socket connection

Abstract

A socket joint that has the following features: a bolt with a received bolt section and a fastening bolt section; a bearing that at least partially surrounds the bolt at the received bolt section, wherein the bearing has an end face and an exit face, the exit face being opposite the end face; and a housing that at least partially surrounds the bearing, wherein the housing extends from an end section to an exit section with an exit surface, wherein the housing has an internal bore with a housing internal bore diameter, wherein the bearing and the received bolt section are at least partially arranged in the internal bore, wherein the housing internal bore diameter is consistent between the exit surface of the bearing and the exit surface of the housing or extends at least partially, such that a radially unimpeded bolt pivoting area is present at the exit section of the housing.

Description

TECHNICAL AREA

[0001] This disclosure relates generally to vehicle parts and, more particularly, to male and female connections used in steering and suspension systems. BACKGROUND

[0002] For some vehicle components, such as an inner tie rod end, space constraints can compromise desired performance. Traditionally, two styles of inner tie rods are used on the market. Both have an area of ​​the inner tie rod end that extends beyond the surface of the stud exit bearing.

[0003] The first design of an inner tie rod (see e.g. Fig. 1A) uses a bolt exit bearing, a rear bearing opposite the bolt exit bearing, a preload component, and a housing with a crush or forge element on the bolt exit side of the housing that secures all components in the assembly.

[0004] The second version (see e.g. Fig. 1B) uses a bolt output bearing with a radially extending stepped portion in the housing to secure the bearing, a rear bearing opposite the bolt output bearing, a preload component, and a cover plate and crimp or press-fit method on the rear of the housing that secures all components in the assembly.

[0005] Without sophisticated assembly, both designs can adversely affect the rotational torque of the bolt, the bearing clearance, and the pivoting or stroke of the bolt due to the design elements. SUMMARY

[0006] According to one embodiment, a socket joint is provided comprising a bolt with a received bolt portion and a fastening bolt portion, and a bearing at least partially surrounding the bolt at the received bolt portion. The bearing has an end surface and an exit surface, the exit surface being opposite the end surface. The socket joint comprises a housing at least partially surrounding the bearing, the housing extending from an end portion to an exit portion having an exit surface, the housing having an internal bore with a housing internal bore diameter, the bearing and the received bolt portion being at least partially disposed in the internal bore.The inner bore diameter of the housing is constant or at least partially widened between the exit surface of the bearing and the exit surface of the housing, so that a radially unobstructed bolt pivoting area is created at the exit section of the housing.

[0007] In some embodiments, the inner bore of the housing is designed to allow a maximum bolt pivot or stroke of 20-30°.

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

[0009] In some embodiments, the proof load of the mechanical locking mechanism exceeds the magnitude of the bolt pull-out force.

[0010] In some embodiments, the bearing is a split bearing having an end bearing and an output bearing, wherein an outer diameter of the output bearing mechanically engages the inner bore of the housing.

[0011] In some embodiments, the mechanical locking is a screw connection.

[0012] In some embodiments, the starting bearing is threaded and the end bearing is unthreaded.

[0013] In some embodiments, the output portion is designed without a flanging or swaged lip.

[0014] In some embodiments, the end portion and the exit portion are delimited by a biasing step.

[0015] In some embodiments, the bolt has a ball with 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 some embodiments, the radial extension of the preload stage is matched to the longest radial extension of the bearing.

[0017] In some embodiments, the exit surface of the housing is primarily radially oriented.

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

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

[0020] In some embodiments, an inner bearing is located between the bearing and the inner bore of the housing.

[0021] In some embodiments, the bearing has a heat-treated spherical pin contact surface.

[0022] In one embodiment, a socket joint is provided comprising a bolt with a received bolt portion and a fastening bolt portion, and a bearing at least partially surrounding the bolt at the received bolt portion. The socket joint or socket joint comprises 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 bolt pivot range. The housing has an internal bore, with the bearing and the received bolt portion being at least partially disposed within the internal bore. At least a portion of the bearing has a mechanical interlock with the internal bore of the housing.

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

[0024] In one embodiment, there is a socket joint comprising a bolt with a received bolt portion and a fastening bolt portion, a bearing that at least partially surrounds the bolt at the received bolt portion, and a housing with an internal bore that at least partially surrounds the received bolt portion of the bolt. The internal bore of the housing is designed to allow the bolt to pivot between a maximum of 20-30°. At least a portion of the bearing has a mechanical interlock with the internal bore of the housing.

[0025] In some embodiments, the inner bore has a housing inner bore diameter that is consistent or at least partially extends between the exit surface of the bearing and the exit surface of the housing to provide a radially unobstructed pin pivot area at an exit portion of the housing.

[0026] Various aspects, embodiments, examples, features, and alternatives set forth in the preceding paragraphs, in the claims, and / or in the following description and drawings may be considered independently of one another or in any combination thereof. For example, features disclosed in connection with one embodiment are applicable to all embodiments, unless there is any incompatibility of the features. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Preferred embodiments are described below in conjunction with the accompanying drawings, wherein like designations refer to like elements and wherein: Fig. 1A is a cross-sectional view of a socket joint according to the prior art; Fig. 1B is a cross-sectional view of another prior art socket joint; Fig. 2 is a cross-sectional view of a socket joint according to one embodiment; Fig. 3 is a perspective view of an exit surface of a bearing of the socket joint of Fig. 2; and Fig. 4 is a perspective view of an end face of the bearing of Fig. 2 and Fig. 3. DETAILED DESCRIPTION

[0028] The socket joints described here can improve various aspects of inner tie rod performance and design compared to the two conventional designs on the market. The design process is simplified by using thread compressive strength calculations to determine the correct thread size appropriate for the target bolt pullout (tensile load) of the desired implementation. Determining the appropriate bolt pullout can also be simplified and made more precise by using the threaded bearing to adjust the preload, rather than a crimping press that grips internal components with a predetermined clamping force.

[0029] In some embodiments, the bolt stroke can also be improved by reducing the protrusion of the housing behind the threaded output bearing. At least in some embodiments, there is no need for a bead profile or housing section to retain the bolt output bearing.

[0030] Fig. Figure 1A shows a prior art socket joint in which the preload is adjusted by swaging the housing against the housing clamping lip on the bolt exit side of the housing, as indicated. This arrangement can assist in properly positioning and tensioning the various components of the socket joint; however, the amount of bolt travel may be limited if the bolt diameter cannot be reduced and the size of the housing swage is such that it cannot be reduced due to bolt withdrawal (tensile) requirements in the desired design. In this embodiment, the maximum bolt travel, as shown, is only about 12°. It may be desirable to allow for greater bolt travel while maintaining a desired preload, as in the designs described herein.

[0031] Fig. Figure 1B shows another example of a prior art socket in which the preload is adjusted by crimping the housing against the housing clamping lip on the rear of the housing, opposite the bolt exit side of the housing, as shown. This arrangement can help to properly position and tighten the various components of the socket connection; however, the extent of bolt travel in this design is likely dependent on the geometry of the housing bolt exit, the bolt diameter at the housing opening, and the diameter of the bolt exit bearing. In this design, the maximum bolt travel is greater than in Fig. 1 A; however, since design requirements vary depending on the desired configuration, it may be advantageous to allow for a greater bolt stroke while maintaining a desired amount of preload, as in the configurations described here.

[0032] Fig. Figure 2 shows a socket joint 10 in accordance with one embodiment. As described herein, the socket joint 10 advantageously improves performance when used as a ball joint for an inner tie rod end 12, which is partially shown. In some embodiments, the joint 10 can be installed directly into a steering cylinder without the need for a conventional tie rod housing or assembly process. However, it is possible for the socket joint 10 to be used in other configurations, such as with an external thread, as is common in automotive rack and pinion applications, or in similar applications beyond tie rod ends. Furthermore, the features of the joint 10 may be useful for other joint applications as well.Accordingly, it is possible to manufacture alternatively configured suspension and / or steering components in accordance with the teachings presented herein. For example, the joint 10 may have any movable socket configuration, such as those without a ball stud, and is not limited to the joint shown in the figures and described herein.

[0033] The socket joint 10 includes a housing 14 that at least partially encloses a bearing 16 and a bolt 18. In the illustrated embodiment, the bearing 16 is a split bearing with a starting bearing 20 and an end bearing 22. The housing 14, the bearing 16, and / or the bolt 18 may include various threads, grooves, projections, etc. beyond those illustrated herein. The socket joint 10 may also include other features, such as a dust boot or other operational features depending on the desired use and location of the joint.

[0034] The housing 14 is a generally circular-cylindrical component that encloses the internal components of the joint or connection 10. The housing 14 has an internal bore 24 with an internal bore diameter D IB. The inner bore 24 generally surrounds the bearing 16 and the bolt 18 at a received bolt portion 26 of the bolt that opposes a mounting bolt portion 28 that extends axially outward from the housing 14. The housing 14 also has a central housing axis A H which passes through the geometric center of the inner bore 24.

[0035] 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 to the inner tie rod end 12, or in other words, an integral part thereof. A preload step 36 defines the end portion 30 and the exit portion 32 and provides a radially extending stop for the end bearing 22. As shown in Fig. 2, the longest radial extent of the bearing 22 is dimensioned with a radial extent of the preload step 36 such that the surface contact between the radial extent of the bearing 22 and the radial extent of the preload step 36 is maximized. Accordingly, the longest radial extent of the bearing 22 is configured to extend entirely along the radial extent of the preload step 36. The end portion 30 adjacent to the preload step 36 has an end portion diameter D EP , which in this embodiment is smaller than the diameter of the inner bore D IB , which generally defines the output portion 32 and thus the diameter of the output portion. Furthermore, in this embodiment, the bolt 18 has a ball 38 that makes up a large portion of the received bolt portion 26. The ball 38 has a ball diameter D B , which is between the diameter of the end part 30 (D EB) and the diameter of the inner bore 24 (D IB ). The respective diameters in this embodiment are measured at their longest dimension, and the radial dimensions or axial dimensions refer to the outward dimension or parallel to the housing axis A H .

[0036] The bearing 16 is located within the internal bore 24 of the housing 14. The discussion here focuses more on the output bearing 20, but the teachings relating to the output bearing 20 may also be applicable to the end bearing 22 or a bearing that does not have a split configuration as shown. The bearing 20 in the illustrated embodiment is made from a metal-based material, such as carburizing steel (e.g., AISI 8620), but other suitable materials are certainly possible. As described further below, the output bearing 20 is threaded, while the end bearing 22 is unthreaded. This provides for a better locking engagement with the output portion 32 of the housing 14, so a separate cover plate or housing closure may not be required.

[0037] As in the Fig. 2 through 4, the bearing 20 has a bearing body 40 that extends from an end surface 42 to an exit surface 44. Like the housing exit surface 34, the exit surface 44 of the bearing 20 extends primarily radially (e.g., a majority of the surface 44 extends in the radial direction). The end surface 42 of the bearing 20 is axially opposite the exit surface 44 and also extends primarily radially. Between the end surface 42 and the exit surface 44 are an axially extending outer diameter surface 46 and an opposing spherical stud contact surface 48. The outer diameter surface 46 is connected to the inner bore 24 of the housing 14, and the spherical stud contact surface 48 is connected to the received stud portion 26 of the stud 18.The bolt 18 and / or bearing 20 may be heat-treated using an induction heat treatment process or the like to improve hardening and wear resistance. Induction heat treatment may increase the fatigue strength of wear surfaces, such as the bearing bolt portion 26 and the spherical bolt contact surface 48.

[0038] The outer diameter surface 46 includes a mechanical lock 50 that engages the inner bore 24 of the housing 14. In this embodiment, the mechanical lock 50 includes a plurality of threads 52 that threadably engage the bore 24. In other embodiments, the mechanical lock 50 may take other forms or be added to the threaded engagement, such as an adhesive layer or one or more locking tabs, to name a few possible examples. In some embodiments, the threads 52 may be coated with an adhesive layer, such as a cyanoacrylate layer, to further strengthen the mechanical lock 50. A secondary securing method may be advantageous for the threads 52 to prevent the threads from becoming loose during operation.Other forms for the mechanical locking mechanism 50 are, of course, possible, such as a flat locknut or a set screw, to name a few examples. In still other embodiments, one or more locking pins, one or more roll pins, a staking method, or even a flat crimp connection may be used as the primary and / or secondary mechanical locking feature, to name a few non-limiting examples. In many embodiments, the mechanical locking mechanism 50 is effected by a structural feature of the bearing 20 itself, not just by a feature of the housing 14 (e.g., a swaged lip or a bead).

[0039] In some embodiments, it may be advantageous to provide the mechanical lock 50 with a proof load that exceeds the pull-out force for the bolt 18. In the illustrated embodiment, the size of the threads 52 can determine the level of the pull-out force of the bolt 18. It is therefore advantageous to select a thread size whose proof load exceeds the required pull-out force for the bolt 18. This arrangement allows the exit area 32 of the housing 18 to be configured without a crimp or press lip, as shown in Fig. 1, because the mechanical lock 50 between the bearing 20 and the housing 14 can maintain a desired arrangement for the internal components of the joint 10. This, in turn, can allow for a larger pin stroke angle or pin pivot angle θ, as described further below. The mechanical lock 50 can also help control the torque of the pivot pin 18.

[0040] Fig. 2 also shows an optional inner bearing 54 that may be used between the bearing 20 and the inner bore 24 of the housing 14. The inner bearing 54 may have a clearance or interference fit within the inner bore 24 of the housing 14. The inner bearing 54 may have an inner thread diameter that engages the threads 52 of the bearing 20. An inner bearing 54 may serve to control the concentricity of the pin ball 38 and the output bearing 20 without undesirably affecting the rotational or articulating torque of the pin 18.

[0041] Regardless of whether the optional inner bearing 54 is used or installed directly into the inner bore 24 of the housing 14, it may be helpful to provide fasteners to enable more efficient installation. In this embodiment, a plurality of drive holes 56 are located on the radially extending exit surface 44 of the bearing 20. The drive holes 56 may be designed to accommodate a wrench or other tool to facilitate engagement of the mechanical lock 50. The preload may be adjusted during assembly by threading the bearing 20 into the housing and reducing the play between the pin ball 38 and the bearing set 16. Accordingly, the assembly process may be simplified by using a torque wrench and a wrench as opposed to more complicated assembly equipment. For example, for crimped housings, as shown in Fig. 1A, sophisticated presses may be required.

[0042] The joint 10 allows for a set preload for the bearing 20 while withstanding tensile loads and proper positioning during operation, and advantageously allows for trouble-free movement of the bolt 18. At the exit portion 32 of the housing 14 there is a radially unobstructed bolt stroke area or bolt pivot area 58. As in the embodiment of Fig. 2 compared to Fig. 1, the radially unobstructed bolt pivoting area 58 has a part of the housing inner bore diameter D IB which is continuous between the exit surface 44 of the bearing 20 and the exit surface 34 of the housing 14. In some embodiments, the housing inner bore diameter D IB at least partially in the radially unobstructed bolt pivoting area 58. As shown, in contrast to Fig. 1 does not have a crushed or squashed edge. Instead, Fig. 2, the exit surface 34 of the housing is primarily radially extending and provides a larger pin pivot range 58 than cranked or swaged ends. However, it should be noted that with threaded arrangements in the inner bore 24, the radial extent can be defined at the top of the threads, so that the arrangement still has a uniform or at least partially extended radial extent. Furthermore, in some embodiments, the output bearing 20 can be arranged closer to or directly adjacent to the exit surface 34 of the housing than is specifically shown. Accordingly, the axial length of the housing 14 and the inner bore 24 can vary, whereby the arrangement of the radially unobstructed pin pivot range 58 differs from the explicit illustration in Fig. 2. As can be seen from the comparison of the Fig. 1A and Fig. 1B with Fig. 2, the bolt 18 in the present embodiment can pivot within the radially extending space, which is generally defined as the radial extent of the bearing exit surface 44, while in the Fig. 1A and Fig. 1B the housing blocks the bolt and projects inward toward the bolt to block this radial space.

[0043] The radially unobstructed bolt pivoting range 58 of Fig. 2 allows a bolt pivot angle θ that can be larger than with cranked or swaged housings, as in Fig. 1A. In Fig. 1A, the maximum bolt pivot angle is specified as approximately 12°, while the maximum bolt pivot angle with the radially unobstructed pivot range 58 of Fig. 2 is approximately 20-30°, particularly 25-30°, or specifically 27° in the illustrated embodiment. The bolt pivot angle is typically the amount by which the bolt axis A Swith respect to the housing axis A Hcan pivot. The larger pin pivot angle θ can be achieved, at least in part, in the embodiments of the present application through the use of the mechanically locked output bearing 20 rather than solely through a mechanical lock from the housing structure, which may eliminate the need for a threaded cover plate or the like disposed between the bearing output surface 44 and the housing output surface 34. Without a threaded cover plate, the radially unobstructed pin pivot range 58 can be larger without compromising proper load support. Accordingly, the compact structure can help maintain power and load requirements while allowing for a greater degree of pin travel.The mechanically locked output bearing 20 with threads 52 can adjust the preload appropriately without overly compromising the radial space at the output area of ​​the housing 14. The increase in bolt travel can also be influenced by other variables in the connection design.

[0044] It is to be understood that the foregoing is a description of one or more preferred embodiments of the invention. The invention is not limited to the particular embodiment(s) disclosed herein, but is defined solely by the following claims. Furthermore, the statements contained in the foregoing description refer to particular embodiments and are not to be construed as limitations on the scope of the invention or the definition of terms used in the claims, unless a term or phrase is expressly defined above. Various other embodiments and various changes and modifications of the disclosed embodiment(s) will become apparent to those skilled in the art. All such other embodiments, changes, and modifications are intended to be within the scope of the appended claims.

[0045] As used in this specification and the claims, the terms "for example," "e.g.," "for instance," "such," and "like," as well as the verbs "comprising," "having," "including," and their other verb forms, when used in connection with an enumeration of one or more components or other items, are each to be construed as open-ended, meaning that the enumeration is not to be considered as excluding other, additional components or items. Other terms are to be interpreted as broadly as possible unless used in a context that requires a different interpretation. Furthermore, the term "and / or" is to be construed as an inclusive OR. Therefore, for example, the phrase "A, B, and / or C" is to be construed to include all of the following: "A"; "B"; "C"; "A and B"; "A and C"; "B and C"; and "A, B, and C."

Claims

[1] A socket joint having the following: a bolt having a received bolt portion and a fixing bolt portion; a bearing at least partially surrounding the bolt at the received bolt portion, the bearing having an end surface and an exit surface, the exit surface being opposite the end surface; and a housing at least partially surrounding the bearing, the housing extending from an end portion to an exit portion having an exit surface, the housing having an internal bore having a housing internal bore diameter, the bearing and the received pin portion being at least partially disposed within the internal bore, the housing internal bore diameter being consistent or at least partially expanding between the exit surface of the bearing and the exit surface of the housing such that a radially unobstructed pin pivot range is present at the exit portion of the housing. [2] The socket connection according to claim 1, wherein the inner bore of the housing is designed to allow a maximum bolt pivot of between 20-30°. [3] The socket joint according to claim 1, wherein at least a portion of the bearing has a mechanical interlock with the inner bore of the housing. [4] The socket joint according to claim 3, wherein a proof load of the mechanical lock exceeds a bolt pull-out force amount. [5] The socket joint of claim 3, wherein the bearing is a split bearing having an end bearing and an output bearing, an outer diameter of the output bearing having the mechanical interlock with the inner bore of the housing. [6] The socket connection according to claim 5, wherein the mechanical locking is a threaded engagement. [7] The socket joint according to claim 5, wherein the starting bearing is threaded and the end bearing is unthreaded. [8] The socket connection according to claim 1, wherein the exit region is formed without a crimp or swaged lip. [9] The socket joint according to claim 1, wherein a preloading step defines the end portion and the output portion, wherein the bolt has a ball having a ball diameter and the end portion has an end portion diameter, the ball diameter being between the inner bore diameter and the end portion diameter. [10] The sleeve connection according to claim 9, wherein the radial extent of the preload step coincides with the longest radial extent of the bearing. [11] The socket joint according to claim 1, wherein the exit surface of the housing is substantially radial. [12] The socket joint according to claim 1, wherein the exit surface of the bearing has a plurality of drive holes. [13] The socket joint according to claim 1, wherein the end portion of the housing is part of a tie rod end portion. [14] The sleeve joint according to claim 1, which has an inner bearing between the bearing and the inner bore of the housing. [15] The socket joint according to claim 1, wherein the bearing has a heat-treated spherical bolt contact surface.

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