DE102008024621B4 - Universal joint for a steering column of a motor vehicle - Google Patents

Abstract

A universal joint for a steering column of a motor vehicle, comprising first and second yokes (12, 13) each having two spaced-apart arms (14, 15, 16, 17), a spider (20) having pivot pins (21) facing the respective one Fork (12, 13) are rotatably mounted, and bushings (23), in each of which one of the pivot pin (21) projects and which are each held in a passage opening (24) in one of the arms (14, 15; 17) one of the joint forks (12, 13) is arranged and by a lateral surface (26) is limited, wherein the bearing of the pivot pin (21) in the bushes (23) each comprise an angular contact ball bearing whose balls (27) on one of the Rolling sleeve (23) arranged runway (28) and one on the pivot pin (21) arranged raceway (29), characterized in that the distance (a) of a respective ball (27) of the angular contact ball bearing of the lateral surface (26) of the passage opening (24 ) smaller than the diameter (d) of the K ugel (27), whereby the angular contact ball bearing as ...

Description

The The invention relates to a universal joint for a steering column of a Motor vehicle, comprising first and second joint forks, which each having two spaced apart arms, a spider with pivot pin, opposite the respective yoke are rotatably mounted, and rifles, in each one of the pivot pin projects and each in one Passage opening held are located in one of the arms of one of the joint forks and from a lateral surface is limited, the storage of the pivot pin in the bushes respectively an angular contact ball bearing comprising, whose balls on a arranged on the sleeve raceway and unroll a track arranged on the pivot pin.

Universal joints for steering columns of motor vehicles have become known in various embodiments. Such universal joints, also known as cardan joints or universal joints, are used in steering columns of motor vehicles for the articulated connection of sections of the steering shaft. For example, from the DE 1 941 975 A a universal joint for a steering column of a motor vehicle has become known, in which the universal joint pin are provided on the front side with blind hole-like recesses in which elastic buffers are arranged. These are based on the floors of the bushes receiving them axially. Only with larger Achsialkräften the end faces of the pivot pins are supported directly against the bottoms of the cans. For radial mounting of the pivot pin, a needle bearing is provided in each case, the needles roll between the pivot pin and the sleeves, which are defined in passage openings in the arms of the joint forks.

From the JP 2007 078 136 A a universal joint is known in which the radial bearings for the pivot pins in addition to the needles have a ring of rolling between the pivot pin and the sleeve balls. At low torques to be transmitted via the universal joint, the forces are additionally transmitted via the balls and at higher torques via the needles.

From the DE 2 750 854 A1 Furthermore, a universal joint is known, in which the raceways for the pivot pins rotatably supporting rolling elements are inclined relative to the longitudinal axes of the rolling elements for receiving Achsialkräften. In one embodiment, balls are described here as rolling elements, which on the one hand roll in a partially spherical raceway, on the other hand on a frustoconical raceway.

A universal joint of the type mentioned is from the DE 10 2005 019 692 A1 known. To form a radial bearing for a respective pivot pin, a needle ring from between the pivot pin and the sleeve rolling pins is used. In addition, the bearing of the pivot pin in the bush comprises an axle bearing designed as an angular ball bearing, via which the pivot pin is supported on the bottom of the bush and guided and centered axially. The disadvantage is the use of both a needle bearing and a ball bearing resulting increased manufacturing costs.

A use of both a needle bearing as a radial bearing and a ball bearing as Achsiallager is also from the JP 09 196 082 A as well as from the GB 891479 A out.

From the DE 2 219 809 A is an elaborate design of a universal joint, in which the spider is mounted relative to the joint forks on several rings of ball bearings, the balls roll between a spherical shell and a hollow spherical shell-shaped part.

The DE 32 11612 A1 describes a relatively complex design of a universal joint, wherein the spider is rotatably supported by diabolo or barrel-shaped rollers whose longitudinal axes are at an angle to the respective longitudinal axis of the spider.

A universal joint formed as a combined radial and axial bearings angular contact ball bearings for receiving the loads goes out of the US 1 604 202 A out.

From the US Pat. No. 3,620,580 goes out a rock drill in the manner of a rotary cutter. The rotary cone is mounted on a pin on various bearings, which include a ball bearing, a thrust end thrust bearing, another thrust bearing in the region of a gradation of the rotary cone and radial plain bearings on both sides of the ball bearing, between an insert of the cone cutter and the pin or an insert of the Cone cutter and an insert of the pin are formed.

task The invention is a universal joint of the type mentioned to provide, which in a simple, inexpensive and advantageous training still record relatively high loads can. According to the invention succeeds this by a universal joint with the features of claim 1.

Due to the construction according to the invention, relatively high forces can be transmitted by the balls of the angular contact ball bearing, wherein the loads occurring during normal operation of the steering column can be transmitted via the balls of the angular contact ball bearing. Advantageously, in an invent According to the invention universal joint, the normal operation in which the loads are transmitted through the angular contact ball bearings, at least up to a torque which acts between the connected to the universal joint shafts of at least 15 Nm, preferably at least 20 Nm, more preferably at least 25 Nm. In car steering columns, in particular hydraulic steering systems, caused by steering movements torques occur to usually 10 Nm.

to Recording an overload is an overload sliding stop between a respective pivot pin and the pivot pin receiving rifle available. Such overload is at an acting torque, which in normal operation exceeds occurring torque. In a system of the overload sliding stop forming Parts of each other allow sliding between these parts. The overload slide stop forms So a kind of plain bearing between the respective pivot pin and the rifle out. In the condition of the overload slide stop can be an acting torque of conveniently more than 150 Nm, preferably up to 250 Nm, recorded or transmitted. For car steering columns, in particular hydraulic steering systems, occur higher than those due to steering movements caused torques, z. B. higher torques than 10 Nm, for example, when approaching on curbs. According to currently valid Regulations must have torques until about the order of magnitude 250 Nm without breakage.

The overload sliding stop is by attaching a section of the pivot pin or one with this rigidly connected part to a portion of the box or a formed with this rigidly connected part. It can do this for example, also on the pivot pin and / or on the sleeve a separate Be determined sliding ring. It is conceivable and possible, for example also that a sliding ring between the pivot pin and the sleeve interposed is, being opposite slidably rotatable in both parts.

The Balls of angular contact ball bearing are advantageously between their careers on the rifle and spring-elastic biased on the pivot pin and center it. This bias can, for example, by an elastic bend the arms of a respective yoke are achieved. It will characterized by the arms in the passages of the arms fixed rifles, in which opposite Pins of the spider protrude towards each other. additionally or instead it is conceivable and possible, separate spring elements provide each supported on the bottom of a bush and the balls in the axial Direction of the respective pivot pin in the sense of approaching apply the center of the spider.

One in accordance with the invention trained universal joint can advantageously without noticeable play in the transmission a torque between an input and an output shaft be formed, thereby improving the steering comfort. At low transmitted torques that can actually happen approaching game approximate Be zero. Across from usual Universal joints with radial needle bearings eliminates this with a torque caused radial play due to the tolerances in the barrel diameter, Needle diameter and pin diameter.

If a caused by the applied torque, on the balls acting force exceeds the preload acting on the balls, Thus, the pivot pin begin radially relative to the longitudinal axes of the bushes to move or to pivot. This movement is limited as mentioned by overload sliding stops, whereby the maximum play of the universal joint is limited. The cans are pressing the arms of the joint forks radially on. When the torque wears off, take the arms and rifles the original axial position again.

Preferably changes the orientation of the longitudinal axis the pivot pin opposite the longitudinal axis the rifle receiving it only at one between the waves connected to the universal joint acting torque, which exceeds 10 Nm.

at a universal joint according to the invention can In normal operation, a low noise level can be achieved.

The The invention further relates to a steering column of a motor vehicle a steering shaft comprising at least two shaft parts which through a universal joint are hinged together, at least one of these two shaft parts connecting universal joint in accordance with the invention are formed. In particular, it is a hydraulic Steering system, preferably for a car. In such occur caused by steering movements of the driver Workloads that are usually in the range up to 10 Nm.

Further Advantages and details of the invention are described below explained in the accompanying drawings. In this show:

1 u. 2 highly schematic representations of possible embodiments of steering columns with at least one inventive Universal joint;

3 an oblique view of a universal joint of the invention with end portions of the connected via the universal joint shafts;

4 an oblique view of a yoke and the spider, on the pivot pin, the bushes are arranged;

5 a side view of the yoke with the spider and the mounted rifles;

6 a section along the line AA of 5 ;

7 an enlarged section of 6 ;

8th a partial section along the line BB of 5 ;

9 a partial section in a sectional plane analogous to 6 and 7 by a second embodiment of the invention;

10 a section analog 9 by a third embodiment of the invention;

11 a section analog 9 by a fourth embodiment of the invention;

12 a section analog 9 by a fifth embodiment of the invention;

13 a section analog 9 by a sixth embodiment of the invention;

14 a section analog 9 by a seventh embodiment of the invention;

15 a section analog 9 by an eighth embodiment of the invention and

16 a section analog 9 by a ninth embodiment of the invention;

17 one opposite 7 again enlarged view of the raceways of the pivot pin and the sleeve, the section of the 7 corresponds;

18 a representation analog 17 a modified embodiment of the raceway on the sleeve.

The Figures have different scales.

The 1 and 2 show in highly schematized form two possible designs of steering columns 1 , At the in 1 illustrated embodiment connects to the steering wheel 2 a first shaft part 3 the steering shaft, which has a universal joint 4 with a second shaft part 5 is connected, which is also referred to as an intermediate wave (which may contain a damper). The shaft part 5 is about a universal joint 6 with a steering column pin 7 of the steering gear in conjunction.

In the embodiment according to the 2 is between the second shaft part 5 and the steering column pivot 7 another wave part 8th available, with the shaft part 5 over a universal joint 11 connected is.

The bearings of the steering shaft and the suspension of the steering column on the chassis, which may be designed to be adjustable in a known manner, are in the 1 and 2 not shown in detail and may be formed in a conventional manner. In the shaft parts 3 and or 5 and or 8th the steering shaft can be provided for deformation in a crash sections 9 . 10 be arranged. A trained according to the invention, universal joint can in places 4 and or 6 and or 11 be used. A steering column having at least one universal joint according to the invention may also contain more shaft parts connected via universal joints.

A first exemplary embodiment of a universal joint formed in accordance with the invention is described below with reference to FIG 3 to 8th and 17 described. For example, about the universal joint 4 , which can also be referred to as a cardan joint or universal joint, which in the 1 and 2 Shaft parts shown in connection with the steering column 3 . 5 connected.

The universal joint 4 includes a first and a second yoke 12 . 13 , The in side view U-shaped joint forks 12 . 13 each have two arms 14 . 15 respectively. 16 . 17 on which of a base part 18 . 19 the yoke 12 . 13 protrude. The poor 14 . 15 respectively. 16 . 17 lie in spaced-apart, preferably approximately parallel planes (the angle which the planes enclose with each other is less than 5 °). To connect the forks 12 . 13 serves a spider 20 , which is offset by 90 ° to each other pivot pin 21 having. Of these, each of the two offset by 180 ° to each other pivot pin 21 whose longitudinal axes 22 coincide, opposite one of the two joint forks 12 . 13 rotatably mounted. For this project the pivot pins 21 each in a box 23 in an opening 24 in each arm 14 - 17 is fixed.

The cans 23 each have one of their longitudinal axis and the longitudinal axis 22 of the pivot pin 21 surrounding and substantially in the axial direction extending jacket 23a and a sleeve (with respect to the direction of the longitudinal axis 22 ) closing ground 23b , The outer diameter of the rifle 23 can z. B. 15 mm +/- 3 mm.

The rifle 23 and the passage opening 24 are coaxial with each other. Without a force acting on the universal joint torque is the pivot pin 21 coaxial with the bush 23 ,

The from the longitudinal axis 22 directed outer surface 25 of the coat 23a lies on the lateral surface 26 the passage opening 24 at. By the at least frictional connection with the respective arm 14 - 17 is the rifle 23 opposite the arm 14 - 17 held unrotatable. Preferably, further, a positive connection of the sleeve 23 opposite the arm 14 - 17 at least in the axial, from the center of the spider 20 direction away. This is here by projecting noses 35 (see. 8th ), which are formed by caulking.

For rotatably supporting the pivot pins 21 opposite the cans 23 There is a single ball-ring, whose balls are in each case 27 on the one hand on one of the rifle 23 arranged career 28 on the other hand at one of the pivot pin 21 arranged career 29 roll. For example, per ball race 10 to 12 roll 27 to be available. The balls 27 For example, they may have diameters in the range of 2.5 mm to 3 mm.

The angular contact ball bearings are in full circle with balls 27 filled, ie it is ball 27 on ball 27 in normal operation against each other arranged unstrained (full spherical).

The means of the balls 27 formed ball bearings are in the form of angular contact ball bearings. Here, the Wälzkörperkräfte in a known manner in the direction of a pressure angle 30 directed, in the longitudinal center section through the sleeve 23 and the pivot pin 21 seen between the ball through the investment points 27 at the raceways 28 . 29 running straight lines 31 and the normal to the longitudinal axis 22 is measured (cf. 7 ). The pressure angle 30 In any case, this is not equal to 0 ° and less than 90 °. A preferred range of the pressure angle 30 when no torque is applied to the universal joint, is from 35 ° to 60 °. For example, it may be about 45 °.

The pressure angle 30 defining straight lines 31 approach to the longitudinal axis 22 towards the center of the spider 20 at. Your intersection with the longitudinal axis 22 is thus closer to the center of the spider 20 as the axial area in which the angular contact ball bearing is located.

The raceways 28 . 29 make an osculation to the balls 27 out. For this they have based on the longitudinal center section through the sleeve 23 and the pivot pin 21 seen radii that are slightly larger than the sphere radius. For example, the osculation of one of the two raceways 28 . 29 , preferably the career 28 at the rifle 23 , another oscillation than the other career 29 . 28 To accommodate tolerances and the displacement of the balls in case of overload (see below) can.

For example, the radius of the raceway 28 at the rifle 23 less than 30%, preferably less than 20%, be greater than the radius of the balls 27 , To accommodate tolerances is the radius of the track 28 at the rifle 23 favorably more than 5% larger than the radius of the balls 27 ,

For example, the radius of the raceway 29 at the pivot 21 less than 20%, preferably less than 10%, be greater than the radius of the balls 27 , Conveniently, it is so much larger than the radius of the balls 27 that the barrel of bullets 27 is ensured, for example by more than 2.5% larger (formation of a "tightest osculation" with optimal Hertzian pressure).

The pivot pins 21 each have one in the axial direction of the pivot pin 21 over the region in which the angular contact ball bearing is arranged, protruding end portion 32 on, the front end of the pivot pin 21 having. The career 29 at the pivot 21 is thus in the area of the longitudinal axis 22 directed side surface of the pivot pin 21 arranged (and not on the front side).

Through this protruding end section 32 (with inlet cone) also a mounting relief is achieved and it can in the range of this end section 32 an overload sliding stopper are formed, as will be explained in more detail.

The career 28 at the respective rifle 23 connects to the central longitudinal axis 22 of the pivot pin 21 directed inner surface 33 of the coat 23a the rifle 23 with the inner surface 34 of the soil 23b the rifle 23 , The balls 27 thus lie in the corner of the box 23 between the coat 23a and the floor 23b ,

The distance a of a respective ball 27 from the lateral surface 26 the passage opening 24 is smaller than the diameter d of the ball 27 , preferably also smaller than the radius of the ball 27 , The distance a is the normal distance between the peripheral surface of the ball 27 and the lateral surface 26 measured. A respective angular contact ball bearing is in this case designed as a combined radial and thrust bearing for receiving the loads during normal operation of the steering column. Another bearing for receiving the loads in normal operation is thus between a respective pivot pin 21 and the rifle receiving it 23 not mandatory.

At a rising load, so a rising between the two shaft parts 3 . 5 applied torque, the balls can 27 along the runways 28 . 29 formed Schmiegungen shift something, whereby the longitudinal axis 22 of the pivot pin 21 from the longitudinal axis of the sleeve 23 begins to deviate. The pressure angle 30 changes here (see below).

On the balls 27 acts a bias in the axial direction of the pivot pin 21 to the center of the spider 20 directed towards or at least has such a component. In the embodiment shown, this bias is caused by a biased bias of the arms 14 . 15 ; 16 . 17 a respective yoke 12 . 13 is trained. This will be the arms 14 . 15 respectively. 16 . 17 , which have a spring elasticity, bent apart during assembly and the cans 23 with the balls 27 on stop at the raceways 29 pressed. Such a slight bending apart during assembly to an axial bias between sleeve 23 and pivot pins 21 to reach is known.

By such a bias a backlash (with low acting torque) is achieved and it starts the deviation between the longitudinal axis 22 of the pivot pin 21 and the longitudinal axis of the sleeve receiving it 23 only if by the acting torque caused by the bias, the respective ball 27 aligning power is overcome.

The bias centered the pivot pin 21 opposite the cans 23 ,

If the applied torque exceeds a predetermined value, so that an overload, there is a between the respective pivot pin 21 and the rifle receiving it 23 trained overload sliding stop effective. In the illustrated embodiment, this overload sliding stop between the end portion 32 of the pivot pin 21 and a side wall 36 a depression in the ground 23b the rifle 23 educated. Due to the gradation in the ground 23b the rifle 23 becomes one towards the longitudinal axis 22 aligned contact surface 36 formed, which is the lateral surface of the end portion 32 opposite. Without acting torque is the end portion 32 from the contact surface 36 spaced. As the torque increases (as of a certain threshold), the end section becomes increasingly close 32 to the contact surface 36 , If the torque exceeds a limit to which the range of normal operation is present, it comes to rest the end portion 32 at the contact surface 36 , From this value of the torque, the forces occurring are transmitted via the slide bearing designed in this way. The raceways 28 . 29 are no longer charged higher.

advantageously, extends the range of normal operation, to which the forces transmitted only on the angular contact ball bearings be, at least up to one over transmitted the universal joint Torque of 15 Nm, preferably at least up to 20 Nm. In practice Normal operation can be up to a torque to be transmitted from 25 Nm are designed. When the range of normal operation is exceeded is, it comes to rest the contact surfaces of the overload slide stop.

By larger dimensions the construction can the stated values of the torque are increased.

Thereby, that only the angular contact ball bearings are effective in normal operation comes it to one opposite usual Joints with needle bearings reduced friction, so a reduced Beugemoment of the universal joint is achieved.

The on the longitudinal axis 22 of the pivot pin 21 related axial area in which the on the sleeve 23 arranged career 28 is located is advantageously as Darge presents in the axial region over which the outer surface 25 of the coat 23a on the lateral surface 26 the passage opening 24 abuts (ie the axial region, over which the career 28 extends, lies between the end points of the axial region, over which the outer surface of the plant 25 of the coat 23a on the lateral surface 26 the passage opening 24 extends).

Since the coat 23a the rifle 23 essentially serves to form the seat and has no independent supporting function, the wall thickness can be measured relatively small, for example, 1 mm or less. The floor 23b the rifle 23 has in contrast to training in the state The technique does not have a resilient function with respect to the axial pressing of the balls 27 , The spring action is only through the fork 12 . 13 and / or a separate spring element, as described below achieved.

The side wall 36 and the career 28 can be manufactured with the same tool, whereby a high accuracy can be achieved.

Between a bent end portion of the shell 23a the rifle 23 and the pivot pin 21 is a lip seal 42 made of an elastic material. This has in the embodiment shown on a V-shaped configuration.

Furthermore, the bent edge of the jacket acts 23a opposite the pivot pin 21 as a gap seal.

To assemble the universal joint is a respective pivot pin 21 in the region of the passage opening 24 arranged. The rifle 23 with the balls arranged therein 27 , which are held by an introduced grease, is fed axially and pressed into the passage opening, wherein the pivot pin 21 in the box 23 is introduced. The poor 14 - 17 a respective yoke 12 . 13 are bent during assembly process accordingly to the resilient bias of the cans 23 against the balls 27 to reach. The poor 14 - 17 be supported accordingly. For positive retention of the cans 23 become the embossing noses 35 forming caulking introduced.

The floor 23b the rifle 23 may preferably be formed so thin that it, if a fallen out during assembly ball 27 between the ground 23b and the pivot pin 21 clamped, deformed to detect this deformation by a probe in the punch during pressing and monitor.

A second embodiment is in 9 shown. The difference to the previously described embodiment consists essentially in the formation of the overload sliding stop. This is in this embodiment between a portion of the outer surface of the pivot pin 21 , which is closer to the center of the spider than the angular contact ball bearing, and a contact surface 36 ' formed by a portion of the inner surface of the shell 23a the rifle 23 is formed.

The overload slide stop here forms an additional seal 42 acting gap seal.

The difference of in 10 illustrated third embodiment of the in 9 illustrated second embodiment consists essentially in the formation of the contact surface 36 '' the rifle 23 , This is in this embodiment at an inwardly rolled stop end of the shell 23a the rifle 23 educated. It can also be calibrated for tight diameter tolerances.

This in 11 illustrated fourth embodiment corresponds to the in 9 illustrated second embodiment with the difference that on the inner surface 33 of the coat 23a the rifle 23 an annular insert 37 (For example, made of plastic) is held. This limits a fat room 38 in which a grease is introduced during assembly to the balls 27 to hold before the pivot pin 21 in the box 23 with the balls held on it 27 is used.

At the in 12 illustrated fifth embodiment is a modified insert 37 present and the contact area 36 is analogous to in 10 illustrated embodiment formed. The insert part 37 (For example, made of steel) has a, in the rolled-up stop end extending leg with a bent at the end, with which it is in a paragraph in the mantle 23a intervenes. The insert part 37 is introduced before case hardening. Also a bead at the end of the coat 23a adjacent leg is possible and possible.

Also at the in 11 illustrated embodiment could be an L-shaped insert formed with a leg on the jacket 23a issue.

This in 13 illustrated sixth embodiment corresponds to the in 9 illustrated second embodiment with the difference that the balls 27 in a ball cage 39 are held as full as possible.

At the in 14 illustrated seventh embodiment, the overload sliding stop between the pivot pin 21 and one on the coat 23a the rifle 23 attached sliding ring 41 educated. This points at its the pivot pin 21 facing contact surface 36 ''' a sliding material. The supporting back can be made of steel. Such sliding materials are known, for example, in the form of bronze alloys with or without incorporated lubricant.

Such slip rings 41 could also be used in the other described embodiments. Instead of a holder on the sleeve 23 the sliding ring could also be on the pivot pin 21 ge be hold. Also between the pivot pin 21 and the rifle 23 inserted slip rings, which are rotatable relative to both parts, are conceivable and possible.

At the in 15 illustrated eighth embodiment is in contrast to the embodiments described above, an additional spring element 40 present, which on the one hand on the ground 23b the rifle 23 supported and on the other hand, the balls 27 in the axial direction of the pivot pin 21 in the direction of the center of the spider is applied towards (and this presses play). When mounting the Kreuzlenkenkees is the spring element 40 and the fork 12 . 13 biased. The relaxed state is shown by dashed lines. The spring elasticity of the arms 14 - 17 It cushions on the balls 27 ,

The spring element 40 is due to the balls 27 each near their poles (imaginary axes of rotation). As a result, the friction can be kept low.

The spring element 40 is formed in the embodiment shown as a kind of plate spring.

When in 16 illustrated ninth embodiment is the spring element 40 not only annular but as the region of the longitudinal axis 22 Covering disc formed. This has a central, for example, spherical pad. The spring element 40 can loose in the can 23 be inserted. It is thus also about the longitudinal axis 22 of the pivot pin 21 or the rifle 23 rotatable and thus can adapt to the rolling rotation speed friction.

The overload sliding stop is in the embodiments of 15 and 16 analogous to the one in 10 illustrated third embodiment. He could also analog in the 9 or 14 be formed illustrated embodiments. Also insert parts for forming a grease chamber, z. B. analogous to those in 11 and 12 illustrated inserts 37 could in the embodiments of 15 and 16 be provided.

While the figures described so far represent the state of the universal joint without acting torque shows 17 in solid lines, the state that is assumed when, due to the magnitude of the applied torque, the overload sliding stop between the pivot pin 21 and the rifle 23 becomes effective, for the first embodiment. For the other embodiments, the situation is analogous. In 17 is further for comparison purposes with dotted lines part of the wall of the pivot pin 21 and a part of the inner wall of the rifle 23 shown for the state without acting torque (the dash-dotted representation of the inner wall of the sleeve 23 for the unloaded condition is about part of the career 28 but omitted for clarity).

With an increasing acting on the universal joint torque occurs when the on the balls 27 acting bias is overcome, to a deflection of the universal joint pin 21 opposite the rifle 23 so that the longitudinal axis 22 of the pivot pin 21 opposite the longitudinal axis of the sleeve 23 is slightly pivoted. Here, the contact points of the balls change 27 at the raceways 28 . 29 and the pressure angle 30 changes. In the condition of the overload slide stop, the contact angle is reduced 30 ' on one opposite the pressure angle 30 in the unloaded state smaller value. Preferably, the pressure angle 30 ' at least 5 ° smaller than the pressure angle 30 ,

By reducing the pressure angle 30 towards the value of the pressure angle 30 ' in the state of contact with increasing load, there is a more effective transmission of the radial forces, whereby the Hertzian pressure, which on the raceways 28 . 29 and the balls 27 acts, is disproportionately increased.

Out 17 is the change in the position of the pivot pin 21 in the system state of the overload slide stop compared to the unloaded state visible. Furthermore, it can be seen that in the condition of the overload slide stop the bush 23 towards the unloaded state by a distance x in the from the center of the spider 20 directed axial direction is shifted, due to the spring elasticity of the arms 14 - 17 , With the change in the position of the pivot pin 21 and the location of the rifle 23 The positions of the balls change as well 27 opposite the raceways 28 . 29 (this change is not shown in 17 ), and thus their contact points on the raceways 28 . 29 , Also the in 17 not shown, right of the midline lying portion of the box 23 is moved in the same direction x (at another way).

The radial gap s, by which the abutment surfaces of the overload slide stop are spaced apart from each other without a torque acting on the universal joint, is preferably less than 0.3 mm and may for example be in the range of 0.1 mm +/- 0.04 mm , Until the overload sliding stopper becomes effective, only the balls are transferred 27 the torque.

In 17 is further the angle 43 eingetra to the hinge pin 21 opposite the rifle 23 can be turned until the overload sliding stop between the pivot pin 21 and the rifle 23 takes effect. This angle is preferably less than 0.5 °.

In the embodiment of 17 becomes the career path 28 the rifle 23 formed by a surface with respect to the longitudinal center section uniform continuous radius. At the closer to the center of the spider 20 located end of the career 28 There is a recess formed by a recess 44 ,

18 shows a contrast modified embodiment in that the recess 44 ' is formed by a further offset radius, the track to the running 28 forming radius (smaller than the pressure angle 30 ' ) is connected via an opposite transition radius and the raceway 28 exempts.

Various other modifications With regard to the arrangement and formation of the raceways 28 . 29 are conceivable and possible without departing from the scope of the invention.

1

steering column

2

steering wheel

3

shaft part

4

Universal joint

5

shaft part

6

Universal joint

7

Pitman pin

8th

shaft part

9

section

10

section

11

Universal joint

12

1. yoke

13

Second yoke

14

poor

15

poor

16

poor

17

poor

18

base

19

base

20

spider

21

pivot pin

22

longitudinal axis

23

rifle

23a

coat

23b

ground

24

Through opening

25

outer surface

26

lateral surface

27

Bullet

28

career

29

career

30 30 '

contact angle

31

Just

32

end

33

palm

34

palm

35

Embossing nose

36 36 '

36 ''' contact surface

37

insert

38

grease chamber

39

ball cage

40

spring element

41

sliding ring

42

poetry

43

angle

44 44 '

recess

Claims (14)

Universal joint for a steering column of a motor vehicle, comprising first and second joint forks ( 12 . 13 ), each having two spaced apart arms ( 14 . 15 ; 16 . 17 ), a spider ( 20 ) with pivot pin ( 21 ), opposite to the respective yoke ( 12 . 13 ) are rotatably mounted, and rifles ( 23 ), in each of which one of the pivot pins ( 21 ) and in each case in an opening ( 24 ) held in one of the arms ( 14 . 15 ; 16 . 17 ) one of the joint forks ( 12 . 13 ) is arranged and from a lateral surface ( 26 ) is limited, the storage of the pivot pin ( 21 ) in the cans ( 23 ) each comprises an angular contact ball bearing whose balls ( 27 ) on one of the rifle ( 23 ) arranged career ( 28 ) and one at the pivot pin ( 21 ) arranged career ( 29 ), characterized in that the distance (a) of a respective ball ( 27 ) of the angular contact ball bearing from the lateral surface ( 26 ) of the passage opening ( 24 ) smaller than the diameter (d) of the ball ( 27 ), wherein the angular contact ball bearing is formed as a combined radial and thrust bearing for receiving the loads in a normal operation of the steering column, and that for receiving overloads, an overload sliding stop between a respective pivot pin ( 21 ) and the rifle receiving it ( 23 ), wherein the overload sliding stop between a relative to the angular contact ball bearing with respect to the axial direction of the pivot pin ( 21 ) closer to the center of the spider ( 20 ) located portion of the pivot pin ( 21 ) and one to the central longitudinal axis ( 22 ) of the pivot pin ( 21 ) directed contact surface ( 36 ' ) of the rifle ( 23 ) or wherein the overload sliding stop between a in the direction of the central longitudinal axis of the pivot pin ( 21 ) directed contact surface ( 36 ) of the rifle ( 23 ), whereby the balls ( 27 ) of a respective angular contact ball bearing in each case on a track ( 29 ) of the pivot pin ( 21 ), which on a side surface of the pivot pin ( 21 ) is arranged and the pivot pin ( 21 ) one, in the axial direction of the pivot pin ( 21 ) over the axial region in which the angular contact ball bearing is arranged, protruding end portion (FIG. 32 ), and the end portion ( 32 ) of the pivot pin ( 21 ) is trained. A universal joint according to claim 1, characterized in that the bush ( 23 ) each a coat ( 23a ) and one, the rifle ( 23 ) closing in the axial direction bottom ( 23b ) having. A universal joint according to claim 2, characterized in that the balls ( 27 ) of the angular contact ball bearing each on a track ( 28 ) of the rifle ( 23 ), one to the central longitudinal axis ( 22 ) of the pivot pin ( 21 ) directed inner surface ( 33 ) of the jacket ( 23a ) with one to the center of the spider ( 20 ) directed inner surface ( 34 ) of the soil ( 23b ) connects. A universal joint according to any one of claims 1 to 3, characterized in that the distance (a) of a respective ball ( 27 ) of the angular contact ball bearing from the lateral surface ( 26 ) of the passage opening ( 24 ) smaller than the radius of the ball ( 27 ). A universal joint according to any one of claims 2 to 4, characterized in that a on the inner surface ( 33 ) of the jacket ( 23a ) held insert ( 37 ), which has a fat space ( 38 ) limited to the introduction of a fat. A universal joint according to any one of claims 1 to 5, characterized in that the balls ( 27 ) of a respective angular contact ball bearing against the pivot pin ( 21 ) ( 29 ) are biased. A universal joint according to claim 6, characterized in that the bias of the balls ( 27 ) against the career ( 29 ) of the pivot pin ( 21 ) by an axial bias of the sleeve ( 23 ) towards the center of the spider ( 20 ) or includes such bias. A universal joint according to claim 6 or 7, characterized in that each angular contact ball bearing at least one, the balls ( 27 ) of the angular contact ball bearing in the axial direction of the pivot pin ( 21 ) to the center of the spider ( 20 ) acting spring element ( 40 ), which is located on the ground ( 23b ) of the rifle ( 23 ) is supported. A universal joint according to any one of claims 1 to 8, characterized in that the pressure angle ( 30 ) of a respective angular contact ball bearing without a torque acting on the universal joint in the range between 35 ° and 60 °. A universal joint according to any one of claims 1 to 9, characterized in that the pressure angles ( 30 ) defining straight lines ( 31 ) to the central longitudinal axis ( 22 ) of the pivot pin ( 21 ) to the center of the spider ( 20 ). A universal joint according to any one of claims 1 to 10, characterized in that in a longitudinal central section through the pivot pin ( 21 ), the radius of the rifle ( 23 ) arranged career ( 28 ) for the balls ( 27 ) of the angular contact ball bearing is less than 30% larger than the radius of the balls ( 27 ). A universal joint according to any one of claims 1 to 11, characterized in that in a longitudinal central section through the pivot pin ( 21 ), the radius of the pivot pin ( 21 ) arranged career ( 29 ) for the balls ( 27 ) of the angular contact ball bearing is less than 20% larger than the radius of the balls ( 27 ). A universal joint according to any one of claims 1 to 12, characterized in that the on the sleeve ( 23 ) ( 28 ) for the balls ( 27 ) of a respective angular contact ball bearing in the axial region, in which the sleeve ( 23 ) with an outer surface ( 25 ) on the lateral surface ( 26 ) of the passage opening ( 24 ) is present. Steering column of a motor vehicle with a steering shaft, the at least two shaft parts ( 3 . 5 . 7 . 8th ), which by a universal joint ( 4 . 6 . 11 ) are hinged, characterized in that at least one two shaft parts ( 3 . 5 . 7 . 8th ) connecting universal joint ( 4 . 6 . 11 ) is designed according to one of claims 1 to 13.