Ball joint

Abstract

The utility model provides a ball-and-socket joint, which comprises a double-screw bolt, a ball-and-socket joint, a ball-and-socket joint, a ball-and-socket joint and a ball-and-socket joint, a bearing at least partially surrounding the stud at the receiving stud portion, the bearing having an end surface and an outlet surface opposite the end surface; and a housing at least partially surrounding the bearing, the housing extending from an end to an outlet portion having an outlet surface, the housing having an inner bore having a housing inner bore diameter in which the bearing and the containment stud portion are at least partially located, the housing bore diameter is consistent or at least partially enlarged between the outlet surface of the bearing and the outlet surface of the housing so as to have a radially unobstructed stud swing region at the housing outlet portion. According to the ball joint provided by the utility model, due to the compact structure, the expected pre-tightening force can be realized, and meanwhile, the swing of the stud is maximized.

Description

Technical Field

[0001] This utility model generally relates to vehicle components, particularly ball joints used in steering and suspension systems. Background Technology

[0002] For certain vehicle components, such as tie rod ends, space constraints can inhibit their desired performance. Traditionally, there are two designs of tie rods used in the market. Both designs have a tie rod area that extends beyond the surface of the stud outlet bearing.

[0003] The first design of the inner tie rod (for example, see...) Figure 1A The assembly uses a stud outlet bearing, a rear bearing opposite the stud outlet bearing, preload components, and a housing. The stud outlet side of the housing has a press-fit or forging feature that secures all components to the assembly.

[0004] The second design (for example, see...) Figure 1B The method of using a stud outlet bearing having a radially extending stepped section in the housing to secure the bearing, the rear bearing opposite the stud outlet bearing, the preload component, and the cover plate, and pressing or forging closure of all components to the assembly on the rear side of the housing.

[0005] Without precise assembly processes, these two designs may unintentionally affect stud rotation torque, bearing clearance, and stud oscillation based on design elements. Utility Model Content

[0006] To at least address the technical problems in the prior art that affect stud rotation torque, bearing clearance, and stud oscillation, according to one embodiment, the present invention provides a ball joint, comprising: a stud having a stud-receiving portion and an attachment portion, and a bearing at least partially surrounding the stud at the stud-receiving portion. The bearing has an end surface and an outlet surface, the outlet surface being opposite to the end surface. The ball joint includes a housing at least partially surrounding the bearing, the housing extending from an end to an outlet portion having an outlet surface, the housing having an inner bore having a housing inner bore diameter, the bearing and the stud-receiving portion being at least partially located within the inner bore. The housing inner bore diameter is consistent or at least partially enlarged between the outlet surface of the bearing and the outlet surface of the housing, so as to have a radially unobstructed stud oscillation area at the outlet portion of the housing.

[0007] In some embodiments, the inner bore of the housing is configured to provide stud oscillation with a maximum range of 20-30°.

[0008] In some embodiments, at least a portion of the bearing is mechanically interlocked with the inner bore of the housing.

[0009] In some embodiments, the verification load of the mechanical interlock exceeds the stud pull-out force.

[0010] In certain embodiments, the bearing is a split bearing comprising an end bearing and an exit bearing, the exit bearing having an outer diameter that mechanically interlocks with the inner bore of the housing.

[0011] In certain embodiments, the mechanical interlock is a threaded engagement.

[0012] In certain embodiments, the exit bearing is threaded and the end bearing is unthreaded.

[0013] In certain embodiments, the exit portion is configured without a crimped or swaged lip.

[0014] In certain embodiments, the pre-load step defines the end portion and the exit portion.

[0015] In certain embodiments, the stud has a ball having a ball diameter and the end portion has an end portion diameter, wherein the ball diameter is between the inner bore diameter and the end portion diameter.

[0016] In certain embodiments, the radial extent of the pre-load step is sized with the longest radial extent of the bearing.

[0017] In certain embodiments, the exit surface of the housing is primarily radially extending.

[0018] In certain embodiments, the exit surface of the bearing comprises a plurality of drive holes.

[0019] In certain embodiments, the end portion of the housing is part of a tie rod end.

[0020] In certain embodiments, there is an internal bearing between the bearing and the inner bore of the housing.

[0021] In certain embodiments, the bearing has a heat treated spherical stud contact surface.

[0022] In one embodiment, the present invention provides a ball joint comprising: a stud having a receiving stud portion and an attachment stud portion; and a bearing at least partially surrounding the stud at the receiving stud portion. The ball joint includes a housing at least partially surrounding the bearing, the housing extending from an end portion to an exit portion, the exit portion having a radially unobstructed stud swing area. The housing has an inner bore, the bearing and the receiving stud portion at least partially located in the inner bore. At least a portion of the bearing has a mechanical interlock with the inner bore of the housing.

[0023] In certain embodiments, the mechanical interlock is a threaded engagement or an adhesive layer.

[0024] In one embodiment, the utility model provides a ball joint, it includes: stud, the stud has accommodating stud part and attachment stud part, bearing, the bearing is at least partially around the stud at accommodating stud part, and housing, the housing has inner hole, the inner hole is at least partially around the accommodating stud part of stud. The inner hole of housing is configured to provide a maximum stud swing between 20-30 °. At least a part of bearing has mechanical interlocking with the inner hole of housing.

[0025] In certain embodiments, the inner hole has a housing inner hole diameter that is uniform or at least partially enlarged between the exit surface of the bearing and the exit surface of the housing to have a radially unobstructed stud swing area at the exit portion of the housing.

[0026] The ball joint provided by the utility model can achieve a larger stud swing angle at least partially by using a mechanically-locked exit bearing, rather than only by mechanical locking imparted by the housing structure, so that there is no need to install a threaded cover plate or similar device between the exit surface of the bearing and the exit surface of the housing. In the absence of a threaded cover plate, the radially unobstructed stud swing area can be larger without affecting proper load management. Therefore, the ball joint provided by the utility model has a compact structure that can help maintain performance and load requirements while facilitating a greater degree of stud swing.

[0027] The various aspects, embodiments, examples, features and alternatives described in the foregoing paragraphs, claims and / or the following description and drawings can be used alone or in any combination. For example, features described in relation to one embodiment are applicable to all embodiments to the extent not incompatible. BRIEF DESCRIPTION OF DRAWINGS

[0028] Preferred exemplary embodiments will be described below with reference to the accompanying drawings, in which like reference numerals indicate like elements, and in which:

[0029] Figure 1A is a cross-sectional view of a ball joint according to the prior art;

[0030] Figure 1B is a cross-sectional view of another ball joint according to the prior art;

[0031] Figure 2 is a cross-sectional view of a ball joint according to one embodiment;

[0032] Figure 3 is Figure 2 is a perspective view of an exit surface of a bearing of the ball joint of

[0033] Figure 4 is Figure 2 and Figure 3perspective view of an end surface of a bearing. DETAILED DESCRIPTION

[0034] Compared to two traditional designs currently on the market, the ball joint embodiments described herein can improve the inner pull rod performance and design in several aspects. The design process is simplified by using a threaded verification load calculation to determine the correct thread size that fits the target stud pull (tensile load) requirement for the desired implementation. It can also simplify and more accurately achieve the proper stud articulation force by using a threaded bearing to set the pre-load instead of using a swage press with a predetermined closing force to capture the inner components.

[0035] In certain embodiments, stud swing can also be enhanced by reducing the presence of a housing beyond the threaded exit bearing. In at least certain embodiments, a swage profile or housing section is not required to retain the stud exit side bearing.

[0036] Figure 1A A prior art ball joint is shown, where, as shown, the pre-load is set by swaging the housing at the stud exit side of the housing at the housing swage lip. This arrangement helps to properly position and tension the various components of the ball joint; however, the amount of stud swing can be limited if the stud diameter cannot be reduced and the housing swage size is such that it cannot be reduced due to the stud pull requirement (tensile load) of the desired implementation. In this embodiment, as shown, the maximum stud swing is only about 12°. It can be desirable to facilitate greater stud swing while maintaining the desired amount of pre-load, as with the embodiments described herein.

[0037] Figure 1B Another example of a prior art ball joint is shown, where, as shown, the pre-load is set by swaging the housing at the rear of the housing opposite the stud exit side of the housing at the housing swage lip. This arrangement helps to properly position and tension the various components of the ball joint; however, the amount of stud swing for this design can depend on the housing stud exit geometry, the stud diameter at the housing opening, and the stud exit bearing throat diameter. In this embodiment, the maximum amount of stud swing is greater than Figure 1A the swing amount shown; however, as the design requirements vary depending on the desired implementation, it can be advantageous to facilitate greater stud swing while maintaining the desired amount of pre-load, as with the embodiments described herein.

[0038] Figure 2A ball and socket joint 10 is shown in accordance with one embodiment. As described herein, the ball and socket joint 10 advantageously improves performance when used as a ball joint for a part illustrated inner tie rod end 12. In certain embodiments, the joint 10 can be fitted directly into a steering cylinder without the need for a traditional tie rod housing or fitting process. However, the ball and socket joint 10 can be used in other configurations, such as a configuration with an external threaded region as is common in automotive rack and pinion applications or similar implementations, and not just tie rod ends. Moreover, features related to the joint 10 can also be useful in other joint applications. Accordingly, alternative configurations of suspension and / or steering components can be made in accordance with the teachings herein. For example, the joint 10 can include any movable socket configuration, such as a socket configuration without a ball stud, and is not limited to the explicit joint shown in the figures and described herein.

[0039] The ball and socket joint 10 includes a housing 14 that at least partially surrounds a bearing 16 and a stud 18. In the illustrated embodiment, the bearing 16 is a split bearing configuration with an exit bearing 20 and an end bearing 22. The housing 14, bearing 16, and / or stud 18 can include various threads, grooves, protrusions, etc. without being limited to particular descriptions. The ball and socket joint 10 can also include other features, such as a dust shield or other operational-based features depending on the intended use and placement of the joint.

[0040] The housing 14 is a generally circular cylindrical component that surrounds the internal components of the joint 10. The housing 14 has an inner bore 24 with an inner bore diameter D IB . The inner bore 24 generally surrounds the bearing 16 and stud 18 at a stud receiving portion 26 that is opposite an attachment stud portion 28 that extends axially out of the housing 14. The housing 14 also has a housing center axis AH that extends through the geometric center of the inner bore 24.

[0041] Structurally, the housing 14 extends from an end portion 30 to an exit portion 32 having an exit surface 34. In this particular embodiment, the end portion 30 is integrally connected with the inner tie rod end 12, or in other words, the end portion 30 is an integral part of the inner tie rod end 12. A preload step 36 demarcates the end portion 30 and the exit portion 32 and provides a radially extending stop for the end bearing 22. As Figure 2 shown, the longest radial extent of the bearing 22 coincides in size with the radial extent of the preload step 36 to maximize surface contact between the radial extent of the bearing 22 and the radial extent of the preload step 36. Accordingly, the longest radial extent of the bearing 22 is configured to extend completely along the radial extent of the preload step 36. The end portion 30 adjacent the preload step 36 has an end portion diameter D EP , which in this embodiment, is less than the inner bore diameter D EP . The exit portion 32 has an exit portion diameter D IBInner diameter D IB The outlet section 32 is usually defined, therefore the end diameter D EP It is also smaller than the diameter of the outlet section. Furthermore, in this embodiment, the stud 18 has a ball 38, which constitutes a large portion of the stud section 26. The ball 38 has a ball diameter D. B The diameter of the sphere is D B Between the end 30 diameter (D) EB ) and the diameter of the inner hole 24 (D) IB Between ), in this embodiment, the corresponding diameter is taken as its longest range, and the radial range or axial range is related to extending outward from the housing axis AH or extending parallel to the housing axis AH, respectively.

[0042] Bearing 16 is located within the inner bore 24 of housing 14. The discussion here focuses more broadly on outlet bearing 20, but the teachings relating to outlet bearing 20 can also be applied to end bearing 22 or bearings without the spliced ​​structure shown. Bearing 20 in the illustrated embodiment is made of a metallic material, such as carburized steel (e.g., AISI 8620), but other workable materials can certainly be used. Furthermore, as further described below, outlet bearing 20 is threaded, while end bearing 22 is unthreaded. This provides a better locking mechanism at the outlet portion 32 of housing 14, potentially eliminating the need for a separate cover or housing closure.

[0043] Reference Figures 2 to 4 The bearing 20 has a bearing body 40 extending from an end surface 42 to an outlet surface 44. Like the housing outlet surface 34, the outlet surface 44 of the bearing 20 extends primarily radially (e.g., most of surface 44 extends radially). The end surface 42 of the bearing 20 is axially opposed to the outlet surface 44 and also extends primarily radially. Between the end surface 42 and the outlet surface 44, there is an axially extending outer diameter surface 46 and an opposing spherical stud contact surface 48. The outer diameter surface 46 contacts the inner bore 24 of the housing 14, and the spherical stud contact surface 48 contacts the receiving stud portion 26 of the stud 18. The stud 18 and / or the bearing 20 may be heat-treated by processes such as induction heat treatment to improve hardening and wear resistance. Induction heat treatment processes can improve the fatigue strength of worn surfaces, such as the receiving stud portion 26 and the spherical stud contact surface 48.

[0044] The outer diameter surface 46 includes a mechanical interlock 50 that engages or snap fits with the inner bore 24 of the housing 14. In the illustrated embodiment, the mechanical interlock 50 includes a plurality of threads 52 that form a threaded engagement with the inner bore 24. In other embodiments, the mechanical interlock 50 can take alternative forms, or can be added to the threaded engagement, such as an adhesive layer, or one or more locking tabs, to name a few possible examples. In certain embodiments, the threads 52 can be used with an adhesive layer such as a cyanoacrylate layer, such that the mechanical interlock 50 is further strengthened. Methods of secondary fixation can be beneficial to the threads 52 to help prevent the threads from loosening in service. The mechanical interlock 50 can of course take other forms as well, such as a low profile lock nut or set screw, to name a few examples. In other embodiments, one or more locking pins, one or more rolling pins, a staking process, or even a low profile crimp, can be used as primary and / or secondary mechanical retention features, to name a few non-limiting examples. In many embodiments, the mechanical interlock 50 is imparted by structural features of the bearing 20 itself, and not just by features on the housing 14 (e.g., swaged lips or indentations).

[0045] In certain embodiments, it can be beneficial for the mechanical interlock 50 to have a proof load that exceeds the pullout force of the stud 18. In the illustrated embodiment, the threads 52 can be sized to determine the size of the pullout force of the stud 18. Thus, it can be beneficial to select a thread size that has a proof load that exceeds the pullout force requirements of the stud 18. As shown, this arrangement allows the exit portion 32 of the housing 14 to be configured without a crimp or swaged lip, as the mechanical interlock 50 between the bearing 20 and the housing 14 can maintain the desired arrangement of the internal components of the joint 10. This in turn can allow for a greater stud swing angle Θ, as will be further detailed below. The mechanical interlock 50 can also help control the articulation torque of the stud 18. Figure 2

[0046] Figure 2 An optional internal bearing 54 is also shown, which can be used between the bearing 20 and the inner bore 24 of the housing 14. The internal bearing 54 can be a clearance or interference fit within the inner bore 24 of the housing 14. The internal bearing 54 can have a threaded inner diameter to engage with the threads 52 of the bearing 20. The internal bearing 54 can be used in embodiments to help control the concentricity of the stud ball 38 and the exit bearing 20, without undesirably affecting the rotation or articulation torque of the stud 18.

[0047] ​Whether using an optional internal bearing 54 or mounting directly into the inner bore 24 of the housing 14, including mounting features that improve installation efficiency is likely beneficial. In this embodiment, a plurality of drive holes 56 are located on the radially extending outlet surface 44 of the bearing 20. The drive holes 56 can be configured to accommodate a wrench or other operating tool to facilitate engagement of the mechanical interlock 50. The preload can be set during assembly by screwing the bearing 20 into the housing and reducing the clearance between the stud ball 38 and the bearing assembly 16. Therefore, the assembly method can be simplified by using a torque wrench and wrench tools compared to more complex assembly equipment. For example, crimping the housing may require a complex press, such as... Figure 1A As shown.

[0048] The connector 10 allows for preload setting on the bearing 20 while simultaneously withstanding tensile loads and providing proper positioning during use, and advantageously allows the stud 18 to be hinged without interference. A radially unobstructed stud swing area 58 exists at the outlet 32 ​​of the housing 14. (As...) Figure 2 As shown in the embodiment, compared to FIG1, the radially unobstructed stud swing region 58 includes the housing inner bore diameter D IB Part of the housing's inner bore diameter D IB The outlet surface 44 of the bearing 20 and the outlet surface 34 of the housing 14 are aligned. In some embodiments, the inner diameter D of the housing is... IB The radially unobstructed stud swing region 58 expands at least partially. As shown in Figure 1, unlike Figure 1, Figure 2 There are no crimped or forged edges. Instead, in Figure 2 In this configuration, the outlet surface 34 of the housing extends primarily radially, providing a larger stud swing area 58 than the press-fit or forged end. However, it should be noted that for the threaded arrangement in the bore 24, the radial range may be defined at the top of the thread, such that the arrangement still includes a uniform or at least partially expanded radial range. Furthermore, in some embodiments, the outlet bearing 20 may be positioned closer to or directly adjacent to the outlet surface 34 of the housing than specifically described. Therefore, the axial lengths of the housing 14 and the bore 24 can vary, thereby altering the arrangement of the radially unobstructed stud swing area 58 to align with... Figure 2 The differences are clearly shown in the text. Additionally, as shown in the text... Figure 1A and Figure 1B and Figure 2 As shown in the comparison, in this embodiment, the stud 18 is capable of oscillating within a radially extending space, which is typically defined as the radial extent of the bearing outlet surface 44, while... Figure 1A and Figure 1B In the middle, the housing blocks and protrudes inward toward the stud to block the radial space.

[0049] Figure 2 The radially unobstructed stud swing zone 58 allows for a stud swing angle θ, which can be greater than the stud swing angle of a stud with a press-fit or forged housing, such as... Figure 1A The stud swing angle is shown in the figure. Figure 1A In the diagram, the maximum stud swing angle is shown to be approximately 12°, while... Figure 2 With a radially unobstructed swing area 58, the maximum stud swing angle is approximately 20-30°, more specifically 25-30°, or more specifically, 27° in the illustrated embodiment. The stud swing angle generally refers to the amount by which the stud axis AS can pivot relative to the housing axis AH. The larger stud swing angle θ of this application can be achieved, at least in part, by using a mechanically locked outlet bearing 20, rather than solely by mechanical locking provided by the housing structure, thus eliminating the need for a threaded cover or similar device between the bearing outlet surface 44 and the housing outlet surface 34. Without a threaded cover, the radially unobstructed stud swing area 58 can be larger without compromising proper load management. Therefore, a compact structure can help maintain performance and load requirements while facilitating a greater degree of stud swing. The mechanically locked outlet bearing 20 with threads 52 can adequately set the preload without unduly interfering with the radial space of the outlet portion of the housing 14. Increased stud swing can also be influenced by other variables in the joint design.

[0050] It should be understood that the foregoing description pertains to one or more preferred exemplary embodiments of the present invention. The present invention is not limited to the specific embodiments disclosed herein, but is defined solely by the following claims. Furthermore, the statements in the foregoing description relate to specific embodiments and should not be construed as limiting the scope of protection of the present invention or the definition of terms used in the claims, unless the terms or phrases are expressly defined above. Various other embodiments and various changes and modifications to the disclosed embodiments will be apparent to those skilled in the art. All such other embodiments, changes, and modifications fall within the scope of the appended claims.

[0051] The terms “for example,” “e.g.,” “such as,” “for instance,” and “like,” and the verbs “comprising,” “having,” “including,” and their other verb forms, when used in this specification and / or claims, are each used open- ended, meaning that an item or items are not required to be present for the statement to be true. Other terms are to be construed using their broadest reasonable interpretation, unless they are used in a context that requires a different interpretation. Further, the term “and / or” should be interpreted to include OR. Therefore, for example, the phrase “A, B, and / or C” should be interpreted to encompass the following: A; B; C; A and B; A and C; B and C; and A, B, and C.

Claims

1. A ball joint, comprising: A stud, the stud having a stud-receiving portion and an attachment portion; A bearing surrounding the stud at least partially at the receiving stud portion, the bearing having an end surface and an outlet surface, the outlet surface being opposite to the end surface; as well as A housing at least partially surrounds the bearing, the housing extending from an end to an outlet portion having an outlet surface, the housing having an inner bore having a housing inner bore diameter, the bearing and the receiving stud portion being at least partially located within the inner bore, wherein the housing inner bore diameter is consistent or at least partially enlarged between the outlet surface of the bearing and the outlet surface of the housing, so as to have a radially unobstructed stud swing area at the housing outlet portion. The bearing is characterized in that it is a split bearing comprising an end bearing and an outlet bearing, wherein the outer diameter of the outlet bearing is mechanically interlocked with the inner bore of the housing.

2. The ball joint according to claim 1, characterized in that, The inner bore of the housing is configured to provide stud oscillation at a maximum of 20-30°.

3. The ball joint according to claim 1, characterized in that, The verification load of the mechanical interlock exceeds the stud pull-out force.

4. The ball joint according to claim 1, characterized in that, The mechanical interlock is a threaded engagement.

5. The ball joint according to claim 1, characterized in that, The outlet bearing is threaded, while the end bearing is unthreaded.

6. The ball joint according to claim 1, characterized in that, The outlet section is configured without a crimped or forged lip.

7. The ball joint according to claim 1, characterized in that, The preload step defines the end and the outlet, wherein the stud has a ball with a ball diameter, and the end has an end diameter, wherein the ball diameter is between the inner diameter and the end diameter.

8. The ball joint according to claim 7, characterized in that, The radial range of the preload step matches the longest radial range of the bearing.

9. The ball joint according to claim 1, characterized in that, The outlet surface of the housing extends primarily in the radial direction.

10. The ball joint according to claim 1, characterized in that, The outlet surface of the bearing includes a plurality of drive holes.

11. The ball joint according to claim 1, characterized in that, The end of the housing is part of the inner tie rod end.

12. The ball joint according to claim 1, characterized in that, This includes an internal bearing located between the inner bore of the housing and the bearing.

13. The ball joint according to claim 1, characterized in that, The bearing has a heat-treated spherical stud contact surface.

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