Swivel bearing, pivot pin and motor vehicle

Abstract

Pivot bearing (2) for a motor vehicle, with a base element (4), and with a pivot pin (6) which can be connected to the base element (4) and has a shaft portion (8), characterized in that the base element (4) has a blind hole-like recess (10) which is designed to receive the shaft portion (8) of the pivot pin (6), and in that the pivot pin (6) has a toothed ring (12) which surrounds the shaft portion (8) of the pivot pin (6) and fixes the pivot pin (6) in the blind hole-like recess (10) in the direction of an axial direction of the shaft portion (8).

Description

[0001] The invention relates to a pivot bearing for a motor vehicle, comprising a base element and a pivot pin connectable to the base element and having a shaft portion. The invention further relates to a pivot pin for connection to a pivot bearing and to a motor vehicle.

[0002] Pivot bearings of the type mentioned above are known from the prior art and can be used in particular in chassis in the automotive sector. In the chassis of a car, articulated connections ensure that the interaction of moving parts and the kinematic specifications are met during driving. For example, a guide joint is connected to a pivot bearing via a conical connection. The conical connection consists in a conically tapered fastening section being pressed into a similarly conical holder. By selecting certain cone ratios, a relatively strong connection is achieved via a self-locking effect, thus further securing the connection against loosening. However, shock loads during driving do not rule out loosening, so the connection is usually additionally secured with a lock nut.The lock nut is screwed onto a shaft portion opposite the opening of the holder, which can be designed as a threaded bolt, for example, whereby the shaft portion protrudes from the component to which the pivot pin is to be attached.

[0003] Ensuring the nut support is correctly and securely requires additional machining effort. Depending on the component, direct access for cutting tools is not always guaranteed, so special solutions are required. One option for machining the nut support surface can be achieved, for example, using side milling cutters that approach the machining position from the front or using special tools that machine the nut support surface from below through a holder designed, for example, as a tapered bore. This has a time-, cost-, and investment-intensive impact on the machining process. Such an arrangement with a lock nut is also space-intensive in terms of height.

[0004] From a customer service perspective, depending on their location in the landing gear, disassembly / assembly may be difficult due to limited space. The exposed nut also represents a point of attack for corrosive influences, which could compromise the secure connection in the long term under unfavorable conditions. However, for safety reasons, secure attachment of these joints to the moving landing gear components must be ensured due to the prevailing forces.

[0005] DE 24 49 381 A1 discloses a wheel suspension for motor vehicles in which the ball joint has a plate-shaped part as a fastening element. This fastening element is secured in a socket by means of screws running transversely to the joining direction.

[0006] From the generic CN 1 09 695 625 A, a ball stud assembly is known in which a cylindrical shaft portion of the ball stud penetrates an inner bore of an intermediate piece and is secured with a nut on the side of the component to which the ball stud is attached, opposite the spherical portion of the ball stud. The intermediate piece has a conically tapered outer surface and is inserted into a suitably designed receptacle in the component. In this way, improved stress distribution in the component can be achieved, making the component less likely to break and thus increasing operational reliability.

[0007] From DE 10 2019 101 642 A1 an air spring system for a motor vehicle is known which has a component which is fixed to a connecting component by means of a connecting element to form a plug connection, wherein the connecting element is designed for fastening in an opening of the connecting component and has a plug element which can be inserted into the opening and which has a receiving groove in which a fixing element for fixing the plug element in the opening is arranged.

[0008] In the Fig. 1 to 2, such a connection is shown using the example of a guide joint, which corresponds to the current state of the art and is known per se in its arrangement and implementation. The guide joint 108 establishes a movable connection between the component 112 and a wishbone that can be attached to the guide joint 108. On the chassis side, the guide joint establishes an articulated connection between the pivot bearing 112 and the wishbone (not shown in the figure). It compensates for angular changes between the aforementioned parts relative to one another, which occur during driving, for example, due to compression and rebound movements as well as steering movements. The guide joint 108 is firmly connected to the component 112 via a conical connection of its pivot pin 102.The pivot pin 102 has a conical fastening portion 104 in the form of a tapered shaft, which is pressed into a receptacle 110 provided in the component 112 to which the guide joint 108 is to be fastened. On the side opposite the fastening portion 104, the pivot pin 102 has a joint or ball portion, which is in the . Fig. 1 is not visible because it is enclosed by the housing of the guide joint 108 and thus concealed.

[0009] The fastening part 104 is held in the receptacle 110 by a force-locking connection. However, it could slip out of the receptacle 110 under shock loads, which is why the fastening part 104 in the form of a threaded bolt with a shaft or bolt portion protrudes from the top of the receptacle 110 and is secured against unintentional loosening by a lock nut 114 and a washer 116.

[0010] In Fig. 2 is a cross-section of the prior art pivot pin 102 of Fig. 1. In the lower part of the figure, the joint portion 106 of the ball joint can also be seen, since the joint housing is not shown in this figure. It can be seen that the fastening portion 104 sits in the component 112 similar to a cork in a bottle neck, but during the joining process, a threaded portion emerged from the component 112, so that this threaded portion now protrudes from the component 112. The lock nut 114 was then screwed onto the threaded portion so that the fastening portion 104 sits firmly in the receptacle 110 and cannot leave it even in the event of strong impacts or other acting forces.

[0011] The object of the present invention is to further develop a pivot bearing of the type mentioned above in such a way that simplified assembly is possible. It is a further object of the present invention to design such a pivot bearing in such a way that its susceptibility to corrosion is reduced.

[0012] The object is achieved according to the invention by a generic pivot bearing in which the base element has a blind hole-like recess which is designed to receive the shaft portion of the pivot pin, and in which the pivot pin has a toothed ring which surrounds the shaft portion of the pivot pin and which fixes the pivot pin in the direction of an axial direction of the shaft portion in the blind hole-like recess.

[0013] The object is further achieved by a pivot pin for connection to a pivot bearing, with a toothed ring enclosing a shaft portion of the pivot pin, wherein the toothed ring has barb-like projections which are designed to elastically yield during a joining movement of the pivot pin along a joining direction and thus temporarily reduce an effective diameter of the pivot pin.

[0014] The object is also achieved by the use of a toothed ring with an annular base body and barb-like projections distributed over a circumference of the base body for fastening a pivot pin in a pivot bearing, as well as by a motor vehicle with a pivot bearing according to the invention.

[0015] The toothed ring provided according to the invention enables extremely simple assembly while simultaneously ensuring a secure fit of the pivot pin in the base element. Unlike the prior art, it is sufficient if the base element is accessible from one side for mounting the pivot pin. Accordingly, it is possible to use a blind hole-like recess as a receptacle for the pivot pin or its shaft portion. In addition to the assembly advantages, this also offers advantages with regard to the corrosion resistance of the pivot bearing, as there are fewer surfaces exposed to corrosive processes.

[0016] An axial direction is understood in particular to mean a direction that extends parallel to a longitudinal axis of the component in question. The component can have at least approximately a rotationally symmetrical basic shape. A radial direction then extends perpendicular to the axial direction.

[0017] In the context of the present description, a blind hole-like recess is understood to mean, in particular, a cavity that has a basic shape that is open on a single side. In particular, the cavity can be open on only one side. It can therefore, for example, have an open side, an end wall and side walls, or a cylindrical side wall. The end wall and / or the side walls can be configured to be at least predominantly and preferably completely closed.

[0018] A base element is understood, in particular, to be a component that forms a larger structure and to which a pivot pin can be connected, in turn enabling a connection to a third component. This connection can, in particular, be a flexible or articulated connection. The base element can, in particular, be a component with a load-bearing function.

[0019] In the context of this description, the toothed ring enclosing the pivot pin or its shaft portion is understood to mean, in particular, that a central opening of the toothed ring is penetrated by the pivot pin or its shaft portion. In particular, the toothed ring can be in full contact with the outside of the pivot pin or its shaft portion with its inner surface.

[0020] In the context of this description, a pivot pin is understood to mean, in particular, an elongated component for connecting two other components. Typically, the first component and the second component extend essentially in a plane perpendicular to the longitudinal axis of the pivot pin. The pivot pin can be part of a joint, in particular a ball joint. Accordingly, it can have a spherical end element on one side.

[0021] In the context of this description, a pivot bearing is understood to be a component of a wheel suspension, in particular a front wheel suspension of a motor vehicle. The pivot bearing performs tasks such as wheel guidance and the transmission of longitudinal and lateral forces to the spring strut, the wishbone and the tie rod. Forces from the road are introduced via the wheel bearing. To enable the vehicle to be steered, the bearing must have several degrees of freedom, in other words it must be pivotable. As a complex component, the pivot bearing can accommodate peripherals such as a spring strut, cover plate, brake caliper, joints, wheel bearings or an ABS sensor. The pivot bearing is usually made in one piece, for example as a cast or forged part. The design and arrangement of the interfaces of the pivot bearing can be specifically tailored to a particular configuration or application.Vehicle kinematics.

[0022] In the context of this description, a toothed ring is understood to mean, in particular, an element with an annular base body that has a plurality of locking elements distributed around its circumference. The locking elements can be designed like barbs. In particular, the locking elements can be configured such that they react differently to different loading directions. They can therefore be designed asymmetrically with respect to a loading direction. Thus, the locking elements can deflect and yield when subjected to a force along one joining direction and lock when subjected to an opposite load.

[0023] According to the invention, the pivot pin can be mounted in the base element by simply pressing it in. The toothed ring can have barb-like projections that elastically compress during the joining process and thus enable the joining movement, but block further movement in the axial direction once the desired position of the pivot pin has been reached. For this purpose, a circumferential projection can be provided on the inside of the blind-hole-like recess. It is also possible for a plurality of projections or depressions corresponding to the projections of the toothed ring to be formed on the inside of the blind-hole-like recess. In any case, it is advantageous if the inside of the blind-hole-like recess is designed in such a way that the projections are able to at least partially rebound in the end position of the pivot pin.The projections can then be supported on a counter bearing within the blind hole-like recess and thus prevent the pivot pin from being pulled out of the recess.

[0024] An advantageous embodiment of the pivot bearing according to the invention provides that the shaft portion of the pivot pin has a cylindrical basic shape. This allows for simple assembly, since no exact orientation of the pivot pin relative to the base element needs to be maintained in order to carry out the joining process. In other words, a substantially rotationally symmetrical design of the shaft portion allows the shaft portion to be rotated about an axis parallel to the joining direction without negatively influencing the joining movement. Furthermore, such a design makes it possible to further strengthen the connection between the pivot pin and the base element through a press fit.

[0025] The toothed ring can expediently be designed such that it has barb-like projections distributed along a circumference of the toothed ring. The blind hole-like recess can then have an abutment in the base element that is designed to correspond to the barb-like projections of the toothed ring. Such an abutment can be formed, for example, by one or more depressions or recesses, a groove, or one or more projections. The abutment can expediently be formed on an inner wall of the blind hole-like recess. Such a groove can, in particular in the axial direction, have an extension approximately corresponding to the extension of the projections. In the radial direction, the groove can have an extension of, for example, between 1 mm and 5 mm or between 1 mm and 3 mm.

[0026] To secure the gear ring to the shaft portion, it is also possible to insert the gear ring into a groove surrounding the shaft portion. This ensures a secure fit of the gear ring on the shaft portion and prevents axial slippage.

[0027] Alternatively, the gear ring can be pressed onto the shaft portion. A so-called interference fit can also be used here. The diameter of the shaft portion is then slightly larger than the inner diameter of the gear ring, at least in the area where the gear ring is to be positioned, so that the gear ring must be slightly stretched to reach the desired position. The elastic restoring force then creates a high frictional force between the inner side of the gear ring and the outer side of the shaft portion, which also prevents the gear ring from slipping in the axial direction.

[0028] It is also possible for the shaft portion to have a tapered shape. In other words, the shaft portion can then have a truncated cone-like basic shape, at least in sections. To this end, it can taper toward an end facing the base element in the assembled state. In this way, the press fit of the shaft portion in the recess can be further reinforced by a so-called conical seat.

[0029] It is possible for the shaft portion to have a larger diameter than the blind-hole-like recess in the base element. The difference between the diameter of the recess and the diameter of the shaft portion can be small, for example, a few mm or approximately 0.1% of the diameter of the shaft portion. Here, too, a so-called interference fit can be used to increase the frictional forces between the shaft portion and the base element, thus achieving a particularly tight fit of the shaft portion and thus of the entire pivot pin in the base element.

[0030] Embodiments of the invention are explained in more detail with reference to the drawings and the following description. They show: Fig. 3: a first embodiment in a sectional side view, Fig. 4: a detailed view of a section of Fig. 3, Fig. 5: the first embodiment in an assembled state, Fig. 6: the first embodiment in different stages during installation, Fig. 7: the first embodiment during the final joining movement, Fig. 8: a second embodiment in a sectional side view, and Fig. 9: a detailed view of a section of Fig. 8.

[0031] Fig. Figure 3 shows a first embodiment of a pivot bearing 2 according to the invention in a sectional side view. The pivot bearing 2 consists of a base element 4, which in this example is formed by a so-called steering lever for connecting a tie rod of a steering gear. Located in the base element 4 is a recess 10 having a cylindrical basic shape and an end wall 28 that closes off the recess 10 in the axial direction. The recess 10 is designed like a blind hole. It is therefore not a through-opening or bore, but rather has an end wall in addition to the circumferential side wall. Accordingly, the recess 10 is only open on one side.

[0032] The pivot pin 6 is designed as a separate component from the base element 4. The pivot pin 6 has a shaft portion 8, which is intended for insertion into the recess 10 of the base element 4, which is designed in the form of a steering lever. Furthermore, the pivot pin 6 has a ball head 18, with which it is mounted in the joint housing 22, also referred to as the joint shell, and can thus establish an articulated connection to another component. In the area of the joint housing 22 and the base element 4, the pivot pin 6 is enclosed by a bellows 24.

[0033] Another, separately constructed component is the toothed ring 12. The toothed ring 12 rests against the cylindrical outer surface of the shaft portion 8. The toothed ring 12 thus encloses the shaft portion 8. It has a base body extending essentially in the axial direction or in the joining direction A, which base body carries the projections 14. In the illustrated, joined state of the component, the projections 14 engage in the groove 16, which expands the recess 10 in sections in the radial direction. In the illustrated embodiment, the groove 16 is arranged in an area near the opening of the recess 10. The projections 14 are supported on a surface in the groove 16 that is oriented essentially in the radial direction. For this purpose, the projections 14 are in contact with the groove 16 with a surface that is also oriented essentially in the radial direction, and in particular with said surface of the groove 16 that is oriented in the radial direction.

[0034] The toothed ring 12 rests against the shaft portion 8 both circumferentially around its outer side and with the radial toothed ring portion 26 against the end face 30 of the shaft portion 8. This prevents the pivot pin 6 from slipping out of the toothed ring 12 under load in an axial direction.

[0035] Fig. 4 shows an enlarged detailed view of a section of Fig. 3. The shaft portion 8 of the pivot pin, the base element 4, and the toothed ring 12 can again be seen, which engages with the projections 14 in the groove 16. The enlarged view clearly shows how the radially extending toothed ring portion 26 engages around the shaft portion 8 and is supported on the end face 30 of the shaft portion 8. This end face 30 extends predominantly in a direction approximately perpendicular to the joining direction A. Part of the bellows 24 can also be seen in the lower part of the figure.

[0036] Fig. Figure 5 shows the first embodiment in an assembled state. The shaft portion of the pivot pin, which is inserted into the recess 10 in the base element 4 and concealed by the bellows 24 in the figure, connects the base element 4 to the joint housing 22, which is part of a wishbone, via the ball head, which is also concealed by a cover.

[0037] Fig. 6 shows the first embodiment in different stages during installation in a perspective view. In a first step, the toothed ring 12 is pressed onto the shaft portion 8 of the pivot pin 6 along the longitudinal axis of the pivot pin 6, which in the figure coincides with the joining direction A. In its final position shown in the right-hand part of the figure, the toothed ring 12 rests with the radial toothed ring portions 26 in the form of radial extensions of its base body against the end face 30 of the shaft portion 8. The pivot pin 6, now connected to the toothed ring 12, is then inserted into the joint housing 22 with the ball head 18 in a second step, also by a movement along the joining direction A. It can be seen that the projections 14 protrude slightly from the base body of the toothed ring 12 and thus increase the effective diameter 20 of the toothed ring 12 so that it is larger than the diameter of the base body of the toothed ring 12.

[0038] Fig. Figure 7 shows the first embodiment during the final joining movement. After the second, in Fig. 6, the pivot pin 6 is connected to the toothed ring 12 and the joint housing 22. The unit thus created is then connected to the base element 4 in a third step by a joining movement along the joining direction A. For this purpose, the shaft portion 8 penetrates into the recess 10 in the base element 4. In the process, the projections 14 are initially pressed together, so that the effective diameter of the toothed ring is reduced. The projections 14 therefore perform a pivoting movement around an area in which they are connected to the base body of the toothed ring 12. In other words, the projections 14 are folded in during a movement in the joining direction. The outer ends of the projections 14 therefore move in the direction of the base body of the toothed ring 12 and simultaneously in the direction of the pivot pin 6 or its shaft portion 8. The complete joining movement is thus made possible.As soon as the pivot pin 6 has reached its end position, the toothed ring 12 with the projections 14 is, as seen in the axial direction, at the same height as the groove (not visible in the figure), so that the projections 14 have space to rebound and thus increase the effective radius of the toothed ring 12 and thus also of the shaft portion 8. Due to the barb-like structure of the projections 14, a renewed compression of the projections 14 is avoided when a load is applied opposite to the joining direction A, so that the pivot pin 6 is prevented from slipping out of the base element 4. This creates a "barb effect".

[0039] Fig. Figure 8 shows a second embodiment of a pivot bearing 2 according to the invention in a sectional side view. The components of the pivot bearing 2 are again the base element 4 with the blind-hole-like recess 10 and the groove 16, the pivot pin 6 with the shaft portion 8 and the ball head 18, and the toothed ring 12 with the barb-like projections 14. The second embodiment differs from the first embodiment only with regard to the shape of the shaft portion 8. The shaft portion 8 here has a conically tapered shape. In other words, the shaft portion 8 has a smaller diameter at its end facing the bottom of the recess 10 than at its end closest to the opening.When the components are joined together, in other words when the shaft portion 8 is inserted into the recess 10, the so-called conical fit generates particularly high static friction forces, which, in addition to the forces imparted by the toothed ring 12, ensure that the shaft portion 8 is firmly seated in the recess 10. This conical fit, with certain cone ratios, creates a self-locking effect that prevents the connection from becoming loose and thus provides additional security for the connection between the pivot pin 6 and the base element 4.

[0040] Fig. 9 shows a detailed view of a section of Fig. 8. It is particularly clearly visible here that an angle α exists between the joining direction A and a direction along which the side wall of the shaft portion 8 extends. This angle can, for example, be between 3° and 15°, in particular between 5° and 10°. List of reference symbols 2 swivel bearings 4 Basic element 6 pivot pins 8 shaft portion 10 Recess 12 toothed ring 14 projections 16 grooves 18 ball head 20 diameters 22 Bearing part / joint housing 24 Seal / bellows 26 radial gear ring portion 28 Front wall of the recess 30 End face of the shaft portion 102 pivot pins 104 fastening portion 106 joint portion 108 bearing shell 110 recording 112 component 114 Lock nut 116 Washer α angle A axial direction

Claims

[1] Pivot bearing (2) for a motor vehicle, comprising a base element (4) and a pivot pin (6) connectable to the base element (4) and having a shaft portion (8), characterized by that the base element (4) has a blind hole-like recess (10) which is designed to receive the shaft portion (8) of the pivot pin (6), and that the pivot pin (6) has a toothed ring (12) which surrounds the shaft portion (8) of the pivot pin (6) and fixes the pivot pin (6) in the direction of an axial direction of the shaft portion (8) in the blind hole-like recess (10). [2] Pivot bearing (2) according to claim 1, characterized by that the shaft portion (8) of the pivot pin (6) has a cylindrical basic shape. [3] Pivot bearing (2) according to one of the preceding claims, characterized bythat the toothed ring (12) has barb-like projections (14) distributed along a circumference of the toothed ring (12), and that the blind hole-like recess (10) in the base element (4) has a counter-bearing designed to correspond to the barb-like projections (14) of the toothed ring (12). [4] Pivot bearing (2) according to claim 3, characterized by that the counter bearing is designed as a groove (16). [5] Pivot bearing (2) according to one of the preceding claims, characterized by that the toothed ring (12) is inserted into a groove surrounding the shaft portion (8). [6] Pivot bearing (2) according to one of the preceding claims, characterized by that the shaft portion (8) has a conical shape. [7] Pivot bearing (2) according to one of the preceding claims, characterized by that the shaft portion (8) has a larger diameter than the blind hole-like recess (10). [8] Pivot pin (6) for connection to a pivot bearing (2), characterized by a toothed ring (12) encircling a shaft portion (8) of the pivot pin (6), wherein the toothed ring (12) has barb-like projections (14) which are designed to elastically yield during a joining movement of the pivot pin (6) along a joining direction and thus reduce an effective diameter of the pivot pin (6) during the joining movement. [9] Use of a toothed ring (12) with an annular base body and barb-like projections (14) distributed over a circumference of the base body for fastening a pivot pin (6) in a pivot bearing (2). [10] Motor vehicle with a pivot bearing (2) according to one of claims 1 to 7 and / or with a pivot pin (6) according to claim 8.

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