DE102016121393A1 - Ball bearing and method for its manufacture, fixed bearing, steering gear and steering system - Google Patents

Abstract

A ball bearing (9) having an inner bearing shell (27) and an outer bearing shell (26) each having at least one guide groove (28) for receiving and guiding balls (29) of the ball bearing (9), wherein the inner bearing shell (27 ) and / or the outer bearing shell (26) comprises at least two partial shells (30), each of which forms a separate guide groove (28) or a section of a guide groove (28), characterized in that the partial shells (30) by means of connecting means with each other are connected. A method for producing such a ball bearing is characterized in that the partial shells (30) of the inner bearing shell (27) and / or the outer bearing shell (26) are processed in the connected state to the guide grooves and / or an outer bearing surface and / or to form an inner bearing surface of the ball bearing (9). Thereby, the production of such a ball bearing can be simplified.

Description

The invention relates to a ball bearing and a method for its production. The invention further relates to a fixed bearing for a steering gear, a steering gear for a steering system, in particular a power steering system, a motor vehicle with such a bearing and such a steering system.

In most motor vehicles, power steering systems are installed, which generate a supportive torque during steering and thereby reduce the steering torque to be applied by the driver to the steering column.

The known power steering systems are based on a steering gear that translates the drive power of a hydraulic or electric steering motor and transmits, for example, the steering column. Such steering gears are regularly formed in the form of a screw gear and in particular as Schraubradgetriebe or worm gear. These include a gear which is directly or indirectly connected to the steering column, and a thus meshed, driven by a shaft of the drive pinion.

As a problem with such steering gears gear play has been shown that forms due to component tolerances, different thermal expansion of the gear elements, due to wear and / or setting of the material in gears made of plastic. In particular, in a so-called Wechsellenken, i. in a direct successive steering with changing steering direction, such a gear play generates unwanted noise, resulting from the alternate application of opposite edges of the teeth of the pinion and gear.

It is known to eliminate this gear play in that the pinion shaft is pivotally mounted about an axis which is perpendicular to the longitudinal axis of the pinion shaft and at a distance from the meshing engagement of pinion and gear, and is pressed by means of one or more spring elements against the gear , The pivotability of the pinion shaft is thereby regularly integrated in one of the two bearings over which the pinion shaft is mounted end. This storage is called "fixed storage". The storage in the region of the other end is then carried out with a defined game (so-called "floating bearing") to allow the deflection caused by the pivoting movement. The fixed bearing is regularly provided on the drive side, while the floating bearing is provided at the free end of the pinion shaft. The one or more spring elements for pressing the pinion to the gear can be integrated into both the floating bearing and the fixed bearing.

Such a steering gear, in which the spring force is generated for springing by means of the fixed bearing, for example, from DE 10 2009 054 655 A1 known. In this steering gear is provided, the rolling bearing, which receives the pinion shaft in the region of the fixed bearing to store outside in a pivot sleeve. The pivot sleeve comprises a bearing sleeve which receives the rolling bearing largely free of play, and an outer ring which is held largely free of play in a receptacle of a housing of the steering gear, wherein the outer ring and the bearing sleeve are connected via a plurality of torsion bars, which in a rotation of outer ring to bearing sleeve be twisted. After assembly of the steering gear, the torsion bars are twisted in such a way that the elastic restoring effect generated thereby causes the springing of the pinion shaft.

Embodiments of steering gears, which to those of DE 10 2009 054 655 A1 are similar, are from the DE 10 2008 040 673 A1 , of the EP 2 836 416 B1 and the EP 2 836 417 B1 known.

In the case of the steering gears known from the cited publications, single row deep groove ball bearings of conventional design are used. These each comprise a one-piece inner bearing shell and a one-piece outer bearing shell. The bearing shells each form a guide groove for receiving and guiding balls. The installation of such a deep groove ball bearing requires an annular gap formed between the bearing shells with a defined minimum width, which is dimensioned so that the balls can be used with a maximum possible eccentric arrangement of the inner bearing shell within the outer bearing shell during assembly in the then crescent-shaped gap , This minimum width of the annular gap limits the size with which the shoulders of the guide grooves cover the balls in the radial direction with respect to the longitudinal or rotational axis of the ball bearing. Due to the relatively high tilt load of the ball bearing in a steering gear, as is known from the cited documents, the balls run on the edge of the raceway shoulders. The bearing capacity of such a loaded ball bearing therefore depends to a considerable extent on the size of the coverage of the shoulders of the guide grooves with respect to the balls. For a relatively small ball bearing then no full pressure ellipse of the balls would be formed on the track of the guide grooves. A solution to this problem could be to dimension the ball bearing as large as possible, whereby the largest possible support surface of the balls is realized on the track. However, such relatively large ball bearings require a correspondingly large space in the steering gear, which is often not available or due to a correspondingly enlarged Design of the steering gear would have a disadvantageous overall.

Basically also known are so-called four-point bearings, which are single-row radial angular contact ball bearings, whose raceways are designed so that axial loads can be recorded in relevant amounts in both directions. Four-point bearings can have a split inner ring, which makes it possible to integrate relatively many balls in it, which ensure a high load capacity of such a four-point bearing.

Producing such ball bearings with split inner rings is relatively complex and therefore costly, since the function and life of ball bearings depends essentially on the accuracy of the guide groove geometry and consequently both ring halves must fit exactly to each other. One way to produce a ball bearing with a split inner ring is to finish the guide groove in the still undivided inner ring and then break the inner ring in the circumferential direction of the raceway ground in two parts. However, this can lead to plasticizations at the fracture, which complicates the necessary for the final assembly of the ball bearing (balls of the ball bearing) joining process of the two ring halves. In addition, the two ring halves must be reassembled just as aligned with each other, as they were aligned with each other when breaking. Alternatively, it is also possible to process the sections of the (common) guide groove formed by the ring halves separately from each other. Subsequently, however, both halves of the ring must be measured accurately in order to be able to be combined with each other by means of a complex assignment process.

The invention has for its object to provide a way to specify a ball bearing, which may be provided in particular for use in a fixed bearing of a steering gear, which ensures a relatively high load capacity even with a tipping load and is as simple and inexpensive to produce.

This object is achieved by a ball bearing according to claim 1 and by a method for producing such a ball bearing according to claim 12. A fixed bearing for a steering gear and a steering gear for a motor vehicle with such a bearing are subject of claims 9 and 10. The subject of claim 11 is also a steering system with a steering gear according to the invention. Advantageous embodiments of the ball bearing according to the invention and thus the fixed bearing according to the invention, the steering gear according to the invention and the steering system according to the invention are subject matters of the dependent claims and / or emerge from the following description of the invention.

An inventive ball bearing comprises at least one inner bearing shell and an outer bearing shell, each having at least one guide groove for receiving and guiding balls of the ball bearing, wherein the inner bearing shell and / or the outer bearing shell comprises at least two partial shells, each of which has a separate guide groove or forms a portion of a (common) guide groove. According to the invention, such a ball bearing is characterized in that the partial shells are connected to one another via preferably force-locking and / or positively locking connection means (detachable and preferably re-connectable).

In a method according to the invention for producing such a ball bearing it is provided that the partial shells of the inner bearing shell and / or the outer bearing shell are processed in the connected state to form the guide groove (s) and / or an outer or an inner bearing surface of the ball bearing. According to the invention, it is accordingly provided to process the split shell (s) provided in the divided but firmly connected state by the connecting means, in particular the (respective) guide groove and / or an inner bearing surface (in a split inner bearing shell) or a outer bearing surface (at a shared outer bearing shell) of the ball bearing form. Consequently, the particularly precisely (finely) to be machined functional surfaces of the shared provided (s) bearing shell (s) of the ball bearing can be processed in an advantageous manner contiguous, whereby in comparison to the known separate processing of non-contiguous sub-shells a complex subsequent measurement of the sub-shells and their Orientation to each other can be avoided, as compared to the known procedure, in which the split provided (s) shells (divided) only after the (fine) processing divided, the complex alignment of the fracture surfaces to each other and possible problems due to plasticizations the breakage point can be avoided.

Such a method for producing a ball bearing can have a particularly advantageous effect if at least one guide groove of at least one of the bearing shells of at least two partial shells, which consequently each provide a section of this guide groove, is formed. This may in particular be the case with a single-row ball bearing.

While (fine) processing of the split bearing shell (s) is provided according to the invention in the contiguous state of the subshells, it can preferably be provided that the subshells are (at least partially) subsequently detached from one another in order to mount the ball bearing and in particular to the balls to position within the guide grooves of the cups. Subsequently, the partial shells can be connected to each other again by means of the connecting means.

In this way, a relatively simple assembly and a ball bearing according to the invention is possible in which the inner bearing shell and / or the outer bearing shell advantageously has guide grooves with relatively large shoulders, whereby a correspondingly high axial load capacity of the ball bearing can be achieved.

A ball bearing according to the invention thus enables the realization of a high axial load capacity, at the same time a relatively easy manufacturability of the ball bearing is possible. Since a high axial load capacity with a good load capacity of the ball bearing even at a relatively high tipping load, as in the operation of a basically from the DE 10 2009 054 655 A1 , of the DE 10 2008 040 673 A1 , of the EP 2 836 416 B1 and the EP 2 836 417 B1 known steering gear can occur, an inventive ball bearing is suitable for use in a fixed bearing of such a steering gear in an advantageous manner.

Such an inventive bearing for a steering gear then includes a ball bearing according to the invention, wherein the inner bearing shell is provided for receiving a pinion shaft of the steering gear, and the outer bearing shell is received in a bearing sleeve. Such a bearing according to the invention further comprises a pivot ring which has an outer ring and an inner ring, which are pivotally connected to each other via one or more torsion bars, wherein the inner ring is connected to the bearing sleeve (which is to include an integral and in particular one-piece design) and the outer ring is provided for storage of the fixed bearing in a housing of the steering gear.

In a preferred development of a ball bearing according to the invention, an embodiment of the subshells and / or the connecting means may be provided such that the subshells can be connected to each other in only one (single) rotational orientation (about the rotational axis of the ball bearing). In this way it can be ensured that the subshells after loosening each other and a renewed connection with each other in the context of assembly of the ball bearing again have exactly the same Drehausrichtung to each other, which have exhibited them in a contiguous state in a previous processing.

In a further preferred embodiment of a ball bearing according to the invention can be provided that the connecting means are integrated into the partial shells or constitute an integral part of the partial shells. This can u.a. It must be avoided that separate connection means must be handled during installation. This advantage of a ball bearing according to the invention is fundamentally independent of the described advantage, which results from a continuous (fine) machining of the functional surfaces (guide grooves, bearing surfaces).

An advantageous possibility for realizing such a ball bearing according to the invention with integrated connecting means is that a first of the partial shells forms a preferably annular, in particular coaxially arranged with respect to the axis of rotation of the ball bearing projection which contacts an inner or outer peripheral surface of a second of the partial shells longitudinal axial overlapping. In this way, a pairing of relatively large contact surfaces can be realized by which a backlash-free as possible cohesion of the partial shells can be positively influenced. Also, connecting means formed in this way can provide for an automatic alignment of the partial shells in the radial direction with respect to the axis of rotation as a result of the extension or attachment of the extension of the first partial shell into or onto the second partial shell.

A connection effect can be realized in an advantageous manner in that the extension of the first sub-shell and the peripheral surface of the second sub-shell have cooperating threads. The partial shells can thus be screwed together. This preferably takes place until they abut each other directly in the axial direction, so that further insertion or attachment or screwing is thereby limited. Such a stop can also serve directly to a well-defined Drehrerichtung the sub-shells to define each other in the connected state.

As an alternative or in addition to such a screw connection, there is also the possibility of dimensioning the extension of the first subshell and the peripheral surface of the second subshell cooperating therewith such that an interference fit is formed. In an exclusively based on a press fit connection effect of the recorded in the receiving opening extension a precisely defined Drehausrichtung the sub-shells to each other in the connected state, for example, be achieved in that the extension of the first sub-shell has a radially outward or inward projection, which in a complementary Recess which is formed in the cooperating with the extension peripheral surface of the second sub-shell, engages. Of course, there is also the possibility that such a projection is formed by the peripheral surface, while the extension has a mating recess.

The connecting means may further comprise a connecting sleeve which contacts an inner or outer circumferential surface of the sub-shells longitudinally overlapping. The connecting sleeve can only be intended to be used in the context of the production of a ball bearing according to the invention and possibly also in the context of a mounting of a fixed bearing according to the invention, without this being part of the ready-mounted fixed bearing. Alternatively, there is also the possibility that the connection sleeve is part of the ball bearing according to the invention. In this case, their inner or outer circumferential surface can also serve in particular as an inner or outer bearing surface of the ball bearing. In particular, in the latter case, a connection of the connecting sleeve with the partial shells as described can be based on a threaded connection. Preferably, however, it is provided that the connecting sleeve forms an interference fit with the partial shells.

In a further preferred embodiment of a ball bearing according to the invention can be provided that the first sub-shell forms the entire inner or outer bearing surface of the ball bearing. It can thereby be achieved that the corresponding inner or outer bearing surface, which may constitute a functional surface of the ball bearing which must be (finely) machined (e.g., honed and / or ground), may be advantageously formed without a parting line. Furthermore, it can then be provided that, in the context of a method according to the invention, this functional surface of the first subshell is (finally) processed even before the first subshell is connected to the second subshell, in order then to process a further functional surface, in particular a guide groove.

In a preferred embodiment of a ball bearing according to the invention it can be provided that the inner bearing shell comprises at least and preferably exactly two partial shells and the outer bearing shell is formed in one piece. This allows a particularly advantageous manufacturability for the ball bearing and thus the fixed bearing according to the invention can be realized. A "one-part design" of one and in particular of the outer bearing shell is understood according to the invention to mean that the associated guide groove is (completely) formed in a one-piece component. This should not exclude that other components are connected to this component, which can be assigned to the corresponding bearing shell.

An inventive steering gear, which is provided for a steering system of a motor vehicle, comprises at least one gear, meshing therewith a screw pinion (in particular screw pinion) and a screw pinion comprising the screw pinion shaft, the Schraubritzelwelle is mounted on one side of the Schraubritzel in a fixed bearing according to the invention and wherein the outer ring of the pivot ring of the fixed bearing is mounted directly or indirectly and preferably immovably in a housing of the steering gear.

A steering system according to the invention comprises at least one steering gear according to the invention as well as a steering motor rotationally drivingly connected to the screw pinion shaft. The gear of the steering gear can also be rotatably or rotationally drivingly connected to a steering shaft, in particular a steering column, the steering system. The steering system according to the invention can be designed, in particular, as a power steering system in which a supporting torque can be generated by means of the steering motor, so that a steering torque to be applied by a driver of a motor vehicle comprising the power steering system to the steering column for steering the motor vehicle is reduced. Alternatively, it is also possible to form the steering system in such a way that the entire steering torque required for steering is generated by the steering motor.

The invention also relates to a motor vehicle with a steering system according to the invention.

The indefinite articles ("a", "an", "an" and "an"), in particular in the patent claims and in the description generally describing the claims, are to be understood as such and not as numerical words. Corresponding to this concretized components are thus to be understood that they are present at least once and may be present more than once.

• 1: ein erfindungsgemäßes Lenkgetriebe in einer Seitenansicht;
• 2: einen Längsschnitt durch das Lenkgetriebe entlang der Schnittebene II - II in der 1;
• 3: das Festlager des Lenkgetriebes gemäß den 1 und 2 in einer Ansicht von vorne;
• 4: einen Längsschnitt durch das Festlager gemäß der 3;
• 5: das erfindungsgemäße Kugellager des Festlagers gemäß den 3 und 4 in isolierter Darstellung in einem Längsschnitt;
• 6: eine alternative Ausgestaltungsform eines erfindungsgemäßen Kugellagers in einem Längsschnitt; und
• 7: eine weitere alternative Ausgestaltungsform eines erfindungsgemäßen Kugellagers in einem Längsschnitt.

The invention will be explained in more detail with reference to an embodiment shown in the drawings. In the drawings shows:

• 1 a steering gear according to the invention in a side view;
• 2 : A longitudinal section through the steering gear along the cutting plane II - II in the 1 ;
• 3 : the bearing of the steering gear according to 1 and 2 in a view from the front;
• 4 a longitudinal section through the fixed bearing according to the 3 ;
• 5 : the ball bearing of the fixed bearing according to the invention according to the 3 and 4 in an isolated representation in a longitudinal section;
• 6 an alternative embodiment of a ball bearing according to the invention in a longitudinal section; and
• 7 : Another alternative embodiment of a ball bearing according to the invention in a longitudinal section.

The 1 and 2 show the essential components of a steering gear according to the invention for a steering system of a motor vehicle. This includes a housing 1 , within which a gear wheel 2 and one with the gear 2 combing screw pinion 3 are stored. The sprocket 3 and one the sprocket 3 comprehensive screw pinion shaft 4 are integrally formed in the form of a screw.

The gear 2 is firmly on an output shaft 5 (see. 1 ) of the steering gear attached. This output shaft 5 , In the illustrated embodiment, a toothing for a secure rotationally fixed connection with the gear 2 can, for example, mesh with a trained as a rack at least in a section handlebar, whereby this performs a translational movement, which can be translated in a known manner via Radlenkhebel (not shown) in a pivoting movement of steered wheels (not shown) of the motor vehicle. At the output shaft 5 but it may also be a steering column of the power steering system, which is connected to a steering wheel and acts via a steering pinion on the handlebar.

The screw pinion shaft 4 has a drive end, via which it is connectable to the output shaft of a steering motor, not shown (for example, an electric motor). In the area of this drive-side end is the Schraubritzelwelle 4 by means of a first bearing in the housing 1 stored. This storage is as a fixed bearing according to the invention 6 formed, which pivoting the Schraubritzelwelle 4 around a pivot axis 7 (see. 1 and 3 ) allows. This pivoting causes a deflection of the drive end opposite end, free end of the Schraubritzelwelle 4 that there by means of a floating bearing 8th in a corresponding receptacle of the housing 1 is stored. This floating bearing 8th is designed so that it is the result of the pivoting of the screw pinion shaft 4 resulting deflection of this free end allows.

Both the fixed camp 6 as well as the floating bearing 8th each comprise a pivot bearing in the form of a ball bearing 9 . 10 , In inner bearings of these ball bearings 9 . 10 are the corresponding sections of the screw pinion shaft 4 stored while outer bearing shells of the ball bearings 9 . 10 in each case a storage device 11 . 12 are stored, in turn, in corresponding receptacles of the housing 1 are included. The storage devices 11 . 12 are constructively designed so that in the case of the fixed camp 6 the pivoting of the screw pinion shaft 4 around the pivot axis 7 and in the case of the floating bearing 8th the deflection of the free end of the Schraubritzelwelle 4 enable.

For this purpose, the storage device comprises 11 of the fixed camp 6 a bearing sleeve 13 with a circular cross section, the inside in a first longitudinal section of the ball bearing 9 and in a second longitudinal section an inner ring 15 a swivel ring 14 receives. The inner ring 15 of the swivel ring 14 is with the interposition of a support disk 19 rotatably and axially secured within the bearing sleeve 13 stored, with the inner ring 15 with the interposition of a washer 20 on the outer bearing shell 26 of the rolling bearing 9 supported. The swivel ring 14 includes next to the inner ring 15 another outer ring 16 , This outer ring 16 is over two torsion bars 17 (see. 1 and 3 ) with the inner ring 15 connected. The outer ring 16 , the inner ring 15 and the torsion bars 17 are for example in one piece and formed for example of spring steel.

An axial position securing of the ball bearing 9 on the screw pinion shaft 4 occurs with the interposition of a pressure piece 21 by means of a screw 22 that is in an internal thread that fits into the corresponding end of the pinion shaft 4 is integrated, is screwed. An axial position assurance of the outer ring 16 of the swivel ring 14 inside the case 1 done by means of a screw ring 23 having an external thread, which in a corresponding internal thread of the housing 1 is screwed.

The two torsion bars 17 form the pivot axis 7 out to the the outer ring 16 relative to the inner ring 15 is pivotable. The torsion bars 17 and thus the pivot axis 7 However, do not run through the center of the swivel ring 14 and thus the cross section of the screw pinion shaft 4 , but radially offset thereto (see. 3 ). The pivot axis 7 thus does not cut the longitudinal axis 18 the screw pinion shaft 4 , Due to the radial offset of the torsion bars 17 to the center of the swivel ring 14 becomes the pivot axis 7 near the outer circumference of the screw pinion shaft 4 shifting, thereby reducing the formation of reaction moments that arise as a result of when tooth meshing of screw pinion 3 and gear 2 resulting Verzahnungskräfte in conjunction with the distance of the line of action of these teeth forces of the pivot axis 7 result or could be reduced or avoided. For the fullest possible avoidance of the reaction moments is provided that the pivot axis 7 lies within that tangential plane that in the point of contact of the two partial or rolling circles of gear 2 and sprockets 3 is trained.

The torsion bars 17 of the swivel ring 14 not only allow pivoting of the outer ring 16 to the inner ring 15 and thus the screw pinion shaft 4 relative to the gear 2 or the housing 1 but at the same time cause the spring force by which the sprocket 3 the screw pinion shaft 4 in the toothing of the gear 2 is pressed in order to achieve the lowest possible backlash and thus a correspondingly low noise during operation of the steering gear, especially in the so-called Wechsellenken. This spring force results from the fact that during assembly of the steering gear, the Schraubritzelwelle 4 far as a result of contact with the gear 2 deflected, that is sufficient torsion of the torsion bars 17 gives, whereby the elastic restoring moments resulting from the torsion of the torsion bars 17 result, contrary to this deflection of the screw pinion shaft 4 act and thus this against the gear 2 apply.

The integration of the fixed camp 6 in the steering gear therefore sees a relatively small (eg, by 0.7 °) spring-loaded inclination of the ball bearing 9 or from its longitudinal axis 18 relative to the outer ring 16 of the swivel ring 14 or to its longitudinal axis. This can cause a considerable tilting load of the ball bearing 9 result, which in principle negative for the load capacity and thus the life of such a ball bearing 9 effect. To this negative influence of the tilting load on the bearing capacity of the ball bearing 9 To compensate is provided, the height of the shoulders of the outer bearing shell 26 and the inner bearing shell 27 trained guide grooves 28 and thus the overlap of the guide grooves 28 concerning the balls 29 of the ball bearing 9 to train relatively large. This relatively large overlap results in a relatively narrow annular gap between the outer race 26 and the inner bearing shell 27 of the ball bearing 9 is trained. This relatively narrow gap would be an assembly of the ball bearing 9 prevent in one embodiment in a conventional construction with both one-piece outer bearing shell and one-piece inner bearing shell. According to the invention, such an assembly is made possible by the fact that, in the present exemplary embodiment, the inner bearing shell 27 from two part shells 30 is trained. Therefore, during assembly of the ball bearing 9 first the outer bearing shell 26 and a first of the subshells 30 the inner bearing shell 27 be positioned to each other, that this sub-shell 30 preferably as coaxially as possible within the outer bearing shell 26 is arranged. Then the balls can 29 , preferably directly in combination with a Kugelkä 31 , in the from the outer bearing shell 26 trained guide groove 28 as well as in the of the first part shell 30 trained section of the guide groove 28 the inner bearing shell 27 to be ordered. Subsequently, the second sub-shell 30 to be assembled. In the assembled state, it is provided that the two partial shells 30 directly against each other support and thereby a substantially gap-free transition of the two sections, which together the guide groove 28 the inner bearing shell 27 training, is achieved.

A cohesion of the two subshells 30 in the ball bearing according to 1 to 5 is by means of connecting means in the form of a connecting sleeve 24 covering the inner peripheral surfaces 25 the partial shells 30 longitudinal axial (over almost the entire width) contacted overlapping, realized. The connection sleeve 24 is dimensioned in terms of their outer diameter so that they after insertion into the part of the shells 30 the inner bearing shell 27 trained central receiving openings 33 with the inner bearing shell 27 forms a press fit by the outer diameter of the connecting sleeve 24 to a defined extent larger than the inner diameter of the receiving openings 33 is provided. An insertion of the connecting sleeve 24 into the receiving openings 33 can be realized solely by force, ie by pressing. There is the additional possibility of creating a temporary difference in body temperature of the connecting sleeve 24 on the one hand and the partial shells on the other 30 the inner bearing shell 27 on the other hand, the force necessary for an insertion of the connecting sleeve 24 into the receiving openings 33 is necessary to reduce (also largely).

The connecting means of the ball bearing according to the invention 9 in the embodiment according to the 1 to 5 as a connecting sleeve 24 are formed, serve on the one hand, during assembly of the fixed bearing 6 the ball bearing 9 to be able to handle as a coherent unit. After an integration of the fixed camp 6 in the steering gear, the connecting means can then be removed again, because then a cohesion of the ball bearing 9 is secured by the integration described in the steering gear. However, embodiments are also possible in which the connecting means even after integration of the respective fixed camp 6 remain mounted in an associated steering gear.

The connecting means further serve, in the context of a method according to the invention, to produce a ball bearing according to the invention 9 by simplifying these sub-shells 30 connect to each other, while at least one functional surface of (provided for example as vorgedrehte blanks) partial shells 30 and in particular, the common guide groove formed by them 28 (post-) edited and in particular ground.

The 6 and 7 show alternative embodiments of inventive ball bearings 9 , in particular for integration into a fixed warehouse 6 according to the 3 and 4 for a steering gear of a steering system according to the 1 and 2 can be provided.

In these two embodiments, it is provided that a first ( 30a ) of the subshells 30 an annular, coaxial with the axis of rotation 18 of the ball bearing 9 extending extension 32 trains, for a connection between the subshells 30 in a complementary receiving opening 33 The second ( 30b ) of the subshells 30 engages and thereby an inner peripheral surface 25 the second subshell 30b longitudinally axial (ie along the axis of rotation 18 extending) overlapping contacted. It can be provided that the extension 32 along the axis of rotation 18 over the entire width of the second partial shell 30b extends, as in the 6 is shown. In this embodiment, it is also provided that the entire inner bearing surface of the ball bearing 9 from the first part shell 30a is trained.

In the embodiment according to the 7 On the other hand, it is provided that the extension 32 the first part shell 30a along the axis of rotation 18 only over a portion of the width of the second subshell 30b extends and the inner bearing surface of the ball bearing 9 to a (larger) part of the first part shell 30a and to a (smaller) part of the second subshell 30b is trained. For this purpose, the inner surfaces of the two partial shells 30 the same diameter as possible.

For the embodiment of a ball bearing according to the invention 9 according to the 6 is provided, a connection effect between the extension 32 and the cooperating with this inner peripheral surface 25 the second subshell 30 to achieve through the formation of a press fit, while at the ball bearing 9 according to the 7 the extension 32 the first part shell 30a an external thread 34 and the cooperating inner peripheral surface 25 the second subshell 30b a matching internal thread 34 trains, a screwing of the two partial shells 30 allow for connection with each other.

Of course, there is also the possibility of the ball bearing 9 as it is basically in the 6 is shown to provide a threaded connection, while a connection between the partial shells 30 at a ball bearing 9 as it is basically in the 7 is shown, is realized by means of a press fit.

LIST OF REFERENCE NUMBERS

1

casing

2

gear

3

Sprockets

4

Schraubritzelwelle

5

output shaft

6

fixed bearing

7

swivel axis

8th

movable bearing

9

Ball bearings of the fixed camp

10

Ball bearing of the floating bearing

11

Storage device of the fixed storage

12

Bearing device of the floating bearing

13

bearing sleeve

14

swivel

15

Inner ring of the swivel ring

16

Outer ring of the swivel ring

17

torsion

18

Longitudinal axis of the screw pinion shaft / ball bearing

19

support disc

20

washer

21

Pressure piece

22

screw

23

screw ring

24

connecting sleeve

25

inner peripheral surface of a partial shell

26

outer bearing shell of a ball bearing

27

inner bearing shell of a ball bearing

28

guide groove

29

Ball of a ball bearing

30

Partial shell of a bearing shell

30a

first part shell

30b

second subshell

31

ball cage

32

extension

33

receiving opening

34

(Internal / external) thread

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009054655 A1 [0006, 0007, 0018]
• DE 102008040673 A1 [0007, 0018]
• EP 2836416 B1 [0007, 0018]
• EP 2836417 B1 [0007, 0018]

Claims (14)

Ball bearing (9) having an inner bearing shell (27) and an outer bearing shell (26), each having at least one guide groove (28) for receiving and guiding balls (29) of the ball bearing (9), wherein the inner bearing shell (27) and / or the outer bearing shell (26) comprises at least two partial shells (30), each of which forms a separate guide groove (28) or a section of a guide groove (28), characterized in that the partial shells (30) are interconnected by means of connecting means , Ball bearing (9) according to Claim 1 characterized by an embodiment of the partial shells (30) and / or the connecting means such that the partial shells (30) can be connected to one another in exclusively a rotational orientation. Ball bearing (9) according to Claim 1 or 2 , characterized in that the connecting means are integrated in the partial shells (30). Ball bearing (9) according to Claim 3 , characterized in that a first (30a) of the subshells (30) forms an extension (32) which contacts an inner or outer peripheral surface (25) of a second (30b) of the subshells (30) longitudinally overlapping. Ball bearing (9) according to Claim 4 , characterized in that the extension (32) of the first sub-shell (30a) and the peripheral surface (25) of the second sub-shell (30b) have cooperating threads (34). Ball bearing (9) according to one of the preceding claims, characterized by a connecting sleeve (24) which contacts an inner or outer circumferential surface (25) of the partial shells (30) so as to overlap longitudinally axially. Ball bearing (9) according to one of Claims 4 to 6 , characterized by a dimensioning of the extension (32) and / or the connecting sleeve (24) on the one hand and with this / these cooperating peripheral surface (25) on the other hand such that a press fit is formed. Ball bearing (9) according to one of Claims 4 to 7 , characterized in that the first partial shell (30a) and / or the connecting sleeve (24) forms the entire inner or outer bearing surface of the ball bearing (9). Fixed bearing (6) for a steering gear with a ball bearing (9) according to one of the preceding claims, wherein the inner bearing shell (27) for receiving a pinion shaft (4) of the steering gear is provided and the outer bearing shell (26) in a bearing sleeve (13). is received, and with a pivot ring (14) having an outer ring (16) and an inner ring (15) which are pivotally connected via one or more torsion bars (17), wherein the inner ring (15) with the bearing sleeve (13). is connected and the outer ring (16) for supporting the fixed bearing (6) in a housing (1) of the steering gear is provided. Steering gear for a steering system of a motor vehicle with a gear (2), a meshing Schraubritzel (3) and a screw pinion (3) comprising Schraubritzelwelle (4), wherein the Schraubritzelwelle (4) on one side of the Schraubritzels (3) in a Fixed bearing (6) according to Claim 10 is mounted and wherein the outer ring (16) of the pivot ring (14) of the fixed bearing (6) is mounted directly or indirectly in a housing (1) of the steering gear. Steering system with a steering gear according to Claim 10 and a steering motor rotatably connected to the Schraubritzelwelle (4) of the steering gear. Method for producing a ball bearing (9) according to one of the Claims 1 to 9 , characterized in that the partial shells (30) of the inner bearing shell (27) and / or the outer bearing shell (26) are machined in the connected state to the guide grooves and / or an outer bearing surface and / or an inner bearing surface of the ball bearing (9 ) train. Method according to Claim 12 , characterized in that the partial shells (30) are subsequently released from each other to mount the ball bearing (9). Method according to Claim 13 , characterized in that the partial shells (30) are connected to each other again by means of the connecting means, after the balls (29) in the of the inner bearing shell (27) and the outer bearing shell (26) formed guide grooves (28) have been arranged.

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