• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The ball joint (200) according to the invention, in particular for a vehicle headlight that can be fixed in a joint position, comprises a joint pin (110) with a joint ball (111) and a joint shaft (112). In addition, a Gelenkpan (220) for receiving the ball joint (111) is provided, wherein the Gelenkpan (220) at least two, preferably three wings (221), which are arranged along the circumference of the Gelenkpan (220) successively and in the fixed state of the ball joint (200) on the joint ball (111) form an inner joint surface of the ball joint (200) and enclose the joint ball (111), wherein the inner joint surface in the fixed state of the ball joint (200) is formed complementary to the surface of the joint ball (111) , Furthermore, a joint sleeve (140) for receiving the joint cup (220) is provided, wherein the joint sleeve (140) at least partially surrounds the wings (221) of the joint cup (220). The ball and socket joint (200) comprises at least one control contour (146; 226) which is adapted to apply a radial contact pressure force to the joint socket (220) by a rotational movement between the joint socket (220) and the joint sleeve (140) Exercise joint ball (111) and thereby fix the ball joint (200).
    公开号:AT519058A1
    申请号:T50807/2016
    申请日:2016-09-12
    公开日:2018-03-15
    发明作者:Bachler Jörg；Hungendorfer Martin；hauer Clemens
    申请人:Zkw Group Gmbh；
    IPC主号:
    专利说明:

    ball joint
    The invention relates to a ball joint, in particular for a vehicle headlight, which can be fixed in a joint position.
    When installing a vehicle headlight in a motor vehicle, the headlight is mounted, for example, on a support frame, a body part or other component of the vehicle. The parts mentioned and the headlight itself have partly high tolerances in their dimensions, but also in the position and execution precision of the mounting units provided for mounting, such as holes, threads, alignment pins, screws, rivets, etc.
    To compensate for such tolerances, there are various concepts for mounting a vehicle headlamp in a motor vehicle, such as by using a screw having at one end a ball that can be used together with a Gelenkpan to form a ball joint. Such ball joints may be fixed to be guided in order to lock the connection at a desired position and to obtain a firm connection between the two parts connected by the ball joint.
    Ball joints according to the prior art have the disadvantage that they have low locking moments. In other words, the holding force of the fixed ball joint for some applications may be insufficient, which may occur especially in such connections between a vehicle headlight and a vehicle-mounted mounting part, since in motor vehicles, among other strong vibrations and high seasonal temperature fluctuations influence the locking force of the fixation of a ball joint can have.
    In another aspect, currently available ball joints are cumbersome to assemble. Even in maintenance situations, it may be necessary to disassemble a ball joint in its components. Prior art ball joints may have increased complexity in handling and disassembly into its component parts. As a result, the service costs can be very high. In addition, some parts of a ball joint, in particular the joint pans, often can not be removed completely non-destructive. The result may be a material weakening or fatigue, which can lead to premature wear of a reassembled ball joint.
    The invention has the object to overcome the disadvantages mentioned.
    The object is achieved on the basis of a ball joint of the type mentioned at the outset in that the ball joint comprises: a joint pin which comprises a joint ball which merges on one side into an end face of a substantially cylindrically shaped joint shaft, and a joint socket for receiving the joint ball, wherein the joint socket comprises at least two, preferably three wings, which are arranged successively along the circumference of the joint socket and in the fixed state of the ball joint on the joint ball form an internal joint surface of the ball joint and enclose the joint ball, which in the fixed state of the ball joint complementary to the surface the joint ball is formed, and a joint sleeve for receiving the joint socket, wherein the joint sleeve at least partially surrounds the wings of the joint socket, wherein the ball joint comprises at least one control contour which is arranged by a rotational movement between en the joint socket and the joint sleeve through the wings of the joint socket to exert a radial contact force on the joint ball and the ball joint can be fixed thereby.
    Under control contours are basically geometric elevations from a spatial surface or, for example, also limiting edges on a first body understood that serve to interact with associated surfaces on a second body, which are referred to here as control surfaces, or other control contours. In this case, control contours can be formed as edges, for example with triangular or rectangular cross-section, or curves, which have a straight or spatially curved course. The control contours can follow on a part of a surface of a body or along the circumference of the body or even a course that follows the circumference several times, for example in the form of a thread in which two control contours can interact with each other. In principle, therefore, a control surface can also be designed as a control contour.
    Control contours, in common with associated control surfaces, generally serve to assure a defined relative movement between the first and second bodies by sliding the control contours over the control surfaces.
    In a first aspect of the invention is achieved by at least one control contour that a contact force can be applied radially, which fixes the joint ball with the joint cup in the moored state. By means of this particularly simple measure, a force acting radially between the joint socket and the joint sleeve can be generated, which presses the joint socket onto the joint ball and a particularly high locking force of the ball joint according to the invention can be achieved.
    The invention can be further improved in that the at least one control contour is formed by a first control contour which is located on the joint sleeve, preferably in a region of the inner surface of the joint sleeve, particularly preferably in a region of the first opening of the joint sleeve. This first control contour is very easy to implement on the joint sleeve. Furthermore, the first control contour can bring about a pressing force on a joint ball, which is exerted on a first hemisphere of the joint ball.
    The first hemisphere of the joint ball refers to one half of the surface of an imaginary sphere whose surface predominantly coincides with that of the joint ball. The first hemisphere extends from the end of the joint pin on which the joint ball is arranged, or the end of the joint pin to the Equator, that is, the largest circumference of the ball transverse to the axis of the pivot, the ball of the ball.
    The second hemisphere of the joint ball extends from the equator to the beginning of the joint shaft of the pivot pin.
    The invention can be further improved in that the at least one control contour is formed by a second control contour which is located on the joint socket, preferably in a region of the outer surface of the joint socket, particularly preferably on the outer surface of the wing.
    By using the second control contour can be achieved that the joint ball is pushed in force during the fixation of the ball joint in the joint socket and thus an axially acting force is generated, that is, the geometric center of the joint ball is moved in the axial direction. This allows the Gelenkpan be very tolerant of size variations of the joint ball, which can be caused by component tolerances, but also come from different diameters of different types and sizes of the ball joint. It is clear that this can only be possible within certain reasonable limits. By pushing in a smaller joint ball compared to the nominal diameter, the clasping of the joint ball by the wings is particularly large and firm.
    However, if two control contours used for the ball joint, the joint ball can be kept centered in its geometric center in the fixation of the ball joint through these control contours. This can be advantageous when using a smaller joint ball compared to the nominal diameter, since the spatial Winkeleinstellbereich of the ball joint can thereby be greater, or a larger diameter of the joint shaft of the pivot pin can be used without the wings abut the joint shaft.
    Further, it is advantageous if the at least one second control contour is located in a region on the outer surface of the joint socket, in particular on the outer surface of the wings, which cooperates with the joint sleeve, wherein the at least one second control contour is located at one end of the wings
    A particularly high locking force of the ball joint can be achieved if at least two control contours, which are formed by first and second control contours, are formed on the ball joint according to the invention, in particular if second control contours are formed on each wing.
    Further, the second control contour can cause a contact force on a joint ball which is exerted on a second hemisphere of the joint ball and the at least one second control contour can thereby ensure a particularly firm determination or fixation of the ball joint according to the invention.
    If at least two different control contours are formed in the form of first and second control contours in the ball joint, pressure forces can be exerted on both hemispheres in each case, which can result in a particularly firm fixation of the ball joint. In other words, a two-part force can be applied to both hemispheres. It is understood that the first and second control contours may each include one or more first and second control contours.
    It is particularly advantageous if the at least one second control contour is located at one end of the wings and is preferably located in an area whose length is 20% of the length of the wings, particularly preferably 10% of the length of the wings.
    It is also particularly advantageous if the at least one second control contour in the assembled state of the ball joint is located in a plane transverse to the installation direction and their radial distance from a first radius at a first angle of rotation about the imaginary longitudinal axis of the joint socket to a second radius in a second Angle of rotation about the imaginary longitudinal axis of the socket changes. The first radius is smaller than the second radius. Furthermore, the at least one second control contour preferably proceeds further to a third radius in a third angle of rotation about the imaginary longitudinal axis of the joint socket. In addition, the third radius preferably corresponds to the first radius, or the third radius corresponds to the second radius. Preferably, the first angle of rotation with respect to the second angle of rotation corresponds to the same amount as the second angle of rotation with respect to the third angle of rotation. Due to the aforementioned embodiment of the joint socket it is achieved that by means of a rotational movement a precisely metered force can be generated on the joint socket, which is set up to press the wings against the joint ball. A symmetrical shape of the embodiment is therefore particularly favorable, since the joint socket can be rotated in both directions about its longitudinal axis in order to fix the ball joint. The symmetrical shape is achieved in that the first radius in the first rotation angle corresponds to the third radius in the third rotation angle. If the third radius in the third rotation angle corresponds to the second radius in the second rotation angle, then the embodiment is asymmetrical and only one direction of rotation is possible when fixing the ball joint. This may be required by installation instructions, but also has the advantage that the rotation of the joint socket is limited at an end stop on the joint sleeve, which can ensure that when installed the correct end position can be detected by the senses of the fitter. In contrast to the asymmetrical shape, the symmetrical shape has no such end stop, however, the center position in the second angle of rotation can be characterized by an audible and / or tactile mechanical locking and / or an optical marking.
    The fixation of the ball joint takes place particularly precisely when the ball joint comprises at least one control surface which is set up to cooperate with the at least one control contour and to press the at least one control contour against the at least one control surface. Furthermore, an axial slippage between the joint socket and the joint sleeve against the installation direction can be prevented.
    It is particularly advantageous if the at least one control surface is formed by at least one first control surface, which is preferably located in a region of the outer surface of the joint cup and particularly preferably at that end of the wing, which points in the installation direction. It can thereby be achieved that during a rotational movement between the joint sleeve and the joint socket, the at least one associated first control contour can slide particularly precisely along the control surface and consequently can follow a precise movement path for exerting a contact force.
    It is also particularly advantageous if the at least one control surface is formed by a second control surface, which is preferably located in a region of the inner surface of the joint sleeve. It can thereby be achieved that during a rotational movement between the joint sleeve and the joint socket the at least one associated second control contour can slide particularly precisely along the control surface and consequently can follow a precise movement path for exerting a contact force.
    Furthermore, it is favorable if, in the position of the second angle of rotation, the at least one second control contour has at least one tab which extends axially and at a radial distance of the second radius and is set up, by interaction with the second control surface a radial contact pressure on the articulated ball exercise. By a radial force, which is effected for example by a control contour, the tab, the joint socket can be pressed against the joint ball. The shape of the tab ensures a precise interaction with a cooperating control surface, which can produce a precisely controllable force.
    The ball joint according to the invention is particularly tolerant of inaccuracies and tolerances of the joint ball, as well as suitable for within certain limits smaller dimensions of the ball joint.
    In a further aspect of the invention it is particularly advantageous if the wings in an unobstructed state, in which an imaginary longitudinal axis of the pivot pin coincides with an imaginary longitudinal axis of the joint socket extend at least to a joint edge, wherein on the surface of the pivot pin between the Joint shaft and the joint ball which is formed along the circumference of the joint socket extending joint edge. This can be achieved that the locking torque is maximized by the maximum available surface of the ball joint is used to form the ball joint and the wings surround the ball as large as possible.
    The pivot pin can be spatially adjusted to the circumstances in an assembly, for example in a vehicle headlight and fixed in one position. To achieve this, the joint pin between the joint ball and the joint shaft on a joint edge, which defines the spatially rotatable region of the connection between the joint ball and joint socket together with the wings of the joint cup and up to the wings of the joint socket in the unadjusted state. Due to the axial length of the wings, the effective joint surface of the ball joint, which is determined by the interacting surfaces of the joint ball and the joint socket, can be optimally utilized.
    The joint edge is not limited to an actual presence of an edge running around the circumference. The hinge edge may alternatively be formed by a transition between a convex curve shape of the joint ball and a concave curve shape of a transition between the joint shaft and the joint ball. Consequently, in this case, the hinge edge is an imaginary line that runs along the circumference and describes the transition between the joint ball and the joint shaft.
    In addition, the ball joint according to the invention is characterized in that the ball joint can be easily disassembled into its individual parts, which is beneficial to the durability of the items as well as the ease of disassembly of the ball joint.
    Said pivot pins are commercially available as standard and have for example at the pivot pin on a thread. Such pivot pins can be designed such that the geometric center of the joint ball is located on the extension of the imaginary longitudinal axis of the joint shaft. It is therefore advantageous if the ball joint according to the invention supports the use of such standard goods.
    In addition, the said standard product can be designed such that the joint ball is flattened on the side facing away from the joint shaft, and preferably has a mounting recess. The mounting recess may, for example, have a mounting recess in the form of an Allen or Torx opening for receiving a corresponding screwdriver, by means of which a thread located on the hinge shaft can be screwed, for example, in a support frame, a body part or other installation component of a vehicle.
    It is also advantageous if the diameter of the joint ball is greater than the radial diameter of the joint shaft and a transition between the joint shaft and joint ball is formed by a concave surface extending along the circumference of the joint socket.
    The effective hinge surface of the ball joint can be used to particular advantage if the joint edge is formed by a sectional curve of the substantially convex surface of the joint ball and the concave surface of the transition from the joint shaft to the joint ball, as is common in standard goods.
    It is particularly advantageous if the wings of the joint socket run in their axial length beyond the joint edge and at the same time the radial distances of the wings to the imaginary axis of the joint shaft are at least not lower. By an appropriate design of the wings can be achieved that the mobility of the ball joint is limited as little as possible in a non-fixed state.
    In a further aspect, the wings have a tapering cross-section in the radial direction between the two ends in order to make assembly of the individual components of the ball joint as simple as possible. By reducing the cross-section, a flexibility of the wings is achieved, which allows the joint ball can be introduced into the joint socket without great force. This reduces, for example, the material fatigue and can ensure an increased service life of the ball joint, in particular when dismantling the ball joint several times in its individual parts.
    It is particularly favorable when the wings are pressed in the fixed state of the ball joint through the joint sleeve in each case in areas adjacent to the tapered in the radial direction cross-section of the joint ball, preferably in each case by a control contour and a control surface. This ensures that the holding force of the ball joint is particularly high, since a two-part force occurs in accordance with the foregoing.
    The invention can be further developed in the aforementioned aspect by a respective film hinge running along the circumference is formed between the two ends of the wings. By using a film hinge, a joint ball can be inserted into the joint socket even more easily, as the wings can be spread apart very easily.
    It is additionally advantageous if in each case an axially extending gap is formed on the joint socket in the unfixed state between the wings. As a result, tolerances in the diameter of the joint ball can be compensated in the joint socket. Within certain limits, even joint balls of different diameters can thereby be accommodated by one and the same ball joint, which can cost-effectively influence the complexity of the product range, as fewer variants of joint pans may be required.
    It is particularly advantageous if the joint cup is limited in the region of its wings in its outer contour by the shape of a truncated cone, the truncated cone decreases from the open ends of the wings towards the wing connecting region of the joint cup in the outer radius. The outer contour is radially outboard and limits the geometry of the joint socket and its wings. The described shape of the joint socket is favorable, since a joint sleeve can be pushed over the wings of the joint socket and pushed through the truncated cone, the joint sleeve on the joint socket or pulled, the wings of the joint socket then interact with the joint sleeve so that the wings against the joint ball are pressed. The pulling or pushing movement can be generated by the fact that the joint sleeve and the joint socket together form a rotary or bayonet-like closure which pushes the joint sleeve to the joint socket together with the latching hooks via a run-on slope or the joint socket into a first opening of the joint sleeve draws.
    A development of the ball joint according to the invention provides that the wings are connected at one end along the circumference of the joint socket continuously with each other and form a common component. This ensures that the joint socket is made in one piece and consequently the manufacturing, logistics and maintenance costs can be reduced.
    In an additional aspect of the invention, it is advantageous if the joint socket has a final end face with a central second opening, the end face being adjacent to the region of the joint socket connecting the wings. Through the opening, a mounting recess in the form of an Allen or Torx opening located in the joint ball is accessible and the mounting pin can be screwed in a vehicle-mounted bracket in the assembled state of the ball joint, for example by means of a thread which is located on the pivot pin.
    In a further aspect of the invention, provision is made for latching hooks to be formed on the region of the joint socket which connects to each other along the circumference of the joint socket, which are preferably arranged to prevent an axial slipping of the joint socket directed against the installation direction of the joint pin and / or part form a bayonet-like closure or a closure with a latching position for fixing the ball joint, wherein the bayonet-like closure is preferably formed together with the joint sleeve.
    Due to the ball joint according to the invention with a bayonet-like closure, which allows the pressing of the wings against the joint ball for fixing the ball joint, further advantages of the invention result from a simple assembly and disassembly of the individual components of the ball joint.
    It is particularly advantageous if the latching hooks are arranged along the circumference between the wings and are preferably U-shaped and preferably elastically deformable. The arrangement of U-shaped latching hook between the wings, it is possible to easily demold the workpiece during manufacture by an injection molding process, that is easy to remove from the injection mold. The u-shape is particularly suitable to form the desired function of the locking hooks as a sliding element on a ramp or run-on slope. If the latching hooks are elastically deformable, the function of latching can be easily realized at the end of the run-up slope and thus a locking of the latching hook can be achieved in an end position. Due to the elasticity of a repeated opening and closing of the lock is possible without significant wear and tear occur and consequently the maintenance of the ball joint according to the invention is particularly simple and inexpensive.
    Furthermore, it is favorable if the in-plane at least one second control contour is set up to exert an axial contact force in the direction of the imaginary longitudinal axis of the joint cup between the joint sleeve and the joint socket with the articulation sleeve and the latching hooks of the joint cup. It can thereby be achieved that the joint socket is firmly connected to the joint sleeve by an axial contact force pressing the two parts together.
    It is advantageous if the joint sleeve comprises at least one run-up slope, which is arranged along the circumference of an imaginary circle, wherein the imaginary circle is located concentrically around the first opening of the joint sleeve. The aforementioned bayonet and locking function can be particularly easily realized.
    In general, a run-up slope is understood to mean a ramp-shaped structure on a body on which a second body can slide when force is applied. Through the ramp can be a orthogonal to the linear axis or in a linear or rotary motion
    Direction of the rotation axis oriented linear motion can be effected. In other words, a run-up slope is a form of a control contour.
    Moreover, it is advantageous if the latching hook slide with an axial rotation of the joint socket with respect to the hinge sleeve on the run-on slope while axially exert a tensile force that presses the joint socket in the joint sleeve. Consequently, the aforementioned function can be realized particularly easily.
    In a particularly advantageous aspect of the invention, the ball joint can be arranged on or within a vehicle headlight and be adapted to fix the vehicle headlight in an installed position. The ball joint according to the invention is particularly suitable for connecting parts in a vehicle headlight and partly to overcome and compensate for high installation tolerances, which happens in such a way that the ball joint is fixed only after attachment of the parts to a vehicle headlight.
    In an additional aspect of the invention, a vehicle headlight, in particular for generating a high beam and / or a low beam light distribution, be provided with at least one ball joint according to the invention for installation of the vehicle headlight in a motor vehicle, wherein the ball joint connects a carrier unit located on the vehicle side with the vehicle headlight , The ball joint according to the invention is particularly suitable for fixing a vehicle headlight on a vehicle-side mount in order to compensate for the sometimes high installation tolerances.
    It is particularly advantageous if the joint socket is made of a plastic material, in particular by an injection molding process, since the shaping and demolding, that is the removal from the injection mold, the joint socket are particularly suitable.
    The invention and its advantages are described in more detail below with reference to non-limiting exemplary embodiments, which are illustrated in the accompanying drawings. The drawings show in
    1 is a perspective view from above of a first embodiment of a joint socket according to the invention,
    2 is a perspective view from above of a joint sleeve according to the invention,
    Fig. 3 is a top perspective view of the first embodiment of the
    Gelenkpan according to FIG. 1, which is arranged in the articulated sleeve according to FIG. 2,
    4 is a perspective view from below of the joint sleeve of FIG. 2,
    Fig. 5 is a perspective view from below of the first embodiment of
    Gelenkpan according to FIG. 1, which is arranged in the articulated sleeve according to FIG. 2,
    6 is a front view of a pivot pin,
    7 is a view of the cross section of the pivot pin of FIG. 6,
    8 is a perspective view of the pivot pin of FIG. 6,
    9 is a perspective view of the hinge pin of FIG. 6, which is arranged in the joint socket according to FIG. 1, FIG.
    10 is a rear perspective view of the hinge pin of FIG. 6 disposed in the socket of FIG. 1, again in the hinge sleeve of FIG. 2, in an unfixed condition. FIG.
    11 shows a detail of a cross section of the articulation pin according to FIG. 6, which is arranged in the joint socket according to FIG. 1, in an unfixed state, FIG.
    FIG. 12 is a rear perspective view of the hinge pin of FIG. 6 disposed in the socket of FIG. 1, again in the hinge sleeve of FIG. 2, in a semi-fixed condition. FIG.
    13 shows a detail of a cross section of the pivot pin according to FIG. 6, which is arranged in the joint socket according to FIG. 1, in a half-fixed state, FIG.
    14 is a rear perspective view of the hinge pin of FIG. 6 disposed in the socket of FIG. 1, again in the hinge sleeve of FIG. 2, in a fixed condition. FIG.
    FIG. 15 shows a section of a cross section of the articulation pin according to FIG. 6, which is arranged in the joint socket according to FIG. 1, in a fixed state, FIG.
    16 is a top view of the joint socket of FIG. 1,
    17 is a perspective view from above of the joint sleeve according to the invention,
    18 is a perspective view from above of a second embodiment of a joint socket according to the invention,
    19 is a perspective view from below of the joint sleeve according to the invention,
    20 is a perspective view from below of the second embodiment of the joint socket according to the invention,
    21 is a top view of the joint sleeve according to the invention,
    22 is a top view of the second embodiment of the invention Gelenkspfanne,
    23 is a bottom view of the joint sleeve according to the invention,
    FIG. 24 shows a view from below of the second embodiment of the joint socket according to the invention, FIG.
    25 is a side view in section A-A of the joint sleeve of FIG. 21,
    26 is a side view in section B-B of the joint socket according to FIG. 24, FIG.
    27 is a top view of the second embodiment of the invention Gelenkspfanne, which is arranged in the joint sleeve according to the invention in a first configuration,
    28 is a perspective view from above of the second embodiment of the joint socket according to the invention, which is arranged in the joint sleeve according to the invention in the first configuration,
    29 is a bottom view of the second embodiment of the invention Gelenkspfanne, which is arranged in the joint sleeve according to the invention in the first configuration,
    30 is a side view in section C-C of the second embodiment of the invention Gelenkspfanne and the joint sleeve of FIG. 29,
    31 is a bottom view of the second embodiment of the invention joint socket, which is arranged in the joint sleeve according to the invention in a second configuration and in which the pivot pin is used,
    32 is a side view in section D-D of the second embodiment of the invention Gelenkspfanne, the pivot pin and the joint sleeve of FIG. 31,
    33 is a top view of the second embodiment of the invention Gelenkspfanne, which is arranged in the joint sleeve according to the invention in a third configuration,
    34 is a bottom view of the second embodiment of the invention Gelenkspfanne, which is arranged in the hinge sleeve according to the invention in the third configuration,
    35 is a side view in section E-E of the second embodiment of the invention Gelenkspfanne, the pivot pin and the joint sleeve of FIG. 34,
    36 is a top view of the second embodiment of the invention joint socket, which is arranged in the hinge sleeve according to the invention in a fourth configuration,
    FIG. 37 is a bottom view of the second embodiment of the joint cup according to the invention, which is arranged in the hinge sleeve according to the invention in the fourth configuration. FIG.
    38 shows a side view in section F-F of the second embodiment of the joint socket according to the invention, the joint pin and the joint sleeve according to FIG. 37.
    In the following figures, important elements of two ball joints 100 and 200 according to the invention are shown, it being understood that not all details shown are essential to the invention and only serve to better understand the invention.
    The two embodiments of the ball joints 100 and 200 differ only in a few details of the shown Gelenkspfannen the two ball joints, so many details of the description apply to both embodiments and are therefore not repeated.
    It is clear that, in addition to the two embodiments of the ball joints 100, 200 according to the invention, further embodiments with combinations of features according to the following claims also fall within their scope of protection. Depending on the requirements, for example, by different applications consequently different features may be formed or not at different parts of a ball joint.
    1 shows an embodiment of a joint socket 120 according to the invention, FIG. 2 shows a joint sleeve 140 according to the invention and FIG. 6 shows a joint pin 110 for a ball joint 100 according to the invention.
    In Fig. 1, the joint socket 120 according to the invention is shown, which is suitable for a ball joint 100 according to the invention (shown in the following figures). The joint socket 120 may for example comprise three wings 121, which are arranged successively along the circumference of the joint socket 120 and in the fixed state of the
    Ball joint 100 on a joint ball 111 of the pivot pin 110 (shown in Fig. 6) form an inner hinge surface of the ball joint 100 and enclose the joint ball 111 which is formed in the fixed state of the ball joint 100 complementary to the surface of the joint ball 111. The wings 121 may each have a film hinge 124 to be more easily stretched and the joint ball of the ball joint 100 to take. The film hinge 124 is formed in each case between the two ends of the wings 121 along the circumference. Furthermore, the installation direction 117 of a joint pin 110 shown in FIG. 6 is shown.
    For mechanical attachment of the joint socket 120, for example in a joint sleeve, a plurality of latching hooks 123 (in this example, three latching hooks 123) may be arranged on the joint socket 120, for example with a counterpart on a joint sleeve to form a bayonet-type closure or a latch with a latching position allows a very simple assembly of the ball joint 100. This assembly may support a second opening 125 having a form of a screwdriver, for example in the form of a hexagon socket (Allen), Torx or Phillips, to allow easy rotation by a corresponding screwdriver. The installation direction 117 of a joint ball in a joint socket can be seen in the figure.
    In the example shown, the wings 121 are connected at one end along the circumference of the joint socket 120 continuously with each other and form a common component.
    The joint socket 120 has a closing end face with a centric second opening 125, the end face being adjacent to the region of the joint socket 120 connecting the wings 121.
    Furthermore, the locking hooks 123 are formed on the interconnecting region of the joint socket 120 in order to be able to prevent an axial slipping of the joint socket 120 directed against the installation direction 117 of a joint pin, which comprises a joint ball for the ball joint 100. In addition, the latching hooks 123 can form part of a bayonet-like closure for locking and for fixing the ball joint. The bayonet-like closure is formed together with a joint sleeve.
    The latching hooks 123 are arranged along the circumference between the vanes 121 and are preferably U-shaped and elastically deformable.
    The wings 121 have between the two ends of a tapered cross-section in the radial direction. In addition, in the fixed state of the ball joint 100, the wings 121 can be pressed against the joint ball by the hinge sleeve 140 shown in Fig. 2 at portions adjacent to the radially tapered cross section as shown by a control contour and a control surface, respectively.
    Furthermore, the wings 121 extend in an unadjusted state, in which an imaginary longitudinal axis 114 of the pivot pin 110 coincides with an imaginary longitudinal axis 122 of the joint socket 120, at least as far as the joint edge 113.
    The wings 121 of the joint cup 120 extend in their axial length beyond the joint edge 113 and thereby the radial distances of the inner side of the wings 121 to the imaginary axis 115 of the joint shaft 112 at least not lower.
    In addition, it is shown in this example that in the non-fixed state between the vanes 121 each have an axially extending gap can be formed.
    In addition, the joint cup 120 may be limited in the region of its wings 121 in its outer contour by the shape of a truncated cone, the truncated cone decreases from the open ends of the wings 121 toward the wing 121 connecting region of the joint cup 120 in the outer radius. This embodiment allows interaction with a joint sleeve, so that the wings can be compressed radially by this interaction.
    FIGS. 2 and 4 show a joint sleeve 140 according to the invention, in which a receptacle for the joint socket 120 is provided. The joint sleeve 140 encloses at least the wings 121 of the joint cup 6. In addition, the joint sleeve 140 may have a receptacle 143 for the latching hooks 123, run-up slopes 142 and third openings 144 for
    Pushing the locking hooks 123. The run-up slopes 142 serve to clamp the joint socket 120 with the hinge sleeve 140 by the latching hooks 123 by a rotary movement, whereby pan receptacles 145 can be radially compressed and the wings 121 can compress or in a ball joint 100 inserted in the ball joint Can push wings 121 to the joint ball and thus achieve a fixation of the ball joint 100, this aspect is not carried out in the present embodiment.
    The run-up slope 142 is arranged along the circumference of an imaginary circle, wherein the imaginary circle is located concentrically around the first opening 141 of the joint sleeve 140.
    The latching hooks 123 slide in an axial rotation of the joint cup 120 with respect to the joint sleeve 140 on the starting slope 142 and thereby exert axially a tensile force that presses the joint cup 120 into the joint sleeve 140.
    In FIG. 3 and FIG. 5, the joint socket 120 is arranged next to the joint sleeve 140 of the ball joint 100 (here without a joint ball). It can be seen that the joint socket 120 inserted into the joint sleeve 140 with the latching hooks 123 forms the bayonet-like closure, which allows a particularly simple assembly of the ball joint 100. The bayonet-like closure ensures by a rotational movement that the latching hooks 123 of the joint cup 120 along bevels 142 are pressed with the joint sleeve 140 and the resulting compound has a stable grip, even with vibrations, as often occur in the use of a vehicle headlight, robust is. A respective latching position 143 of the latching hooks 123 at the end of the ramps 142 reinforces this favorable property and will be explained in detail in the course of the following further description of Figures 17 to 38. The rotational movement can be exerted by a screwdriver which is inserted into the opening.
    FIGS. 6, 7 and 8 show a pivot pin 110 for forming the ball joint 100 according to the invention. The pivot pin 110 comprises a pivot ball 111, which merges on one side into an end face of a substantially cylindrically shaped hinge shaft 112. The shape of the hinge shaft 112 ultimately depends on the application, which function the ball joint is to exercise. Frequently, flexible fasteners by such
    Ball joint created so that attachment of the joint shaft 112 can be done for example on a support frame of a vehicle headlamp. For this it may be favorable if the hinge shaft 112 has an external thread, so that the hinge shaft 112 can be screwed to the support frame. Alternatively, an external hexagonal shape may be desired to realize, for example, a plug connection. On the outer contour elevations may be appropriate to the hinge pin 110 during assembly easy to grab or screwed with a tool can, as shown in Figure 8 in an axially narrow section of the pivot pin 110 by an approximately square cross section of the contour.
    On the surface of the hinge pin 110 between the hinge shaft 112 and the joint ball 111, a joint edge 113 extending along the circumference of the joint socket 120 may be formed.
    In addition, the pivot pin 110 has a mounting recess 116, which is for example formed to receive a screwdriver and thereby allows a rotational movement for screwing the pivot pin 110 in a support frame or for fixing in a bayonet-like closure.
    In principle, it is possible that the joint ball 111 is not located in an imaginary extension of the imaginary longitudinal axis of the pivot pin 114. This variant can be favorable for very special constructions. Often, however, a simpler shape of the pivot pin 110 is assumed, in which the imaginary longitudinal axis of the pivot pin 114 coincides with the imaginary longitudinal axis 115 of the hinge shaft 112, as illustrated in the example shown. The geometric center of the joint ball 111 is located on an extension of an imaginary longitudinal axis 115 of the joint shaft 112. Furthermore, the joint ball 111 can be flattened on the side facing away from the joint shaft 112 and have the mounting recess 116.
    In the example shown, the diameter of the joint ball 111 is greater than the radial diameter of the joint shaft 112 and a transition between hinge shaft 112 and ball joint 111 is formed by a concave surface extending along the circumference of the joint socket 120. Here, the joint edge 113 by a sectional curve of the
    Substantially convex surface of the joint ball 111 and the concave surface of the transition from the hinge shaft 112 to the joint ball 111 is formed.
    In Fig. 9, the pivot pin 110 is shown, which is arranged in the joint socket 120 to form the ball joint 100. It is the second opening 125 recognizable, through which access to the mounting recess 116 is possible.
    It will also be appreciated that the hinge cup 120 has three wings 121 that are slightly flared outwardly by respective film hinges 124 on the wings 121 for receiving the hinge pin 110 with its hinge ball 111. Furthermore, a plane 128 of the joint socket 120 can be seen, which is located in the assembled state of the ball joint 100 transversely to the recognizable in Fig. 1 mounting direction 117, and may be located in the control contours 126, with the control surfaces 147 shown in Fig. 4 on the Joint sleeve 140 can interact.
    Fig. 10 shows an assembly consisting of the pivot pin 110 and the joint cup 120, which is located in the joint sleeve 140, in a non-fixed state of the formed ball joint 100. In this example, the ball joint 100 only by turning the joint cup 120 in the joint sleeve 140 fixed by a bayonet-like closure, the two components pressed together and locks. The bayonet-like closure is formed by the latching hooks 123 and the corresponding shape of the joint sleeve 140, wherein in each case the start-up slope shown in FIG. 2 142 serves on the part of the joint sleeve 140 to press the two components together or to determine the joint cup 120 axially.
    The ball joint 100 comprises a control contour which is adapted to exert a radial contact pressure on the joint ball 111 by a rotational movement between the joint cup 120 and the joint sleeve 140 through the wings 121 of the joint cup 120, whereby the ball joint 100 can be fixed thereby.
    The control contour is formed by a first control contour 146, which is located on the joint sleeve 140, in particular in a region of the inner surface or the first opening 141 of the joint sleeve 140, wherein the first control contour 146 shown in FIG. 4 in this embodiment, only the wings 121 radially compresses and exerts no radially acting contact force on the ball joint 111. In another embodiment, this aspect of the force transmission can be configured in such a way that, in addition, an indirect contact pressure force is exerted by the articulated sleeve 140 on the articulation ball 111 by the vanes 121.
    FIG. 11 shows a section of the ball joint 100 in cross section, which runs through the axis of the pivot pin 110. It can be seen that the wings 121 of the joint cup 120 are wide open to receive the ball joint 111. It is favorable for the flexibility or flexibility of the wings, in particular for the assembly of the ball joint when introducing the joint ball 111 in the joint cup 120, when the wings 121 have a tapered cross section in the radial direction between the two ends.
    The wings 121 are then pressed in the fixed state of the ball joint 100 by the joint sleeve 140 in each case in areas adjacent to the tapered in the radial direction of the cross section of the joint ball. In the present example, the force is applied by control contours and control surfaces, as described in more detail below.
    FIGS. 12 and 13 show the previous arrangement in a half-fixed state of the ball joint 100. This semi-fixed state is achieved by slightly twisting the bayonet-type closure (about half the total twisting range of the bayonet-type closure) and the hinge sleeve 140 the conical shape of the outer contour of the joint socket 120 and the corresponding counterpart on the joint sleeve 140 is pressed against the joint socket 120, or the wings 121 are pressed against the joint ball 111. To close the vanes 121, it may be helpful if the second control contour 126 engages the counter element formed by the second control surface 147 on the pivot sleeve 140. This is illustrated in FIG. 12 and is more specifically explained in the description of the figures for FIGS. 34 and 35.
    FIGS. 14 and 15 show the previous arrangement in a fully fixed state of the ball joint 100. This fully fixed state is achieved by further twisting and locking the bayonet-type closure and pushing the joint sleeve 140 farther to the joint socket 120 and thereby the Wing 121 firmly pressed against the joint ball 111. It can be seen that the wings 121 form an inner hinge surface of the ball joint 100, which is formed in the fixed state of the ball joint 100 complementary to the surface of the joint ball 111.
    According to the invention, in the fixed state of the ball joint 100, the wings 121 enclose the joint ball 111. Furthermore, the wings 121 extend in an unadjusted state, in which an imaginary longitudinal axis of the joint pin 114 coincides with an imaginary longitudinal axis of the joint socket 122, at least as far as the joint edge 113 a mechanically particularly strong fixation of the ball joint 100 is achieved.
    The example shown for the ball joint 100 may be arranged on or within a vehicle headlight and be configured to fix the vehicle headlight in an installed position. The ball joint 100 can connect a vehicle-mounted carrier unit with the vehicle headlight.
    16 shows the joint socket 120, in which the wings 121, the second control contours 126 and the latching hooks 123 can be seen. Furthermore, a first radius 129 in a first rotational angle 130, a second radius 131 in a second rotational angle 132 and a third radius 133 in a third rotational angle 134 can be seen. The radii 129,131,133 and the rotation angle 130,132,134 are present on each of the three wings 121, wherein they are each located at an angle of 120 ° from each other about the longitudinal axis 122 of the joint cup twisted. Further, an end stop 137, in which a ball joint is fixable shown.
    FIGS. 17 to 38 show another embodiment of a ball joint 200 with its components to illustrate the mechanism for the closure of the ball joint 200 as well as the bayonet-type closure. The ball joint 200 differs from the previously shown embodiment of the ball joint 100 only in details of the joint cup 120. The other components 110,140 of the ball joint 200 are identical.
    FIG. 17 shows a joint sleeve 140 with a first opening 141 into which a joint socket 220 according to FIG. 18 and a joint pin 110 can be inserted. The first opening 141 of the joint sleeve is made round and has at three equidistant points along the circumference of the first opening 141 third openings 144 for latching hooks 223, between which arcuate guides along the circumference of the first opening 141 are located and form part of control edges can. Through the three third openings 144 for three latching hooks 223, the joint socket 220 can be pushed through with the three latching hooks 223.
    Along the circumference of the first opening 141 in the joint sleeve 140 along the circumference, starting at the third openings 144 for the latching hooks 223 each chamfers 142 are provided, which are adapted to the three latching hooks 223 against the hinge sleeve 140 upon rotation of the joint cup 220 slide the respective run-on slope 142 and engage in an end position by the chamfers 142 have ends, each comprising stepped, radial extensions 143 into which the latching hooks 223 can engage radially, as shown in detail in Fig. 21 below.
    Consequently, the run-on slopes 142 each have a radial width which radially compress the latching hooks 223 and the latching hooks 223 engage and lock only in the aforementioned expansions. For this purpose, the latching hooks 223 are U-shaped, in order to allow the latching function to be radially resilient. The outer surfaces of the joint cup 220 and of wings 221 form first control surfaces 227, which can interact with first control contours 146, which are shown below.
    In general, a run-up slope is understood to mean a ramp-shaped structure or surface on a body on which a second body can slide when force is applied. By means of the ramp, a linear movement oriented orthogonally to the linear axis or in the direction of the axis of rotation can be effected by a linear or rotary movement. In other words, a tarnish oblique is a form of a control contour.
    Under control contours are basically geometric elevations from a spatial surface or, for example, also limiting edges on a first body understood that serve to interact with associated surfaces on a second body, which are referred to here as control surfaces, or other control contours. In this case, control contours can be formed as edges, for example with triangular or rectangular cross-section, or curves, which have a straight or spatially curved course. The control contours can follow on a part of a surface of a body or along the circumference of the body or even a course that follows the circumference several times, for example in the form of a thread in which two control contours can interact with each other.
    Control contours, in common with associated control surfaces, generally serve to assure a defined relative movement between the first and second bodies by sliding the control contours over the control surfaces. In the present ball joint 200 there is a rotational movement between the joint sleeve 140, are located on the first control contours 146, and the joint cup 6, are located on the first control surfaces 227, and as shown later between second control contours 226 and second control surfaces 147. The rotation is also used in the bayonet-like closure.
    A control contour is formed by three second control contours 226 which are located on the joint cup 220, here for example in an area of the outer surface of the joint cup 220 shown in FIG. 19 and in particular on the outer surface of the blades 221.
    The second control contours 226 are located at one end of the wings 221. Particularly favorable is an area whose length is 10% of the length of the wings 221.
    The ball joint 200 has control surfaces 227, 147 configured to cooperate with control contours 146, 226 and to urge the control contours 146, 266 against the control surfaces 227, 147. Furthermore, an axial slippage between the joint socket 220 and the joint sleeve 140 against the installation direction 117 can be prevented.
    The joint socket 220 of the ball joint 200 differs from the joint socket 120 of the ball joint 100 in that the second control contours 226 are shaped differently than the control contours 126. The remaining components of the joint cup 220 correspond to those of the joint cup 120 in the second embodiment.
    The second control contours 226 are in the assembled state of the ball joint 200 shown in FIG. 26 in a plane 228 transverse to the installation direction 117 and their radial distance is from a first radius 229 at a first rotation angle 230 about the imaginary longitudinal axis 222 of the socket to a second Radius 231 at a second angle of rotation 232 about the imaginary longitudinal axis 222 of the joint socket over, as shown in Fig. 22. The first radius 229 is smaller than the second radius 231. The second control contours 226 continue to a third radius 233 at a third angle of rotation 234 about the imaginary longitudinal axis 222 of the socket over. The third radius 233 here corresponds to the first radius 229.
    The difference between the first radius 229 and the second radius 231 may be, for example, on the order of the radius of the joint ball 111.
    Advantageously, as can be seen in FIGS. 31 and 32, the wide opening of the vanes 221 in a first angular position in the first rotation angle 230, which may correspond, for example, to the tool-falling state of the joint cup 120 in production as an injection molded part. This facilitates both the assembly because of the reduced expenditure of force when inserting the joint ball 111 in the joint socket 220, as well as in the manufacture of the joint cup 220 itself by the easier mold release from the tool, that is, the removal of the workpiece from the mold.
    In the first embodiment of the ball joint 100 with the joint cup 120, the third radius 133 corresponds to the second radius 131 and in the angular position 137 follows a stop in which the latching hooks 223 have reached the respective ends of the chamfers 142 and can contact the hinge sleeve 140, as well the locking hooks 223 can relax radially in the widenings 143 and lock in place there. In this embodiment, the joint cup 220 can be rotated in both directions of rotation in the joint sleeve 140, which has guides for the latching hooks 223 with a corresponding direction of rotation, while in the first embodiment of the joint cup 120 can be rotated in only one direction of rotation in the joint sleeve 140 , The embodiment shown in Figs. 17 and 21 shows guides for rotating the hinge cup 220 counterclockwise. For both Gelenkspfannen 120, 220 corresponds to the first rotation angle 130,230 compared to the second rotation angle 132, 232 the same amount as the second rotation angle 132, 232 against the third rotation angle 134, 234. Further, in the position of the second rotation angle 132,232, the second control contours 126,226 tabs 135, 235, which extend axially and at a radial distance of the second radius 131, 231 and are arranged to exert a radial contact pressure on the joint ball 111 by interaction with the second control surface 147 in a locking position of FIGS. 14, 15 and 37, 38.
    Likewise, the second control contours 126, 226 situated in the plane 128, 228 are arranged, with the joint sleeve 140 and the latching hooks 123, 223 of the joint cup 120, 220 with the starting bevel 142, an axial contact force in the direction of the imaginary longitudinal axis 122, 222 of the joint cup between the joint sleeve 140 and the joint cup 120,220 exercise. In this case, the plane 228 located in the surface of the wings 221, as seen for example in the following in Fig. 30, with the underside of the joint sleeve 140 in contact, which closes the control surface 147, and is when sliding the locking hooks 223 on the run-up 142th strained against them. As a result, the joint socket 120,220 is fixed in the locking position in the axial direction in the joint sleeve 140.
    In Fig. 19, the joint sleeve 140 is shown. The hinge sleeve 140 includes first control contours 146 located along the circumference of the first opening 141 of the hinge sleeve 140. For this embodiment, it should be noted that the first control contours 146 serve only to compress the wings 221 after insertion of the joint ball 111 of the hinge pin 110 in the joint socket 220, but not so strong that a contact pressure by the first control contours 146 by means of the control surfaces 227th is exerted on the joint ball 111. In this embodiment, only the second control contours 226, together with the second control surfaces 147, exert the contact force on the joint ball 111 in order to achieve a fixation of the ball joint 200.
    Of course, there are also other embodiments of ball joints according to the invention which cause a force exerted by all the aforementioned control contours 146,126, 226 and control surfaces 127,227,147 on the ball joint 111 through the wings 121, 221 and are covered by the scope of the following claims.
    The control surfaces are formed by first control surfaces 227 which are located in a region of the outer surface of the joint cup 220 and in particular at that end of the wings 221, which point in the installation direction 117.
    The control surfaces are further formed by second control surfaces 226 located in an area of the inner surface of the hinge sleeve 140.
    Further, on the hinge sleeve 140 partial surfaces are formed, which along the circumference of an imaginary circular line which passes through the outer boundaries of the third openings 144 for latching hooks 223, are arranged and their inner surfaces second control surfaces 147, with second control contours 226, the are shown below, can interact. The partial surfaces are only partially formed along the circumference of the imaginary circular line to make the component lighter and less expensive. Along the circumference of the first opening 141 of the joint sleeve 140 in the axial direction, the first opening 141 widens radially and forms pan receptacles 145.
    Fig. 20 shows the hinge cup 220, wherein at the open ends of the wings 221 outer second control contours 226 with tabs 235, which may for example, as shown, additional stop elements with defined stop surfaces are arranged, which can interact with the second control surfaces 147.
    21 shows the joint sleeve 140, in which the run-on slopes 142 and the third openings 144 for latching hooks 223 can be seen.
    FIG. 22 shows the joint socket 220, in which the wings 221, the second control contours 226 and the latching hooks 223 can be seen. Furthermore, a first radius 229 in a first rotation angle 230, a second radius 231 in a second rotation angle 232 and a third radius 233 in a third rotation angle 234 can be seen. The radii 229,231,233 and the rotation angle 230, 232,234 are present on each of the three wings 221, wherein they are each located at an angle of 120 ° from each other about the longitudinal axis 222 of the joint cup twisted.
    FIG. 23 shows the joint sleeve 140, in which the socket receivers 145 and the second control surfaces 226 can be seen.
    FIG. 24 shows the joint socket 220, in which the wings 221, the second control contours 226 and the latching hooks 223 can be seen.
    FIG. 25 shows the joint sleeve 140 in a section A-A according to FIG. 21, in which the run-on slopes 142 can be seen. Furthermore, the first control contours 146, which merge into the pan receptacles 145, are shown. In addition, the second control surfaces 147 can be seen.
    FIG. 26 shows the joint socket 220 in a section B-B according to FIG. 24, in which the wings 221, the second control contours 226 and the latching hooks 223 can be seen. Further, the first control surfaces 227 are located, which are located on the outer surface of the wings 221. Further, a plane 228 of the hinge cup 220 can be seen, which is located in the assembled state of the ball joint 200 transverse to the installation direction 117, and may be located in the control contours 226, which can interact with control surfaces 147 on the joint sleeve 140.
    FIGS. 27 and 28 show the joint sleeve 140 in which the joint socket 220 is inserted. The U-shaped latching hooks 223 of the joint socket 220 are inserted into the third openings 144 for latching hooks 223 and lie with their open ends on surfaces which connect to the third openings 144 radially and are located in a plane with the beginning of the run-up slopes 142 and go over into the ramps 142. Consequently, the third openings 144 do not extend over the entire radial width of the chamfers 142, but form a latching edge 148 for the latching hooks 223. The latching hooks 223 are therefore pre-locked after insertion into the third openings 144 and the latching edge 148 by the u -shaped latching hooks 223 are inserted through the third openings 144, while the latching hooks 223 are radially compressed by the third openings 144 and relax on further passing through the third openings 144 out again by an elastic spring force and by the latching edge 148 against slipping or a withdrawal are secured. The arrangement forms such a basic position of the ball joint 200. During rotation, the latching hooks 223 slide on the chamfers 142. The hatched areas on the run-up slopes 142 indicate radially extending ramps in which the chamfers 142 axially increase the thickness of the support surface relative to the
    Surface which is located transversely to the insertion direction of the joint socket 220 in the joint sleeve 140 has.
    Likewise, the aforementioned extensions 143 of the run-on slopes 142 can be seen, which serve to engage the latching hooks 223 and prevent possible subsequent movement against the direction of the locking movement. The run-up slopes 142 are respectively bounded by said extensions and the third openings 144 of the latching hooks 223.
    FIGS. 29 and 30 show the joint sleeve 140, in which the joint cup 220 is inserted in the basic position of the ball joint 200. It can be seen that in the basic position, the second control contours 226 are rotated with the associated second control surfaces 226, so that between the second control contours 226 and the second control surfaces 147 can take place no interaction in the normal position. The first control contours 146 can also interact with the first control surfaces 227 only after rotation.
    It can also be seen that the first control surfaces 227 do not rest against the socket receivers 145, so that an expansion of the wings 221 is possible. This expansion is intended to insert a pivot pin 110 with a pivot ball into the hinge cup 220. This process is illustrated in FIGS. 31 to 32. FIG. 30 shows the joint socket 220 in section C-C of FIG. 29, wherein it can be seen that the leaves 221 are in an unexpanded state. In Fig. 29 it is shown that an imaginary circle, which extends through the second control contours 226 transverse to the installation direction 117, approximately corresponds to the first opening 141 of the joint sleeve 140, while in Fig. 31, the imaginary circle in the expanded state of the hinge socket 220 substantially larger is. FIG. 32 is a sectional view D-D of FIG. 31. FIG.
    In Fig. 33, a second, rotated position of the assembled ball joint 200, comprising the pivot pin 110, the joint cup 220 and the hinge sleeve 140 is shown. The applied twist is approximately half of the limited by the run-up slopes 142 twisting range.
    FIG. 34 shows the joint socket 220 and the joint sleeve 140, wherein in the second position of the ball joint 200, the latching hooks 223 exert an axial tensile force on the ball joint 200 by the run-on slopes 142 and pull the joint socket 220 into the joint sleeve 140. It is thus achieved that the first control contours 146 come into contact with the first control surfaces 227 in the form of control edges and can interact. The interaction causes the wings 221 to be radially urged together by the first control contours 146, as shown in FIG. In the second position, the second control contours 226, which lie in the plane 228, with portions whose radial distance corresponds to the second radius with the associated second control surfaces 147 in abutment. The final determination of the ball joint 200 is achieved when the tabs 235 interact with their stop members with the second control surfaces 147. Since the second control contour 226 has an increasing distance at a rotation about the imaginary longitudinal axis 222 of the joint cup, the wings are moved radially inwardly with increasing rotation of the joint cup 220 relative to the joint sleeve 140 and the inside of the joint cup 220 pressed against the joint ball 111. The radially acting contact force causes in this embodiment by the displacement of the joint ball 111 into the joint cup 220 in the formation of an axial component of the contact pressure. This component results in particular from the high enclosure of the joint ball 111.
    In Fig. 36, the assembled ball joint 200 comprising the pivot pin 110, the hinge cup 220 and the hinge sleeve 140 is shown in an end position of rotation. It can be seen that the latching hooks 223 are engaged in the widening of the run-up slopes 143.
    FIG. 37 shows the joint socket 220 and the joint sleeve 140, wherein in the end position of the ball joint 200, the second control contours 226 come into contact with the second control surfaces 147 and can interact. The interaction causes the vanes 221 to be pushed radially further toward each other and to the articulation ball 111 by the second control contours 226, as seen in FIG.
    List of reference numerals: 100,200 ball joint 128,228 level of the joint cup 129, 229 first radius 110 joint pin 130,230 first rotation angle 111 joint ball 131,231 second radius 112 joint shaft 132,232 second rotation angle 113 joint edge 133,233 third Radi3 114 imaginary longitudinal axis of the 134,234 third rotation angle
    Pivot pin 135,235 tab 115 imaginary longitudinal axis of the 136,236 installation direction of the
    Articulated joint socket 116 Mounting recess 137 End stop 117 Installation direction of the
    Joint pin 140 Joint sleeve 141 First opening of the 120.220 joint socket Joint sleeve 121.221 Wing 142 Starting slope 122.222 Thought longitudinal axis of the 143 Expansion of the
    Articulated cup Angle of slope 123.223 Detent hook 144 Third opening for latching hooks 124.224 Film hinge 145 Cup holder 125.225 Second opening of 146 First control contour
    Joint cup 147 second control surface 126.226 second control contour 148 latching edge 127.227 first control surface
    权利要求:
    Claims (26)
    [1]
    claims
    A ball and socket joint (100, 200), in particular for a vehicle headlight which can be fixed in a joint position, characterized by a pivot pin (110) which comprises a joint ball (111) which is formed on one side in an end face of a substantially cylindrically shaped joint shaft (112 ), and a joint cup (120, 220) for receiving the joint ball (111), wherein the joint cup (120, 220) at least two, preferably three wings (121,221) arranged along the circumference of the joint cup (120,220) arranged successively and in the fixed state of the ball joint (100, 200) on the joint ball (111) form an internal joint surface of the ball joint (100, 200) and enclose the joint ball (111), which in the fixed state of the ball joint (100, 200) is complementary to the surface of the joint ball (111). is formed, and a hinge sleeve (140) for receiving the Gelenkpan (120, 220), wherein the hinge sleeve (140) at least partially Wing (121, 221) of the joint cup (120,220) encloses, wherein the ball joint (100, 200) at least one control contour (146; 126, 226), which is set up by a rotational movement between the joint socket (120, 220) and the joint sleeve (140) through the wings (121, 221) of the joint socket (120, 220) a radial contact force on the joint ball (111 ) and the ball joint (100, 200) can be fixed thereby.
    [2]
    2. ball joint (100, 200) according to claim 1, characterized in that the at least one control contour (146, 126, 226) by a first control contour (146) is formed, which is located on the joint sleeve (140), preferably in an area of inner surface of the joint sleeve (140), particularly preferably in a region of the first opening (141) of the joint sleeve (140).
    [3]
    3. ball joint (100, 200) according to claim 1 or 2, characterized in that the at least one control contour (146; 126, 226) by a second control contour (126, 226) is formed, which is the Gelenkpan (120,220) located, preferably in a portion of the outer surface of the hinge cup (120,220), more preferably on the outer surface of the wings (121, 221).
    [4]
    4. ball joint (100, 200) according to claim 3, characterized in that the at least one second control contour (23) at one end of the wings (121,221) is located and preferably in a region whose length is 20% of the length of the wings (121, 221 ), more preferably 10% of the length of the wings (121.221).
    [5]
    5. ball joint (100, 200) according to claim 3 or 4, characterized in that the at least one second control contour (126,226) in the assembled state of the ball joint (100,200) in a plane (128, 228) is located transversely to the installation direction (117) and their radial distance from a first radius (129,229) at a first angle of rotation (130,230) about the imaginary longitudinal axis (122,222) of the socket to a second radius (131,231) at a second angle of rotation (132,232) about the imaginary longitudinal axis (122,222) wherein the first radius (129, 229) is smaller than the second radius (131, 231), and the at least one second control contour (126, 266) preferably further to a third radius (133, 233) at a third angle of rotation ( 134, 234) passes around the imaginary longitudinal axis (122, 222) of the joint socket, the third radius (133, 233) preferably corresponding to the first radius (129, 229), or the third radius (133, 233) to the second radius (131, 231) and Preferably, the first rotation angle (130,230) compared to the second rotation angle (132, 232) corresponds to the same amount as the second rotation angle (132, 232) compared to the third rotation angle (134, 234).
    [6]
    6. Ball joint (100, 200) according to claim 1, characterized in that the ball joint (100, 200) comprises at least one control surface (127, 227, 147) which is set up with the at least one control contour (146; 226) and to urge the at least one control contour (146, 126, 226) against the at least one control surface (127, 227, 147) and preferably further against axial slippage between the hinge cup (120, 220) and the hinge sleeve (140) to prevent the installation direction (117).
    [7]
    7. Ball joint (100, 200) according to any one of claims 1 to 6, characterized in that the at least one control surface (127,227; 147) by at least a first control surface (127,227) is formed, which preferably in a region of the outer surface of the Gelenkpan (120,220) and more preferably located at that end of the wings (121, 221) pointing in the installation direction (117).
    [8]
    8. Ball joint (100, 200) according to one of claims 1 to 7, characterized in that the at least one control surface (127, 227; 147) is formed by a second control surface (147), which preferably in a region of the inner surface of the joint sleeve (14). 140).
    [9]
    9. ball joint (100, 200) according to claim 5 and 8, characterized in that in the position of the second angle of rotation (132,232), the at least one second control contour (126, 226) at least one tab (135,235), which is axially and in a radial Distance of the second radius (131, 231) extends and is adapted to exert by interaction with the second control surface (147) a radial contact pressure on the joint ball (111).
    [10]
    10. ball joint (100, 200) according to one of claims 1 to 9, characterized in that the wings (121, 221) in an unadjusted state in which an imaginary longitudinal axis (114) of the pivot pin (110) with an imaginary longitudinal axis (122,222 ) of the joint socket (120, 220) coincides, at least on the joint edge (113), on the surface of the joint pin (110) between the joint shaft (112) and the joint ball (111) along the circumference of the joint socket (120, 220) extending hinge edge (113) is formed.
    [11]
    11. ball joint (100, 200) according to claim 10, characterized in that the wings (121, 221) of the joint socket (120, 220) extend in its axial length beyond the joint edge (113) and the radial distances of the inner side of the wings (121, 221) to the imaginary axis (115) of the joint shaft (112) are at least not lower.
    [12]
    12. ball joint (100, 200) according to one of claims 1 to 11, characterized in that the wings (121, 221) between the two ends have a tapered cross-section in the radial direction.
    [13]
    13. ball joint (100, 200) according to claim 12, characterized in that the wings (121, 221) in the fixed state of the ball joint (100, 200) through the joint sleeve (140) respectively in areas adjacent to the tapered in the radial direction cross-section of the joint ball are pressed, preferably in each case by a control contour (146, 126, 226) and a control surface (127, 227, 147).
    [14]
    14 ball joint (100, 200) according to one of claims 1 to 13, characterized in that between the two ends of the wings (121, 221) each have a circumferentially extending film hinge (124, 224) is formed.
    [15]
    15 ball joint (100, 200) according to one of claims 1 to 14, characterized in that on the Gelenkpan (120, 220) in the unfixed state between the wings (121, 221) each have an axially extending gap is formed.
    [16]
    16. ball joint (100, 200) according to one of claims 1 to 15, characterized in that the Gelenkpan (120, 220) in the region of its wings (121, 221) is limited in its outer contour by the shape of a truncated cone, wherein the truncated cone of the open ends of the wings (121, 221) towards which the wings (121,221) connecting portion of the joint cup (120,220) decreases in outer radius.
    [17]
    17. ball joint (100, 200) according to one of claims 1 to 16, characterized in that the wings (121,221) at one end along the circumference of the joint socket (120,220) are interconnected throughout and form a common component.
    [18]
    18, ball joint (100, 200) according to one of claims 1 to 17, characterized in that the Gelenkpan (120,220) has a final end face with a central second opening (125, 225), wherein the end face on the wings (121,221) connecting region the joint cup (120, 220) is adjacent.
    [19]
    19, ball joint (100, 200) according to claim 18, characterized in that at the interconnecting region of the joint socket (120, 220) and preferably along the circumference latching hooks (123, 223) are formed, which are preferably arranged, an axial, against the Mounting direction (117) of the pivot pin (110) directed slipping the Gelenkpan (120, 220) to prevent.
    [20]
    20 ball joint (100, 200) according to claim 19, characterized in that the latching hooks (123,223) along the circumference between the wings (121, 221) are arranged and preferably U-shaped and preferably elastically deformable.
    [21]
    21 ball joint (100, 200) according to claim 5 and one of claims 19 or 20, characterized in that in the plane (128, 228) located at least a second control contour (126, 226) is arranged with the hinge sleeve (140) and the latching hooks (123, 223) of the joint cup (120, 220) with the run-on slope (142) exert an axial contact force in the direction of the imaginary longitudinal axis (122, 222) of the joint cup between the joint sleeve (140) and the joint cup (120, 220).
    [22]
    22, ball joint (100, 200) according to one of claims 1 to 21, characterized in that the hinge sleeve (140) comprises at least one run-on slope (142) which is arranged along the circumference of an imaginary circle, wherein the imaginary circle concentrically around the first opening (141) of the hinge sleeve (140) is located.
    [23]
    23 ball joint (100, 200) according to claim 22, characterized in that the latching hooks (123,223) slide in an axial rotation of the joint cup (120,220) with respect to the joint sleeve (140) on the run-on slope (142) and thereby axially exert a tensile force, the Articulated pan (120, 220) presses into the joint sleeve (140).
    [24]
    24. ball joint (100, 200) according to one of claims 1 to 23, characterized in that the ball joint (100, 200) is arranged on or within a vehicle headlamp and is adapted to fix the vehicle headlamp in a mounting position.
    [25]
    25. ball joint (100, 200) according to one of claims 1 to 24, characterized in that the joint socket (120, 220) is made of a plastic material and in particular by an injection molding process.
    [26]
    26. A vehicle headlight, in particular for generating a high beam and / or a low beam light distribution, with at least one ball joint (100, 200) according to one of claims 1 to 23 for installation of the vehicle headlight in a motor vehicle, characterized in that the ball joint (100 , 200) connects a carrier unit located on the vehicle side with the vehicle headlight.
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    同族专利:
    公开号 | 公开日
    EP3299642A1|2018-03-28|
    CN107813758B|2021-02-09|
    EP3299642B1|2019-10-23|
    CN107813758A|2018-03-20|
    AT519058B1|2018-07-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4318162A|1979-10-16|1982-03-02|General Electric Company|Snap in coupling assembly for a vehicle headlamp|
    EP0271676A1|1986-11-22|1988-06-22|TRW Ehrenreich GmbH & Co. KG|Ball joint|
    DE3841632A1|1987-12-14|1989-06-22|Cibie Projecteurs|FASTENING AND LATHE, IN PARTICULAR FOR DEVICE FOR ADJUSTING AN OPTICAL ELEMENT, SPECIFICALLY FOR MOTOR VEHICLE HEADLIGHTS|
    JPH0223236U|1988-08-01|1990-02-15|
    US5853261A|1996-07-23|1998-12-29|Cibie Do Brasil Ltda.|Lock for an adjusting screw of a car light optical block|
    DE19638031A1|1996-09-18|1998-04-02|Stabilus Gmbh|Self-locking ball joint for piston-cylinder aggregate Ball joint|
    DE202006011220U1|2006-07-20|2006-12-14|Fan, Eagle, Chu-Pei|Connector for mounting components over wide range of angles to each other comprises plate attached to ball which fits into externally threaded socket with locking ring, outer layer of ball being softer than its core|
    DE102013225002A1|2013-12-05|2015-06-11|Deere & Company|Mounting arrangement for a display or operating device|
    JP5399282B2|2010-02-03|2014-01-29|株式会社小糸製作所|clip|US11022171B2|2018-06-20|2021-06-01|Burton Technologies, Llc|Ball stud track assembly|
    EP3795421A1|2019-09-20|2021-03-24|ZKW Group GmbH|Lighting device for a motor vehicle headlight|
    DE102020100014A1|2020-01-02|2021-07-08|HELLA GmbH & Co. KGaA|Joining arrangement comprising a receiving means and a ball joint|
    DE102020100918A1|2020-01-16|2021-07-22|HELLA GmbH & Co. KGaA|Joining arrangement comprising a receiving means and a ball joint|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50807/2016A|AT519058B1|2016-09-12|2016-09-12|ball joint|ATA50807/2016A| AT519058B1|2016-09-12|2016-09-12|ball joint|
    EP17188747.4A| EP3299642B1|2016-09-12|2017-08-31|Vehicle headlight with ball joint|
    CN201710819032.8A| CN107813758B|2016-09-12|2017-09-12|Ball joint|
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