Abstract:
A pivot socket of the present invention incorporates a stud shaft component having a lower part-spherical head portion disposed within a housing cavity, and an axial pin extension extending upward into the cavity therefrom. The lower part-spherical head portion seats against a partial spherical bearing surface disposed within the housing cavity, and the axial pin extension is enclosed within a corrugated or crinkled coil compliance bearing formed from sheet steel. During use, lateral and axial loads imparted on the stud shaft are transformed into radial and axial component forces at the partial spherical bearing surface and the corrugated or crinkled coil compliance bearing. The radial force components are distributed to the interior walls of the housing cavity, while the axial force components are transferred axially through the corrugated or crinkled coil compliance bearing to the end closure components secured to the housing. Little or no lateral force components are transferred to the corrugated or crinkled coil compliance bearing from lateral loads imparted on the stud shaft, thereby reducing wear on the pivot socket components and extending the useful life thereof.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This is a divisional application related to U.S. patent application Ser. No. 09/566,288 filed May 5, 2000, from which priority is claimed. 
    
    
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     Not Applicable. 
     BACKGROUND OF THE INVENTION 
     This invention relates to the design of movable sockets, for example, ball joints as used in automotive steering and suspension systems, and more particularly, to a movable socket configured with a spherical or part-spherical bearing surface and a projecting pin stud restrained within an elastomeric or spring-centered compliance bearing. The movable socket of the present invention is additionally configured to have increased durability under conditions of high load and misalignment and to be assembled using conventional techniques. While the present invention is described in detail with respect to automotive applications, those skilled in the art will recognize the broader applicability of the invention. 
     Conventional ball joints, and other movable sockets are used, for example, in automotive steering and suspension applications. The sockets comprise a housing having a circular cylindrical internal surface, a ball stud with a part-spherical ball head contained in the housing, and a synthetic resin or sintered alloy bearing member supporting the ball head within the housing. These components are commonly installed into the housing through a posterior opening, with the ball stud extending outward through an axially disposed anterior opening of a smaller diameter than the ball head. Traditionally, the posterior opening is closed by means of a cover-plate, spun, swaged, or welded in place. Once secured in place, the cover-plate presses on the bearing member either directly or indirectly through a resilient rubber intermediate component. 
     Several ball joint designs incorporating a projecting pin from the upper surface of the ball stud are shown in the prior art. These designs are intended to limit angular movement of the stud relative to the housing in which it is contained. 
     U.S. Pat. No. 3,790,195 issued to Edward J. Herbenar on Feb. 5, 1974 discloses a preloaded socket joint for an automotive steering linkage. The &#39;195 socket joint is primarily for rotational movement with a stud projecting from an internal cavity housing and having a part-spherical bulged section received in the housing and seated against a spherical face seat adjacent the projecting point of the stud from the housing. The stud further includes an axial extension beyond the half sphere within the housing which is received in a bearing with a resilient member entrapped between the wall of the cavity and the bushing. The opposite end of the housing cavity from the point of projection is closed by a cap which applies a preload to the axial end of the stud within the cavity and to the resilient member. As can be seen in FIG. 1 of the &#39;195 patent, all axial loads on the stud are transferred either directly through the stud itself to the cap which closes the housing, or through the bushing and resilient member to the cap. 
     U.S. Pat. No. 3,945,737 issued on Mar. 23, 1976, also to Edward J. Herbenar discloses a modification of the socket joint shown in the &#39;195 patent. The &#39;737 pivot joint provides a housing with a part-spherical bearing seat at one end thereof, a recessed closure cap secured in the other end thereof, and a stud having a shank projecting freely into the housing with a head tiltable on the seat. The stud further includes a tapered pin depending from the head and bottomed directly on the closure plate together with an axially split rubber bushing surrounding the pin and snugly seated in the housing. A wear take-up member between the closure plate and the bushing urges the bushing toward the head of the stud, and a ring surrounding the recess of the closure plate limits the tilting of the stud on the bearing seat. In this design, the compressive loads of the stud and the angulation loads of the stud are taken by the same member, i.e. the axially split, resilient bushing with a tapered bore. Thus, the design inhibits freedom in selecting an axial preload independently of angulation considerations and vice-versa. 
     U.S. Pat. No. 5,597,258 issued to Kincaid et al. on Jan. 28, 1997 discloses a preloaded pivot joint with a stud capable of rotation and angulation. The preloaded pivot joint is designed such that different internal components transfer the respective lateral loads, axial compression loads, and angulation loads experienced by the stud. Specifically, as seen in FIG. 1 of the &#39;258 patent, the stud incorporates a hemi-spherical portion for transferring lateral loads to a fixed bearing seat within the stud housing, a concentric convex tip for transferring compressive (axial) loads directly to a spring biased bearing seat, and a cylindrical extension between the hemi-spherical portion and the convex tip for radially transferring angulation loads to a hardened cylindrical metal ring of a resilient composite bushing. 
     Each of these prior art pivot sockets includes compliance components formed of a resilient material such as rubber, polyurethane, and the like, which surrounds a projection pin portion of the stud and which transfers some form of loading from the stud to the housing. Accordingly, it is highly advantageous to develop a preloaded pivot joint wherein a single compliance component transfers both axial and angulation loads to either the hardened housing walls or the end closure components, limiting the movement of the stud, but which does not carry lateral loads, reducing wear on the pivot socket components and extending the useful life thereof and which provides freedom in selecting an axial preload independently of stud angulation considerations. 
     BRIEF SUMMARY OF THE INVENTION 
     Among the several objects and advantages of the present invention are: 
     The provision of a pivot socket employing a lower partially-spherical bearing surface to seat a stud having an axial extension within a housing cavity, and further employing a resilient component to surround the axial extension and to transfer axial load components from the bearing surfaces to end closure components; 
     The provision of the aforementioned pivot socket wherein the resilient component experiences little or no direct radial force when lateral forces are imparted to the stud; 
     The provision of the aforementioned pivot socket wherein the stud includes a partially spherical portion configured to seat against the lower partial spherical bearing surface; 
     The provision of the aforementioned pivot socket wherein the lower partial spherical bearing surface transfers lateral loads radially and axially from the partially spherical stud portion to the housing; 
     The provision of the aforementioned pivot socket wherein a preload component transfers axial loads stud portion axially to the resilient component surrounding the axial extension of the stud; 
     The provision of the aforementioned pivot socket wherein the resilient component surrounding the axial extension of the stud extends from the end closure components to adjacent an upper surface of the preload component; 
     The provision of the aforementioned pivot socket wherein a preload component is interposed between the resilient component and the upper surface of the partially spherical stud portion; 
     The provision of the aforementioned pivot socket wherein the resilient component acts alone to provide both the axial preload between an upper spherical bearing and the lower partially spherical bearing, as well as providing resistance to angular displacement of the stud member; and 
     The provision of the aforementioned pivot socket wherein the configuration of the resilient component permits assembly of the pivot socket using conventional methods. 
     Briefly stated, a pivot socket of the present invention incorporates a stud shaft component having a part-spherical head portion disposed within a housing cavity, and an axial pin extension extending upward into the housing cavity. The part-spherical head portion is seated against a lower partial spherical bearing surface disposed within the housing cavity, and the axial pin extension is enclosed within a resilient cushion. During use, lateral or axial loads imparted on the stud shaft are transformed into radial and axial component forces at the bearing surface. The radial force components are transferred primarily to the interior walls of the housing cavity, while the axial force components are transferred axially through the resilient cushion to the end closure components secured to the housing. Little or no radial force components are transferred to the resilient cushion from lateral or axial loads imparted on the stud shaft, reducing wear on the pivot socket components and extending the useful life thereof. 
    
    
     The foregoing and other objects, features, and advantages of the invention as well as presently preferred embodiments thereof will become more apparent from the reading of the following description in connection with the accompanying drawings. 
     BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS 
     In the accompanying drawings which form part of the specification: 
     FIG. 1 is a sectional view of an embodiment of a preloaded pivot socket of the present invention, illustrating an elastomeric cushion resilient member; 
     FIG. 2 is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating an elastomeric cushion resilient member and Belleville washer preload configuration; 
     FIG. 3 is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating a conical spring resilient member; 
     FIG. 4 is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating a spring steel resilient member and Belleville washer preload configuration; 
     FIG. 5 is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating an elastomeric compliance bearing resilient member; 
     FIG. 6 is a perspective exploded view of the preloaded pivot socket of FIG. 5; 
     FIG. 7 is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating an elastomeric compliance bearing resilient member and slipper sleeve. 
     FIG. 8A is a section view of an alternate embodiment of the preloaded pivot socket of the present invention, illustrating a crinkled coil of spring steel as a compliance bearing resilient member; 
     FIG. 8B is a top-down cross sectional view of the alternate embodiment of the preloaded pivot socket of FIG. 8A, illustrating the arrangement of the crinkled coil of spring steel; 
     FIG. 9 is a sectional view of a second embodiment of the preloaded pivot socket of the present invention, illustrating an elastomeric cushion resilient member; and 
     FIG. 10 is a perspective exploded view of the preloaded pivot socket of FIG.  9 . 
    
    
     Corresponding reference numerals indicate corresponding parts throughout the several figures of the drawings. 
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     The following detailed description illustrates the invention by way of example and not by way of limitation. The description clearly enables one skilled in the art to make and use the invention, describes several embodiments, adaptations, variations, alternatives, and uses of the invention, including what is presently believe to be the best mode of carrying out the invention. 
     Turning to FIG. 1, a first embodiment of the pivot joint of the present invention is shown generally at  10 . The pivot joint includes a housing  12 , within which the various internal components of the pivot joint are enclosed. Housing  12  is generally cylindrical, with a central bore  14  of non-uniform radius having a posterior opening  16  and an anterior opening  18 . The radius of central bore  14  decreases to define a reduced diameter portion  20  at the base of the housing, adjacent anterior opening  18 . A circumferential groove  22  is formed in bore  14 , adjacent the posterior opening  16 . The exterior surface  26  of housing  12  may follow the general contour of the central bore  14 . In the embodiment illustrated, the surface  26  has an expanded ridge  28  formed in it. The ridge  28  is used for attachment of pivot joint  10  to other components (not shown). As may be appreciated, the ridge  28  also may be adapted for other specific kinds of installations employing threads or other connectors (not shown). 
     To assemble ball joint  10 , a lower bearing  30  sized to fit within central bore  14  is seated within housing  12 . The lower bearing  30  includes a central bore  32  axially aligned with a vertical axis VA of the housing, and an outer surface  34  of bearing  30  is designed to correspond to the surface  20  in housing  12 . The inner surface  35  of the lower bearing  30  is formed in a partially spherical shape to receive a stud  36 , and may include one or more crenellations or breaks  37  to facilitate expansion and contraction. 
     Stud  36  has a generally cylindrical body  38  and an enlarged spherical ball or head portion  40 . To assembly the pivot joint the lower end of the cylindrical body  38  is passed through central bores  32  and  14 , such that the lower part-spherical surface  42  of the head portion  40  rests on an inner part-spherical surface  35  of lower bearing  30  seated within housing  12 . The body  38  may include a uniform diameter upper portion  50  adjacent head portion  40 , a tapered central portion  52 , and a lower portion  54  of a narrow uniform diameter. A passage  55  through the lower portion  54  allows for the connection of additional components (not shown) thereto. The upper portion  50  is sized to fit within the central bore  32  of bearing  30 , with the central portion  52  and lower portion  54  extending through the anterior opening  18 , externally of housing  12 . It will be noted that there is a gap G of predetermined width between the anterior opening  18  and the upper portion  50 . This gap G or clearance permits conical and rotational movement of head portion  40  with respect to housing  12  with a predetermined limited range of movement. 
     Head portion  40  of the stud  36  additionally includes an upper part-spherical surface  56  having the substantially same radial dimensions as the lower part-spherical surface  42 . When assembled, the upper part-spherical surface  56  and the lower part-spherical surface  42  define a generally spherical bearing unit within housing  12  which permits the aforesaid conical movement of the stud  36 . 
     Projecting axially upward from the upper part-spherical surface  56  of stud  36  is a cylindrical axial extension or pin portion  58  coaxial with stud  36  and having a diameter approximately equivalent to that of the upper portion  50  of stud  36 . The length of the pin portion  58  is selected such that the face  60  of the pin portion is disposed below the circumferential groove  22  in the housing  12 . Those skilled in the art will readily recognize that the numerous size configurations for the stud  36 , the head portion  40 , and the pin portion  58  are possible, and will depend upon the particular application for which the pivot joint is utilized. 
     Once the lower part-spherical surface  42  of ball portion  40  is seated against the inner surface  35  of the lower bearing  30 , an upper bearing  62  having an outer surface  63  sized to fit within the central bore  14  and an inner part-spherical bearing surface  64  conforming to the upper part-spherical surface  56  of the head portion  40  is seated against within the housing  12 , against the upper part-spherical surface  56 . The upper bearing  62  may include a number of resected portions  65  and slits  66  for lubrication and to allow for contraction and expansion within the central bore  14 , so as to conform tightly against the surface  56 . 
     In the embodiment shown in FIG. 1, a shaped elastomeric cushion  68  having a central bore  70  sized to fit around the pin portion  58  of the stud  36  is seated against an upper face  72  of the upper bearing  62 . The elastomeric cushion  68  may be isolated from the pin portion by means of a steel sleeve (not shown). The outer diameter of the elastomeric cushion  68  is sized to fit within the central bore  14 , contacting the housing  12  and to extend slightly above the circumferential groove  22 . To enclose the installed components within the housing, and to apply a predetermined preload pressure to the upper bearing  62  and lower bearing  30 , an end closure cap  74  is installed within the circumferential groove  22  to close the posterior opening  16 , partially compressing the elastomeric cushion  68 . The end closure cap  74  may be retained within the circumferential groove  22  by any conventional means such as welding, spinning, or swaging of the housing  12 , and may contain an axially disposed grease fitting  75 . The compression of the elastomeric cushion  68  provides a resilient preload force downward from the end closure cap  74  and onto the upper face  72  of the upper bearing  62 . The upper bearing  62  transfers a portion of the preload force onto the head portion  40  of the stud  40  which, in turn, transfers the force axially to the lower bearing  30  and to the housing  12 . This preload force takes up any dimensional slop in the manner in which ball  40  is socketed in the bearings  30  and  62 . 
     In this configuration, when a lateral force is applied to the portions of the stud  36  which projects from housing  12 , the force is transferred radially into the lower bearing  30  and upper bearing  62 . Due to the part-spherical curvature of the inner surfaces of these bearings, and the partially spherical configuration of the head or ball portion  40  of stud  36 , a portion of the radially transferred force is directed outward against the housing  12 , and a portion of the force is directed axially upward through the bearing  62  and axially downward through the bearing  30 . The axially downward force is received in the lower portions of the housing  12  against which the bearing  30  is seated. The upper bearing  62  is not restrained against axial upward movement by any portion of the housing  12 . Hence, if unimpeded, the upper bearing  62  would move axially upward in response to a lateral force on the stud  36 . However, the elastomeric cushion  68  is interposed between the end closure cap  74  and the upper face  72  of the upper bearing  62 . Correspondingly, the component of the lateral force on the stud  36  which is directed radially upward through the upper bearing  62  is transferred through the elastomeric cushion  68  to the end closure cap  74  and the housing  12 . 
     In the event a direct axial load is applied to stud  36 , it will similarly be transferred though the upper bearing  62  to housing  12  and to elastomeric cushion  68  and end closure cap  74 . Only when angulation loads are applied to stud  36 , resulting in a rocking movement of the head portion  40  about a central pivot point will cause elastomeric cushion  68  to experience radial forces transmitted through pin portion  58 . By isolating elastomeric cushion  68  from radial forces due to axial and lateral loads on stud  36 , the wear on cushion  68  is reduced. 
     In a first alternate embodiment of the pivot joint of the present invention, shown in FIG. 2, a Belleville washer  76  is interposed between elastomeric cushion  68  and upper face  72  of upper bearing  62 . Prior to the closure of central bore  14  by end closure cap  74 , Belleville washer  76  is in a slightly conical configuration. The preload compression force applied through elastomeric cushion  68  by end closure cap  74  when it is seated within circumferential groove  22  to close posterior opening  16  deforms the Belleville washer to a substantially planar configuration, increasing the amount of preload force applied to the components within housing  12 . 
     Turning to FIG. 3, a second alternate configuration of the pivot joint of the present invention is shown, in which elastomeric cushion  68  is replaced by a conical compression spring  168 . Conical compression spring  168  is wound such that the lower portion of spring  168  seated on upper face  72  of upper bearing  68  is disposed apart from pin projection  58 , and seated within a recessed channel or groove (not shown) to prevent radial motion. Alternatively, the lower portion of spring  168  contacting upper face  72  may be wound so as to additionally contact housing  12 . Conversely, the upper portion of conical compression spring  168  is wound in a smaller diameter, to simultaneously contact end closure cap  74  and pin portion  58  adjacent face  60 . 
     During installation, when conical compression spring  168  is enclosed between end closure cap  74  and upper face  72  of upper bearing  62 , it is compressed to provide a preload force on upper bearing  62 , lower bearing  30 , and stud  36 . As with elastomeric cushion  68 , the conical compression spring is configured to transfer axial loads resulting from axial or lateral forces on stud  36  upward to end closure cap  74  from upper bearing  62 . The upper portion of the spring  168  in contact with the pin portion  58  of stud  36  resists radial forces resulting from any angulation forces on stud  36 . Those skilled in the art will recognize that a variety of conical compression springs may be employed within the scope of the present invention. For example, the number of coils in the spring, the thickness of the coils, and the expansive force of the spring may be varied depending upon the particular application for which pivot joint  10  is designed. Alternatively, the shape of compression spring  168  may be that of an hourglass, such that the constricted portion of compression spring  168  contacts the surface of pin portion  58  approximately midway between head portion  40  and face  60 , while the upper coils of compression spring  168  are in contact with inner bore  14  of housing  12  and end closure cap  74 , adjacent circumferential groove  22 . Such an hourglass configuration may be composed of a pair of conical springs, positioned about pin portion  40  with one spring inverted relative to the other. 
     Turning to FIG. 4, a third alternate embodiment of pivot joint of the present invention is shown wherein conical compression spring  168  is replaced with a flared tube  268  formed from spring-steel. Flared tube  268  is formed with an upper cylindrical portion  270  having a diameter sized to contact the surface of pin portion  58  adjacent end closure cap  74 . A circumferential flange  272  extends radially outward from portion  270  to seat against the surface of end closure cap  74 . Lower portion  274  of flared tube  268  is flared outward in a radially increasing manner to seat against housing  12 . In a relaxed state, prior to the installation of end closure cap  74  in circumferential groove  22 , flared tube  268  has an overall length slightly greater than the distance between upper surface  72  of upper bearing  62  and circumferential groove  22 . Seating end closure cap  74  in circumferential groove  22  compresses flared tube  268  against upper face  72  of upper bearing  62 , causing lower portion  274  to flex and exert a preload force on upper bearing  62 , lower bearing  30 , and stud  36 . To further increase the preload force and to provide for an even distribution of axial forces between upper face  72  of upper bearing  62  and flared tube  268 , a Belleville washer  276  may be interposed between lower portion  274  and upper face  72 . The preload forces exerted by the installation of end closure cap  74  into circumferential groove  22  additionally result in a deformation of Belleville washer  276 . 
     As with elastomeric cushion  68 , flared tube  268  is configured to transfer axial loads resulting from axial or lateral forces on stud  36  upward to end closure cap  74  from upper bearing  62 . Upper portion  270  of flared tube  268  in contact with pin portion  58  of stud  36  resists radial forces resulting from any angulation forces on the stud  36 . Those skilled in the art will recognized that a variety of flared tubes  268  may be employed within the scope of the present invention. For example, the thickness of the tube, and the expansive force of the flare material may be varied depending upon the particular application for which pivot joint  10  is designed. Alternatively, the shape of flared tube  268  may be that of an hourglass, such that a constricted portion (not shown) of flared tube  268  contacts the surface of pin portion  58  approximately midway between head portion  40  and face  60 , while the upper portion is contact with housing  12  and end closure cap  74 , adjacent circumferential groove  22 . 
     Turning to FIGS. 5 and 6, a fourth alternate embodiment of pivot joint of the present invention is illustrated wherein elastomeric cushion  68  is replaced with an elastomeric compliance bearing  368 . Elastomeric compliance bearing  368  is composed of an outer metal ring  370  in contact with housing  12 , an inner bearing sleeve  372  sized to fit around pin portion  58 , and an intermediate ring  374  of elastomeric material disposed between outer ring  370  and sleeve  372 . Seated between elastomeric compliance bearing  368  and upper face  72  of upper bearing  62  is a Belleville washer  378  and a telescoping ring  380 . During installation, Belleville washer  378  is seated against upper face  72  of upper bearing  62 . Next, telescoping ring  380  is placed on Belleville washer  378 , and elastomeric compliance bearing  368  seated thereon. Finally, end closure cap  74  is installed within circumferential groove  22 . The installation of end closure cap  74  deforms Belleville washer  378  and crushes portions of telescoping ring  380 , such that the Belleville washer exerts a preload force on upper bearing  62 , stud  36 , and lower bearing  30 . 
     As with elastomeric cushion  68 , elastomeric compliance bearing  368  is configured to transfer axial loads resulting from axial or lateral forces on stud  36  upward to end closure cap  74  from upper bearing  62 . These axial loads are transferred from upper bearing  62  through Belleville washer  378  and crushed telescoping ring  380  to outer metal ring  370  of the elastomeric compliance bearing and to end close cap  74 . Inner bearing sleeve  372  in contact with pin portion  58  of stud  36 , and elastomeric intermediate ring  374  resists any radial forces resulting from angulation forces on stud  36 . Those skilled in the art will recognize that a variety of materials may be utilized to form elastomeric compliance bearing  368  within the scope of the present invention. For example, the thickness of outer ring  370  and inner sleeve  372  may be varied depending upon the particular application for which pivot joint  10  is designed. Alternatively, inner sleeve  372  may be eliminated, and the properties of elastomeric intermediate ring  374  varied to absorb radial forces directly from pin portion  58 . 
     Turning next to FIG. 7, a fifth alternate embodiment of the present invention pivot joint is shown wherein lower bearing  30  is replaced with a slipper sleeve  400 . Although shown in the context of the embodiment of FIG. 6, slipper sleeve  400  illustrated in FIG. 7 will readily be understood by one skilled in the art of pivot joint design to be usable with each embodiment disclosed herein. Utilizing slipper sleeve  400  in place of lower bearing  30  permits the pivot point of stud  36  to sit lower in housing  12 , such that a lower profile socket can be utilized. 
     FIGS. 8A through 10 illustrate alternate embodiments of the present invention pivot joint wherein upper bearing  62  and upper part-spherical surface  56  are eliminated, and the cylindrical axial extension or pin portion  58  is elongated. In place of upper part-spherical surface  56 , a flat radial upper surface  402  directly receives Belleville washer  378  and a first flat washer  380 . 
     Turning specifically to FIGS. 8A and 8B, a sixth alternative embodiment of the present invention pivot joint is shown wherein elastomeric cushion  68  is replaced with a resilient member comprising a corrugated or crinkled coil compliance bearing  410  formed from sheet steel. Crinkled coil compliance bearing  410  includes a number of radially orientated peaks  412  and valleys  414 , and is spiral wound about axial stud  58  such that each peak  412  on a first portion of spiral wound crinkled coil compliance bearing  410  is radially aligned, and in contact with, a valley  414  on a second portion of spiral wound crinkled coil compliance bearing  410 . Those skilled in the art will recognize that alternative windings of crinkled coil compliance bearing  410  are possible, and may include the use of two or more concentric rings (not shown) of crinkled coil compliance bearings arranged such that peaks  412  on a first ring are radially aligned, and in contact with, a valley  414  on a second ring. Seated between crinkled coil compliance bearing  410  and flat radial surface  402  is Belleville washer  378  and first flat washer  380 . During installation, Belleville washer  378  is seated against flat radial surface  402 . Next, first flat washer  380  is placed on Belleville washer  378 , and crinkled coil compliance bearing  410  seated edge-wise on the upper surface of first flat washer  380 . A second flat washer  415  is positioned on the upper edge of crinkled coil compliance bearing  410 , and a telescoping ring  416  is seated thereon. Finally, end closure cap  74  is installed within circumferential groove  22 . The installation of end closure cap  74  deforms Belleville washer  378  and crushes portions of telescoping ring  416 , such that the Belleville washer exerts a preload force on flat radial surface  402 , stud  36 , and lower bearing  30 . Also shown in FIG. 8A is a dust cover  420  secured to the lower portion of the housing, surrounding stud  36 . Dust cover  420  may be constructed from any flexible material to provide a protective enclosure for stud  36  and lower portion of the housing. 
     As with elastomeric cushion  68 , crinkled coil compliance bearing  410  is configured to transfer axial loads resulting from axial or lateral forces on stud  36  upward to end closure cap  74  from upper bearing  62 . These axial loads are transferred from flat radial surface  406  through Belleville washer  378  and first flat washer  380  to crinkled coil compliance bearing  410  and up to end closure cap  74  through second flat washer  415  and telescoping ring  416 . The contacting peaks  412  of crinkled coil compliance bearing  410  resist any radial forces resulting from angulation forces on the stud  36  by resiliently deforming. Lateral loads on stud  36  are transformed into a axial forces by the interaction of lower bearing  30  and stud  36 , and are transferred to end closure cap  74  through crinkled coil compliance bearing  410 . Those skilled in the art will recognize that a variety of materials may be utilized to form crinkled coil compliance bearing  410  within the scope of the present invention. For example, the resilience of the sheet steel may be varied depending upon the particular application for which pivot joint  10  is designed. Alternatively, the number of peaks  412  and valleys  414 , as well as number of spiral windings of crinkled coil compliance bearing  410  may be varied to absorb radial forces directly from pin portion  58 . 
     Turning specifically to FIGS. 9 and 10, a seventh alternative embodiment of the present invention pivot joint is shown wherein a resilient member comprising an elongated elastomeric cushion  468  rests on the upper surface of first flat washer  380 . Elongated elastomeric cushion  468  surrounds the length of the cylindrical axial extension or pin portion  58 , and is secured between the inner surface of the housing defining central bore  14  and the exterior surface of pin portion  58  by an interference fit. As with elastomeric cushion  68 , elongated elastomeric cushion  468  is configured to transfer axial forces resulting from axial or lateral loads on stud  36  upward to end closure cap  74  from flat radial surface  406 , however, the greater surface area of the elongated elastomeric cushion  468  permits the transfer of greater loads without permanent deformation or damage. These axial loads are transferred from flat radial surface  406  through Belleville washer  378  and first flat washer  380  to elongated elastomeric cushion  468  and up to end close cap  74  through second flat washer  415  and telescoping ring  416 . Elongated elastomeric cushion  468  additionally resists any radial forces resulting from angulation forces on stud  36  by resiliently deforming, allowing only minor freedom of movement of stud  36 . Those skilled in the art will recognize that a variety of materials may be utilized to form elongated elastomeric cushion  468  within the scope of the present invention. 
     In view of the above, it will be seen that the several objects of the invention are achieved and other advantageous results are obtained. Several embodiments are shown wherein the internal components of a pivot joint surrounding a partially spherical head portion of the stud transfer lateral and axial forces exerted on the stud axially to the end closure cap of the housing through internal components other than the stud itself. Simultaneously, these internal components are capable of providing a radial resistance to angulation forces applied to the stud and transferred to the components through a pin projection on the upper end of the stud within the housing. As various changes could be made in the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.