Sliding constant velocity ball joint

Abstract

The sliding constant velocity ball joint (1) comprises at least an outer joint part (2) having a first axis of rotation (4) extending along an axial direction (3) and having a number of outer ball tracks (5) and a number of outer centerlines (6), an inner joint part (7) having a number of inner ball tracks (8) and a number of inner centerlines (9), a number of torque transmitting balls (10) which are assigned to one another and which form track pairs (11) and in which the torque transmitting balls (10) are guided, respectively, in the outer ball tracks (5) and the inner ball tracks (8), and a cage (12) having a number of cage windows (13) for receiving one or more of the balls (10). The centerlines (6, 9) extend along the ball tracks (5, 8) from a first end region (14) along the axial direction (3) to a second end region (15). The centerlines (6, 9) of each track pair (11) each extend at a tilt angle (16) inclined in a radial direction (17) and a twist angle (18) inclined in a circumferential direction (19).

Description

[Technical field]

[0001] The present invention relates to a sliding constant velocity ball joint, which (hereinafter also referred to as joint) can be mounted in particular on lateral or longitudinal shaft systems of motor vehicles. In particular, the sliding constant velocity ball joint is used in floating joint shaft systems, in which a sliding constant velocity ball joint is arranged at each end of a torque transmission shaft. In particular, such joint shaft systems can be used in the region of the rear axle of rear-wheel drive motor vehicles. [Prior art documents] [Patent documents]

[0002] [Patent Document 1] DE 10 2007 010 352(A1) Summary of the Invention [Problem to be solved by the invention]

[0003] In a sliding constant velocity ball joint, the inner joint part is axially displaceable relative to the outer joint part. In the case of a sliding joint, the total displacement distance (i.e. the maximum distance the inner joint part can be displaced relative to the outer joint part) is in particular at least 5 millimeters.

[0004] At least some of the outer ball tracks and at least some of the inner ball tracks can have an inclination angle (inclined radially) (in any orientation) relative to the axis of rotation, or a twist angle (inclined circumferentially) (in any orientation) relative to the axis of rotation, or both. Alternatively, they can have no track inclination angle, i.e. they can run parallel to the axial or rotational axis. When the joint is in a straight position or arrangement (i.e. when the inner joint part is not bent relative to the outer joint part), in the case of a sliding constant velocity ball joint, the inner joint part can be displaced along a common axis of rotation relative to the outer joint part, so that these axes of rotation remain coaxially arranged with respect to one another. Displacement is also possible when the joint is bent.

[0005] In particular, the ball track base (i.e. in the case of each outer ball track, the area of ​​each ball track which is at the greatest distance from the axis of rotation, and in the case of each inner ball track, the area of ​​each ball track which is at the smallest distance from the axis of rotation of the inner joint part) or the centre line of each ball track along the displacement distance (path of the centre point of the ball as it moves along the ball track) is respectively at a (approximately) constant radial distance from the axis of rotation (in the case of a tilt angle of zero degrees). However, designs of sliding constant velocity ball joints are also known in which the ball track base or centre line is not at a constant distance from the axis of rotation (in the case of a tilt angle other than zero degrees). Here, the distance from the axis of rotation is in particular the same for (only) opposing ball tracks, but is not constant over the displacement distance or along the ball track.

[0006] When the inner joint part is displaced relative to the outer joint part, the balls move (e.g. roll, slide, slide, etc.) in the ball tracks, guided by the tracks. Ideally, the cage moves only half the length of the displacement distance of the inner joint part relative to the outer joint part. No relative rotation occurs between the inner joint part, the outer joint part, and the cage in the circumferential direction. Therefore, in order for the ball tracks to tilt in the axial direction, it is necessary for the cage to have a cage window that is wide enough so that the balls can be displaced in the circumferential direction when the joint parts are displaced relative to each other in the axial direction.

[0007] When the inner joint part is bent, it is pivoted from a straight position (where the first axis of rotation of the outer joint part and the second axis of rotation of the inner joint part are arranged coaxially with each other) to a bent position (deviation from) where the first axis of rotation of the outer joint part and the second axis of rotation of the inner joint part form a bent angle (deviation from zero degrees).

[0008] The sliding constant velocity ball joint considered in this case comprises at least an outer joint part with a first axis of rotation extending along the axial direction and with a number of outer ball tracks and a number of outer centerlines, an inner joint part with a number of inner ball tracks and a number of inner centerlines, a number of torque transmission balls guided in the outer and inner ball tracks, which are assigned to each other and form track pairs, and a cage with a number of cage windows for accommodating one or more of these balls. Each centerline extends along the ball track from a first end area (of the joint or of the corresponding joint part) along the axial direction to a second end area (of the joint or of the corresponding joint part). The centerlines of each track pair extend in opposite directions, respectively with an inclination angle inclined to the radial direction and a twist angle inclined to the circumferential direction.

[0009] A joint of this kind is known from US Pat. No. 5,399,623, in which the ratio of twist angle to tilt angle is 5:3.

[0010] Known sliding constant velocity ball joints can generate noise (clicking noise) when turning large corners. The noise is caused by the change in the contact points of the balls at the respective cage windows. This phenomenon can be exacerbated in combination with a large clearance between the windows and the balls in the ball cage (large clearance fits).

[0011] It is known that reducing the clearance between the window and the balls can eliminate this problem, i.e. the resulting noise. Therefore, the fit between the cage window and the balls can be designed as a nominal fit or an intermediate fit. However, a more precise fit is detrimental to the efficiency and lifespan of the sliding constant velocity ball joint.

[0012] There is a continuing need for improvements in sliding constant velocity ball joints.

[0013] The object of the present invention is therefore to at least partially solve the aforementioned problems, in particular to propose a sliding constant velocity ball joint which generates as little or as little noise as possible during operation and which is free as far as possible from restrictions in terms of efficiency or service life. [Means for solving the problem]

[0014] A sliding constant velocity ball joint having the features according to claim 1 contributes to solving these problems. Advantageous developments are the subject matter of the dependent claims. The features recited in the claims can be combined in any technically feasible manner and may be supplemented by the illustrative technical content and details of the figures of this specification, which disclose further embodiments of the invention.

[0015] We propose a sliding type constant velocity ball joint. This sliding type constant velocity ball joint has the following features: an outer joint part having a first axis of rotation extending along an axial direction and having a plurality of outer ball tracks and a plurality of outer centerlines (6); an inner joint part (7) having a plurality of inner ball tracks and a plurality of inner centerlines, in particular having a second axis of rotation 35; a plurality of torque transmission balls, each of which is guided in a respective one of the outer and inner ball tracks, the torque transmission balls being assigned to one another and forming a track pair; a cage having a plurality of cage windows for receiving one or more of the balls; At least the following is provided.

[0016] The centerlines of each pair of tracks extend at a radial inclination angle relative to the axial direction (or respective axis of rotation) and a circumferential helix angle relative to the axial direction (or respective axis of rotation). The centerlines extend in opposite directions.

[0017] In this sliding type constant velocity ball joint, each tilt angle has an absolute value (greater than 0 degrees) of at most 4 degrees, each twist angle has an absolute value of at least 9 degrees; Each tilt angle has an absolute value of at least 9 degrees, and each twist angle has an absolute value (greater than 0 degrees) of at most 4 degrees.

[0018] The centre line of each ball track (the path of the centre point of the ball as it moves along the ball track) extends along the axis of rotation or axial direction of each of the joint parts from a first end region (where the ball track begins) to a second end region (where the ball track terminates).

[0019] The ball tracks or centre lines extending along the circumferential direction can also be represented in an unfolded state, i.e. in a two-dimensional flat image rather than in space, in which case the ball tracks or centre lines inclined at an inclination angle are projected onto a flat image, in particular in which the centre lines extend as straight lines.

[0020] In particular, the ball tracks extend at a radially inclined (constant) inclination angle 16 (also referred to as pitch angle) relative to the axial direction (or relative to the first axis of rotation in the case of the outer centerline and relative to the second axis of rotation in the case of the inner centerline) while the ball tracks extend at a circumferentially inclined (constant) twist angle (also referred to as track twist angle) relative to the axial direction (or relative to the first axis of rotation in the case of the outer centerline and relative to the second axis of rotation in the case of the inner centerline).

[0021] Each of the ball tracks of a track pair extends in an opposite direction, i.e., both the tilt and twist angles of their respective outer centerlines extend in the opposite direction to the tilt and twist angles of their respective inner centerlines.

[0022] In particular, the absolute value of the tilt angle is the same for all ball tracks.

[0023] In particular, the absolute value of the twist angle is the same for all ball tracks.

[0024] It has been found that the claimed ranges of inclination and twist angles allow a significant reduction in the noise that would otherwise occur. In particular, it is possible to ensure that the balls do not leave the contact surfaces on one side of the cage window and therefore remain in permanent contact with them. At the same time, the contact surfaces on the other side of the cage window are rarely or not changed at all. In particular, the contact surfaces are prevented from changing during a stationary operating mode of the vehicle, for example during forward movement. However, a change in the contact surfaces may occur, for example when the direction of rotation is reversed after the vehicle has come to a standstill, but this does not pose a problem in such cases.

[0025] By considering various boundary conditions (speed of the sliding constant velocity ball joint, torque transmitted through the sliding constant velocity ball joint, drive direction, turning angle of the sliding constant velocity ball joint, cage window clearance, etc.), it was possible to identify angle values ​​for the tilt angle and twist angle at which the above-described problems were solved over a continuous range of motion. By simulating the position of the rolling elements (balls) in the cage window through rotation, it was possible to determine a correlation in which the noise performance of the sliding constant velocity ball joint was significantly improved for certain combinations of tilt angle and twist angle.

[0026] In particular, this discovery relates to the subject sliding constant velocity ball joints in which the tilt and twist angles are constant over the path of the ball track.

[0027] The aforementioned combinations of tilt and twist angles can be used, particularly for constant velocity ball joints where, due to the kinematics of the joint, the cage may lose contact with the outer and / or inner joint parts during operation, thereby causing noise (e.g. in counter track joints).

[0028] In particular, the cage has webs along the circumferential direction between the cage windows, which are guided in a known manner via spherical contact surfaces on at least one of the outer and inner joint parts.

[0029] In the case of floating side shafts, for example, the webs are spherical on both the outer and inner diameters, so that the spherical inner joint part can form a fastener in the axial direction. In so-called long plunge joints, only the outer diameter is spherical, for example, because these joints are mounted together with fixed joints, so no fasteners are required (i.e. there is no contact between the ball of the cage and the inner part of the joint).

[0030] In particular, each centre line is a straight line, i.e. the tilt and twist angles have constant absolute values ​​along the path of the ball track.

[0031] In particular, the sliding type constant velocity ball joint has 8+2n balls (where n=0, 1, 2...), i.e. 8, 10, 12, etc. balls.

[0032] In particular, the outer ball tracks arranged adjacent to one another in the circumferential direction and the inner ball tracks arranged adjacent to one another in the circumferential direction are inclined in different directions, i.e., have opposite inclination and twist angles.

[0033] In particular, the tilt angle has an absolute value greater than zero degrees and is at most 4 degrees, preferably at most 2 degrees, particularly preferably at most 1 degree. In particular, the twist angle has an absolute value less than 20 degrees and is at most 9 degrees, preferably at most 10 degrees, particularly preferably at most 11.5 degrees.

[0034] Alternatively, the tilt angle has an absolute value less than 20 degrees, and is at most 9 degrees, preferably at most 10 degrees, and particularly preferably at most 11.5 degrees. In particular, the twist angle has an absolute value greater than zero degrees, and is at most 4 degrees, preferably at most 2 degrees, and particularly preferably at most 1 degree.

[0035] When designing a sliding constant velocity ball joint, it should be noted that, in particular, the larger the tilt angle, the larger the installation space in the radial direction of the sliding constant velocity ball joint becomes (significantly) and the (significant) restriction is imposed on the amount of sliding allowance in a given installation space. It should also be noted that, in the case of a large twist angle, the installation space in the radial direction increases only slightly and the displacement element is only restricted less in a given installation space.

[0036] Therefore, a smaller tilt angle and a larger twist angle are preferred.

[0037] In particular, when each tilt angle has an absolute value of at most 4 degrees, the absolute value of each twist angle is at most 18 degrees, preferably at most 16 degrees, particularly preferably at most 14 degrees or at most 12.5 degrees. In particular, the twist angles have an absolute value of at most 10 degrees, preferably less than 9.5 degrees.

[0038] In particular, (when each tilt angle has an absolute value of at most 4 degrees) the absolute value of each tilt angle is at most 2 degrees, preferably at most 1 degree or at most 0.2 degrees to 0.8 degrees.

[0039] According to a preferred embodiment, the sliding constant velocity ball joint has a tilt angle of 0.5 degrees (tolerance less than 10%) and a twist angle of 12 degrees (tolerance less than 5%).

[0040] In particular, the tilt angle is determined as a function of the maximum deflection angle that occurs during the specified operation of the sliding constant velocity ball joint. If the maximum deflection angle is less than 12 degrees, the tilt angle is 0.5 degrees (with a tolerance of less than 20%). If the maximum deflection angle is greater than 12 degrees (and less than, for example, 24 degrees), the tilt angle is 1 degree (with a tolerance of less than 20%).

[0041] In particular, each ball contacts a corresponding ball track at two contact points and is disposed at a contact angle with respect to the base of the ball track in a cross section aligned with the extension of the corresponding centerline, the contact angle being between 38 degrees and 44 degrees, in particular in the range of 40 degrees to 42 degrees.

[0042] In particular, the first contact angle of the outer ball track and the second contact angle of the inner contact track differ from each other by at least 1 degree in absolute value, preferably by 2 degrees in absolute value.

[0043] In particular, the inner joint part is displaceable in the axial direction relative to the outer joint part by at least 5 millimeters, preferably by at least 10 millimeters or at least 20 millimeters.

[0044] Further, a motor vehicle is proposed comprising at least one constant velocity sliding ball joint as proposed herein. In particular, the constant velocity sliding ball joint is proposed for use in passenger cars.

[0045] A vehicle is proposed which comprises a drive unit and each wheel, in which at least one constant velocity sliding ball joint, such as the above mentioned constant velocity sliding ball joint, is designed to transmit torque from the drive unit to the wheel.

[0046] Any discussion of constant velocity ball joints is particularly applicable to automotive applications, and vice versa.

[0047] In particular, in the claims and in the restatements of these claims, the indefinite articles ("ein", "eine", "einer", "eines") are intended to be understood as such, rather than as numerals, and therefore the correspondingly introduced terms or elements are intended to be understood as occurring at least once, but in particular as possibly occurring several times.

[0048] For the avoidance of doubt, ordinal numbers used herein ("first," "second," etc.) are primarily intended to distinguish between several similar objects, values, or steps; i.e., these ordinal numbers do not necessarily define any dependency or ordering of these objects, values, or steps relative to one another. If a dependency or ordering is necessary, this will either be set forth herein or will be apparent to those of skill in the art upon inspection of the actually described configuration. Where an element may occur more than once ("at least one"), a description of one of those elements may, but does not necessarily, apply equally to all or some of those elements.

[0049] The present invention and technical background will be described in more detail below with reference to the accompanying drawings. It should be noted that the detailed embodiments do not intend to limit the present invention. Unless otherwise specified, it is possible to extract partial features of the technical contents described in the drawings and combine them with other components and the knowledge of this specification. It should be noted that the drawings and the ratios shown in the drawings are merely schematic. [Brief description of the drawings]

[0050] [Figure 1] 1 shows a plan view of a car. [Diagram 2] FIG. 2 is a longitudinal cross-sectional view of a constant velocity ball joint in a straight arrangement. [Diagram 3] FIG. 3 is a longitudinal sectional view of the sliding constant velocity ball joint in FIG. 2 in a bent position. [Figure 4] 3 is a vertical sectional view of an outer joint portion of the sliding type constant velocity ball joint in FIGS. 1 and 2. FIG. [Diagram 5] FIG. 3 is a side view of an inner joint portion of the sliding type constant velocity ball joint in FIGS. 1 and 2. [Figure 6] FIG. 5 is a cross-sectional perspective view of the outer joint portion in FIG. 4. [Figure 7]FIG. 6 is a cross-sectional perspective view of the inner joint portion in FIG. 5. [Figure 8] 1 shows a schematic diagram of the tilt and twist angles of the ball track. [Figure 9] 1 shows cross-sectional views of the ball tracks, arranged transversely to the direction of their respective centerlines. [Figure 10] FIG. 1 is a schematic side view of a ball arrangement in a known sliding type constant velocity ball joint. [Figure 11] 1 is a schematic side view of a ball arrangement in a known sliding type constant velocity ball joint having a small clearance between the balls and the cage window. FIG. [Figure 12] 4 is a schematic side view showing the arrangement of balls in one of the sliding type constant velocity ball joints shown in FIGS. 2 and 3. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0051] Figure 1 is a schematic top view of a motor vehicle 27. The motor vehicle 27 comprises a drive unit 28 (engine) and a gearbox 30. Torque is transmitted from the drive unit 28 via the gearbox 30 to several linkages 31, 32. In the area of ​​the front axle (here in the upper part of the figure) two side shaft mechanisms 31 are shown. One side shaft mechanism 31 (right in Figure 1) is linked to the gearbox 30 via a differential 33.

[0052] Torque is transmitted from the gearbox 30 to each shaft 34 via a differential 33 or via a sliding constant velocity ball joint 1 of the other lateral shaft mechanism 31 (left in Figure 1) having an outer joint part 2, a ball 10 and an inner joint part 7, and from there to another sliding constant velocity ball joint 1 or a constant velocity (fixed) joint connected to the wheels 29.

[0053] Further alternatively or additionally, torque can be transmitted from the gearbox 30 via a sliding constant velocity ball joint 1 to a longitudinal shaft mechanism 32. The torque is transmitted via the longitudinal shaft mechanism 32 to a (rear axle) differential 33. The torque is transmitted via the (rear axle) differential 33 to the respective side shaft mechanisms 31. Each side shaft mechanism 31 is provided with two constant velocity ball joints 1, which are connected to each other by respective shafts 34.

[0054] FIG. 2 shows a longitudinal section of the sliding constant velocity ball joint 1 in a straight arrangement. FIG. 3 shows a longitudinal section of the sliding constant velocity ball joint 1 in FIG. 2 in a bent arrangement. FIG. 4 shows a longitudinal section of the outer joint part 2 of the sliding constant velocity ball joint 1 in FIG. 1 and FIG. 2. FIG. 5 shows a side view of the inner joint part 7 of the sliding constant velocity ball joint 1 in FIG. 1 and FIG. 2. FIG. 6 shows a cross-sectional perspective view of the outer joint part 2 in FIG. 4. FIG. 7 shows a cross-sectional perspective view of the inner joint part 7 in FIG. 5. FIG. 8 shows a schematic diagram of the inclination angle 16 and the twist angle 18 of the ball tracks 5, 8. FIG. 2 to FIG. 8 are explained together below.

[0055] The sliding constant velocity ball joint 1 comprises an outer joint part 2 having a first axis of rotation 4 extending along an axial direction 3 and having an outer ball track 5 and an outer centerline 6, an inner joint part 7 having a second axis of rotation 35 and having an inner ball track 8 and an inner centerline 9, a plurality of torque transmitting balls 10 forming track pairs 11 and guided about associated outer ball track 5 and inner ball track 8, and a cage 12 having a plurality of cage windows 13 for receiving one or more of these balls 10.

[0056] The inner joint part 7 is displaceable relative to the outer joint part 2 in the axial direction 3 .

[0057] Figure 2 shows a straight arrangement of the sliding constant velocity ball joint 1 with a coaxial arrangement of the first rotation axis 4 and the second rotation axis 35. Figure 3 shows a bent arrangement in which the inner joint part 7, i.e. the second rotation axis 35, is pivoted by a bend angle 26 with respect to the outer joint part 2, i.e. the first rotation axis 35.

[0058] The cage 12 has webs 36 between the cage windows 13 along the circumferential direction 19, which are guided in known manner on the outer joint part 2 via spherical contact surfaces 37. The webs 36 are not shown in the cross-sectional views of Figures 2 and 3, since they are behind the balls 10 along the circumferential direction 19, but are only indicated.

[0059] The sliding type constant velocity ball joint 1 has eight balls 10 .

[0060] The centerlines 6, 9 of each track pair 11 respectively extend at an inclination angle 16, i.e. inclined radially 17 relative to the axial direction 3 (or respective axis of rotation 4, 35), and extend at a twist angle 18, i.e. inclined circumferentially 19 relative to the axial direction 3 (or respective axis of rotation 4, 35). The centerlines 6, 9 respectively extend in opposite directions.

[0061] The sliding type constant velocity ball joint 1 has a tilt angle 16 of 0.5 degrees and a torsion angle 18 of 12 degrees.

[0062] The centre line 6, 9 of each ball track 5, 8 (the path of the centre point of the ball 10 during its movement along the ball track 5, 8) extends along the axis of rotation 4, 35 or axial direction 3 of the joint parts 2, 7 respectively, from a first end region 14 (where the ball track 5, 8 begins) to a second end region 15 (where the ball track 5, 8 ends).

[0063] The ball tracks 5, 8 or centre lines 6, 9 extending along the circumferential direction 19 can also be represented in an unfolded state, i.e. in a two-dimensional planar image rather than in space (see FIG. 8). In that case, the ball tracks 5, 8 or centre lines inclined with a tilt angle 16 are projected onto the flat image. Centre lines 6, 9 with a constant tilt angle 16 or a constant twist angle 18 have a straight line path, i.e. the tilt angle 16 and twist angle 18, respectively, do not change in absolute value along the path of the ball tracks 5, 8.

[0064] The outer ball tracks 5 and the inner ball tracks 8, which are arranged adjacent to each other in the circumferential direction 19, are inclined in different directions, i.e., have opposite inclination angles 16 and twist angles 18.

[0065] In FIG. 8, the top left diagram shows the ball tracks 5, 8 as viewed along the axial direction 3 or as viewed along the respective rotation axes 4, 35 of the joint parts 2, 7. The centre lines 6, 9 extend at an incline relative to the axial direction 3. The top right diagram shows the path of the ball tracks 5, 8 or of the centre lines 6, 9 in a side view of the joint parts 2, 7, where the centre lines 6, 9 extend in the plane of the diagram. The centre lines 6, 9 are inclined to the axial direction 3 by an inclination angle 16. The bottom left diagram shows the ball tracks 5, 8 or of the path of the centre lines 6, 9 in a plan view or in an unfolded state, i.e. in a two-dimensional plan view. The centre lines 6, 9 are inclined to the axial direction 3 by a torsion angle 18.

[0066] On the one hand, the ball tracks 5, 8 extend at a constant inclination angle 16 (also referred to as pitch angle) inclined in a radial direction 17 relative to the axial direction 3 (or relative to the first axis of rotation 4 in the case of the outer centerline 6 and relative to the second axis of rotation 35 in the case of the inner centerline 9). At the same time, the ball tracks 5, 8 extend at a constant twist angle 18 (also referred to as track twist angle) inclined in a circumferential direction 19 relative to the axial direction 3 (or relative to the first axis of rotation 4 in the case of the outer centerline 6 and relative to the second axis of rotation 35 in the case of the inner centerline 9).

[0067] The ball tracks 5, 8 of a track pair 11 each extend in an opposite direction, i.e., both the tilt angle 16 and twist angle 18 of their respective outer centerlines 6 extend in the opposite direction to the tilt angle 16 and twist angle 18 of their respective inner centerlines 9.

[0068] In Figures 6 and 7 a cross section through the respective joint parts 2, 7 is taken such that the respective upper ball tracks 5, 8 are cut along the ball track base 25. The joint parts 2, 7 are therefore shown rotated by a twist angle 18 compared to the views of Figures 2 to 4.

[0069] Figure 9 shows a cross section 22 of the ball tracks 5, 8, arranged transversely to the direction 21 of their respective centre lines 6, 9. Please refer to the description of figures 2 to 8.

[0070] Each ball 10 contacts a corresponding ball track 5, 8 at two respective contact points 20 which are disposed at contact angles 23, 24, respectively, with respect to a ball track base 25 in a cross section 22 arranged transverse to the extension direction 21 of the corresponding centre lines 6, 9. The contact angles 23, 24 are approximately 40 degrees, with the first contact angle 23 of the outer ball track 5 differing from the second contact angle 24 of the inner contact track 8 by approximately 2 degrees.

[0071] Fig. 10 shows, in a schematic side view, the arrangement of balls 10 in a known sliding type constant velocity ball joint 1. Fig. 11 shows, in a schematic side view, the arrangement of balls 10 in a known sliding type constant velocity ball joint 1 in which the clearance between the balls 10 and the cage window 13 is small. Figs. 10 and 11 will be explained together below. Please refer to Figs. 2 to 9.

[0072] The views of Figures 10 and 11 (as well as the view of Figure 12) show the ball 10 viewed along the circumferential direction 19. The second axis of rotation 35 is also shown in each case.

[0073] The balls 10 are located in the cage windows 13 between the outer ball track 5 and the inner ball track 8. During operation of the sliding constant velocity ball joint 1, depending on various boundary conditions, the balls 10 will either change their contact points 38 at the respective cage windows 13 or the balls 10 will be fixed by the ball tracks 5, 8 and the cage 12 will continue to move. Such an effect may be amplified in combination with a large clearance between the cage windows 13 and the balls 10 in the cage 12 (large clearance fit).

[0074] It is known to eliminate this problem, i.e. the resulting noise, by reducing the clearance between the cage window 13 and the ball 10 (see FIG. 11).

[0075] Figure 12 shows in a schematic side view the arrangement of the balls 10 in the sliding type constant velocity ball joint 1 according to one of Figures 2 and 3. Please refer to the description of Figures 2 to 11.

[0076] It has been found that the proposed ranges of tilt angle 16 and twist angle 18 achieve a significant reduction in noise that might otherwise occur. In particular, it is possible to ensure that the ball 10 does not move away from the contacts 38 (contact surfaces) on one side of the cage window 13 and thus remains in permanent contact with them, while the contacts 38 on the other side of the cage window 13 are changed less or not at all. [Explanation of symbols]

[0077] 1. Sliding constant velocity ball joint 2 Outer joint part 3 Axial Direction 4 (First) Rotation Axis 5 Outer ball track 6 Outer center line 7 Inner joint part 8 Inner Ball Track 9 Inner center line 10 Ball 11 Truck vs. 12 Cage 13 Cage Window 14 First end region 15 Second end region 16 Tilt angle 17 Radial 18 Twist angle 19 Circumferential direction 20 Contacts 21 Route Directions 22 Section 23 First Contact Angle 24 Second Contact Angle 25 Ball Track Base 26 Turning Point 27 Automobiles 28 Drive unit 29 Wheels 30 Gearbox 31 Side shaft mechanism 32 Forward and backward shaft mechanism 33 Differential device 34 Shaft 35 Second Rotation Axis 36 Web 37 Contact surface 38 Contacts

Claims

1. A sliding type constant velocity ball joint (1), an outer joint part (2) having a first axis of rotation (4) extending along an axial direction (3) and having a plurality of outer ball tracks (5) and a plurality of outer centerlines (6); an inner joint part (7) having a plurality of inner ball tracks (8) and a plurality of inner centerlines (9); A plurality of torque transmitting balls (10), a plurality of torque-transmitting balls (10) which are guided in a plurality of outer ball tracks (5) and a plurality of inner ball tracks (8) which are assigned to one another and form track pairs (11), respectively, in said plurality of outer ball tracks (5) and said plurality of inner ball tracks (8); a cage (12) having a plurality of cage windows (13) for receiving one or more of said balls (10); At least said centre line (6,9) extends along said ball track (5,8) from a first end region (14) along said axial direction (3) to a second end region (15); the centerlines (6, 9) of each of the track pairs (11) each extend at an inclination angle (16) inclined radially (17) relative to the axial direction (3) and at a twist angle (18) inclined circumferentially (19) relative to the axial direction (3); The centerlines (6, 9) extend in opposite directions, each of said tilt angles (16) having an absolute value of at least 4 degrees and each of said twist angles (18) having an absolute value of at least 9 degrees; each said tilt angle (16) having an absolute value of at least 9 degrees and each said twist angle (18) having an absolute value of at most 4 degrees; Sliding type constant velocity ball joint (1).

2. A sliding type constant velocity ball joint (1) according to claim 1, The center line (6, 9) is a straight line. Sliding type constant velocity ball joint (1).

3. A sliding type constant velocity ball joint (1) according to claim 1 or 2, The balls (10) are provided in a number of 8, 10, or 12. Sliding type constant velocity ball joint (1).

4. A sliding type constant velocity ball joint (1) according to any one of claims 1 to 3, In the circumferential direction (19), adjacent outer ball tracks (5) and adjacent inner ball tracks (8) are inclined in different directions, each having an opposing tilt angle (16) and twist angle (18); Sliding type constant velocity ball joint (1).

5. A sliding type constant velocity ball joint (1) according to any one of claims 1 to 4, said absolute value of each of said twist angles (18) being at most 18 degrees when each of said tilt angles (16) has an absolute value of at most 4 degrees; Sliding type constant velocity ball joint (1).

6. A sliding type constant velocity ball joint (1) according to claim 5, the absolute value of each of the tilt angles (16) is at most 2 degrees; Sliding type constant velocity ball joint (1).

7. A sliding type constant velocity ball joint (1) according to any one of claims 1 to 6, Each of the balls (10) contacts a corresponding one of the ball tracks (5, 8) at two contact points (20); at a cross section (22) transverse to the direction (21) of extension of the corresponding center line (6, 9), the cross section (22) is disposed at a contact angle (23, 24) with respect to the ball track base (25); said contact angles (23, 24) being between 38 degrees and 44 degrees; Sliding type constant velocity ball joint (1).

8. A sliding type constant velocity ball joint (1) according to claim 7, said first contact angle (23) of said outer ball track (5) and said second contact angle (24) of said inner contact track (8) differ from each other by at least 1 degree in absolute value; Sliding type constant velocity ball joint (1).

9. A sliding type constant velocity ball joint (1) according to any one of claims 1 to 8, the inner joint part (7) is displaceable in the axial direction (3) by at least 5 millimeters relative to the outer joint part (2); Sliding type constant velocity ball joint (1).

10. A motor vehicle (27) comprising a drive unit (28) and each wheel (29), at least one constant velocity sliding ball joint (1) according to one of claims 1 to 9, designed to transmit torque from the drive unit (28) to the wheels (29), Automobiles (27).

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