facing side of a rolling bearing

(5 ', 5) is provided.

4. Rolling bearing joint according to one of claims 1 to 3, characterized in that two inner bearing shells (7, 7 ') are integrally formed with two cone pins (17, 17'), the egg Have ne central bore (19, 19 ') for the passage of a clamping screw (13), and which engage in two correspondingly conical ends of a tubular part (2) and are braced with it.

5. Rolling bearing joint according to one of claims 1 to 4, characterized in that the tubular part (2) is part of a bicycle frame, in particular part of a bottom bracket attachment.

6. Rolling bearing joint according to one of claims 1 to 5, characterized in that the outer bearing shells (6, 6 ') have an external thread and in two preferably rigidly interconnected eyelets (11) or short, internally threaded pipe pieces of

Housing (1) are screwed in.

7. Rolling bearing joint according to claim 6, characterized in that the eyelets are part of a bicycle rear frame and have a clear distance which corresponds at least to the axial length of the double hollow conical, tubular part of the bicycle frame.

8. Rolling bearing joint according to one of claims 1 to 7, characterized in that the inner surface of one of the outer bearing shells is a substantially smooth, cylindrical inner wall without radially inwardly projecting parts, while the inner surface of the other outer bearing shell has a radially inwardly projecting collar which serves as a stop for a rolling bearing race, and has a circumferential groove at a distance and parallel to the collar for receiving a retaining ring such that the outer rolling bearing race between the collar (14) and the retaining ring (9) is axially fixed to the bearing shell.

9. roller joint according to one of claims 1 to 8, characterized in that the inner bearing shells (7, 7 ') each have an outwardly projecting collar (12, 12'), which serves as a stop for each inner roller bearing race, and at a distance and parallel to the collar (12, 12 ') has a circumferential groove for receiving a retaining ring in such a way that one of the inner rolling bearing races is axially fixed between the collar and the securing ring.

10. Rolling joint according to one of claims 1 to 9, characterized in that the rolling bearings are pre-assembled, preferably encapsulated rolling bearings with an inner and outer race.

11. Rolling bearing joint according to one of claims 1 to 10, characterized in that the rolling bearings are ball bearings.

12. Rolling bearing joint according to claim 4 or one of the claims dependent on claim 4, characterized in that both cone pins (7, 7 ') have a central bore (19, 19'), a first of which is provided with an internal thread, while the the second is designed as a through hole for the passage of a bolt that can be screwed into the internal thread of the other cone pin, the head of which bears against a matching collar or edge of the through hole of the second cone pin, so that the two cone pins are moved towards one another by tightening the bolt.

13. Rolling bearing joint according to one of claims 1 to 12, characterized in that the open outer ends of the cone pins can be closed by a cover.

14. Rolling bearing joint according to one of claims 1 to 13, characterized in that one of the outer bearing shells has a right-hand thread and the other has a left-hand thread, which preferably correspond to the standard threads of bicycle pedal bearings.