A vehicle door/tailgate handle assembly for unlatching either a combined door/tailgate and window as a unit or the window unit alone provides an improved centering/alignment feature which avoids reliance on prior known spirally wrapped, low tolerance, low cycle life springs. The handle assembly includes a handle grip, mounting base and a centering member which centers and aligns the handle grip on the mounting base. The handle grip is rotatably mounted in a shaft receiving passage on the mounting base and a centering member is slidably disposed on shaft for movement along and rotation with the shaft for slidable engagement with the rear side of the mounting base. When a rotational torque is applied to the handle grip, the centering member slides along the shaft away from the rear side of the mounting base to permit the handle grip to rotate between a first unlatching position and a second unlatching position. The centering member aligns the handle grip with the mounting base in a third, centered position when the rotational torque is removed from the handle grip. Preferably, the handle grip, mounting base and centering member include cooperating camming surfaces which are urged toward one another by a compression/coil spring having a high cycle life and low failure rate. Stop surfaces are preferably included on the handle grip and mounting base to limit the extend of rotational movement.

TECHNICAL FIELD AND BACKGROUND OF THE INVENTION 
     The present invention relates to handle assembly especially suited for vehicle doors and on tailgates on sport utility vehicles, vans, mini-vans, station wagons, and the like, and, more particularly, to a rear tailgate handle with improved centering and alignment with a mounting base. 
     Handles that are used to unlatch the tailgate of a vehicle are quite often also used to unlatch a window unit housed in the tailgate. Typically, the handle grip of the assembly assumes a neutral position in which both the window unit and the tailgate are latched. The handle must be rotated from its neutral position to one of two positions, with one position unlatching the tailgate and the other position unlatching the window unit in the tailgate. The direction of the handle grip's rotation dictates which of the two is unlocked for opening. For example, a counterclockwise rotation could unlock the tailgate while a clockwise rotation of the handle would then unlock the window unit in the tailgate. The un-rotated center position of the handle grip defines the neutral position of the assembly in which both the tailgate and the tailgate window are latched. 
     Conventional tailgate handles include spirally wrapped springs to center a handle grip on the handle mounting base in its neutral position. The spirally wrapped spring has distal ends which engage both the handle mounting base and the handle grip, with the spring being coiled around the handle mounting base to bias the handle grip to the center position, wherein the handle grip is aligned with the handle mounting base. 
     Several problems have developed with the conventional handles, however. As best shown in FIG. 1 of the drawings, over time the spirally wrapped spring can relax or its distal ends can bend and, eventually, no longer fully bias the handle grip to the center position. This results in a handle grip that is no longer aligned with the handle mounting base by an angular amount X (FIG. 1). Moreover, wrapped spring suppliers do not generally guarantee their springs for a tolerance less than ±7 degrees of play. While this particular non-aligned condition does not seriously affect the latching/unlatching function of the handle, the handle does have the appearance of being broken and is not aesthetically pleasing. 
     Second, the installation of a spirally wrapped spring is labor intensive and difficult. Conventionally, during installation, a first end of the spring is inserted through a slotted opening provided in a collar of the mounting base and into a receiving structure provided in the shaft, with the first end of the spring abutting a first side of the slotted opening to fix the end of the spring in a unilateral direction. The spring is coiled around the collar of the mounting base, and, then, the second end of the spring is inserted through the same opening in the mounting base, abutting a second side of the opening, and into the same receiving structure on the shaft. During such installation, the spring is easily bent; therefore, the quality of the installation and handle performance can be jeopardized. In addition, the spring is hard to grasp during such coiling and requires a significant level of manual dexterity to complete the assembly. During operation, when the handle grip is rotated, the shaft, which is fixed to the handle grip, rotates, pulling the first end of the spring while the second end of the spring is seated against the second side of the slotted opening. This causes the spring to twist and compress until the first end of the spring is rotated from the first side to the second side of the slotted opening, so that both ends of the spring abut the same side of the slotted opening. At this point the spring cannot undergo further twisting or compression, and the handle grip is fully turned in one direction. When the handle is released, the spring will expand and induce rotation in the shaft until the first end of the spring is again abutting the first side of the slotted opening. Similarly, when the handle is rotated in the opposite direction, the same operation occurs except that the second end of the spring will travel from the second side of the slotted opening to the first side of the slotted opening. When operated in this way, the wrapped spring tends to lose tension over time. Coupled with the imprecise tolerance levels in the manufacture of such springs, the loss in tension prevents full return of the shaft and handle grip, resulting in the above non-centered position. 
     Lastly, a spirally wrapped spring has a relatively low cycle life. The wrapped spring is typically mounted to the mounting base and the shaft of the handle grip at its free ends, but the free ends are bent inward to grip the sides of the slotted opening in the mounting base and the receiving structure in the shaft. The bends at the free ends increase stress concentration factors on the spring and, ultimately, may lead to breakage. When combined with the necessary cycles associated with a tailgate handle over the life span of a vehicle and environmental factors, such as exposure to extreme temperatures and corrosive substances, the overall cycle life of the spring is significantly reduced and, often, reduced to unacceptable levels for automobile manufacturers. 
     Consequently, there is a need for a door/tailgate handle that can maintain the alignment of the handle grip with its mounting base, perform all required latching/unlatching functions, and yet have a significantly longer cycle life. 
     SUMMARY OF THE INVENTION 
     Accordingly, the present invention provides a new and unique handle assembly, especially for vehicle doors, lift gates and/or tailgates on sport utility vehicles, vans, mini-vans, station wagons, and the like, which includes an improved centering feature to align the handle with its mounting plate except when the handle is in use. The handle grip is positively aligned with its mounting base through a centering member including camming surfaces which are continuously urged against one another to maintain the handle grip in alignment without looseness or play and without reliance on low tolerance, low cycle life spirally wrapped springs. 
     According to one aspect of the invention, a vehicle handle assembly includes a handle grip having front and rear surfaces and a shaft on the rear surface adapted to extend through a mounting base for the handle grip. The mounting base is adapted to mount the handle grip on a vehicle panel and includes front and rear sides and a shaft receiving passage extending therethrough. The shaft of the handle grip extends through and is journaled in the shaft receiving passage for rotational movement therein. A centering member is slidably disposed on the shaft for longitudinal movement along the shaft and rotation with the shaft. The centering member is positioned on that portion of the shaft which extends through the shaft receiving passage in the mounting base and slidably engages the rear side of the mounting base. When a rotational torque is applied to the handle grip, the centering member slides along this shaft away from the rear side of the mounting base to permit the handle grip to rotate between a first unlatching position and a second unlatching position. The centering member aligns the handle grip with the mounting base in a third, centered position when the rotational torque is removed from the handle grip. 
     In preferred aspects of the invention, a spring is telescoped over the shaft and held in engagement with the centering member by a retaining clip. Preferably, the spring is a coil spring having a compression force selected such that when a rotational force that induces a compression force greater than the selected compression force of the spring is applied to the handle grip, the centering member will move along the shaft in the intended manner and compress the spring. 
     In other aspects, the handle assembly preferably includes cooperating camming surfaces on the centering member and the rear of the mounting base. Preferably, such camming surfaces include at least one notch in the mounting base and a corresponding camming projection formed in the shape of a triangularly shaped tooth engaging the notch. The camming surfaces on the tooth extend at an angle to the shaft axis for proper camming operation. In addition, a second camming surface may be included between the handle grip and the centering member to eliminate any play or looseness of the handle grip when in the centered position. Such additional camming surface preferably includes a notch in the handle grip and a projecting tooth having angled camming surfaces on the centering member at a position spaced from the first camming surface. Preferably, the centering member is a cup-shaped, annular body having a base and a cylindrical wall with a shaft opening extending through the base and at least one of the above mentioned camming surfaces formed on the cylindrical wall for slidably engaging the corresponding camming surface on either the mounting base or handle grip. 
     In addition, the handle assembly preferably includes a stop on the handle grip which engages shoulders or stop surfaces on the mounting base to limit rotation of the handle grip whereby the camming surfaces remain engaged at all times so that the handle grip is returned to its centered position when the rotational force is removed. 
     As will be understood, the vehicle door/tailgate handle assembly of the present invention provides numerous advantages over prior known handle assemblies used on vehicle tailgates or doors. The handle assembly overcomes the lack of alignment between the handle and mounting base which is evident with prior known handle assemblies using spirally wrapped springs or other methods. The handle grip on the present invention is continuously centered and aligned with the mounting base by the combination of a cammed centering member and a compression/coil spring which constantly urges the centering device to return the handle grip to its parallel, centered position. The compression/coil spring is far less susceptible to relaxation than a spirally wrapped spring. The handle grip maintains its aligned position with the mounting base throughout the life of the vehicle. Moreover, even when the compression/coil spring in the present invention experiences limited relaxation, such relaxation merely causes reduced handle effort but does not effect maintenance of the centering/alignment feature. Further, such alignment is maintained with little or no looseness or play between the handle grip and the mounting base when in the centered position, unlike prior known assemblies. The compression/coil spring is less susceptible to fatigue or failure because its method of application relies on compression instead of twist-type tensioning. In addition, the force is applied in a relatively uniform manner over the entire spring such that the coils of the spring are compressed rather than twisted. There are no bent ends to increase local stress in the spring. Consequently, the cycle life of the preferred compression/coil spring is increased some five to one hundred times over the spirally wrapped spring. Thus, repair and replacement costs are significantly reduced. Further, manufacture of the present vehicle handle assembly is easier than with prior known handles incorporating spirally wrapped springs since the parts of the present invention are easily telescoped and slide over one another with only a single retaining clip being installed to finish the assembly. The previous requirements of manual dexterity and stretching of a twisted, spiral spring are completely unnecessary, thereby reducing assembly time and increasing reliability of the resultant product. 
     These and other objects, advantages, purposes and features of the invention will become more apparent from a study of the following description taken in conjunction with the drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a front elevation of a prior art rear tailgate handle mounted on a vehicle panel illustrating the non-parallelism between the handle grip and the mounting base; 
     FIG. 2 is a front elevation of the vehicle handle assembly of the present invention mounted to a vehicle panel such as a rear tailgate; 
     FIG. 3 is an exploded perspective view of the vehicle handle assembly of FIG. 2; 
     FIG. 4 is a top plan view of the vehicle handle assembly with the handle grip in the mounting base and the centering member fully engaged with the collar of the mounting base; 
     FIG. 5 is a sectional plan view of the handle assembly taken along line V--V of FIG. 2, illustrating the handle grip mounted to the mounting base and the centering member installed on the shaft handle grip and fully biased against the mounting base; 
     FIG. 6 is a side elevation of the vehicle handle assembly showing the handle grip mounted in the mounting base; 
     FIG. 7 is a sectional side elevation of the vehicle handle assembly taken along line VII--VII of FIG. 2, illustrating the centering member fully biased against the handle grip; 
     FIG. 8 is a top plan view of the handle grip; 
     FIG. 9 is a bottom plan view of the handle grip; 
     FIG. 10 is a side elevational view of the handle grip showing the positioning lugs; 
     FIG. 11 is an enlarged partial plan view of the handle grip with the centering member positioned to abut the lower portion of the handle grip positioning collar; 
     FIG. 12 is a rear elevation view of the handle grip; 
     FIG. 13 is a front elevation of the handle mounting base; 
     FIG. 14 is a rear elevation of the mounting base; 
     FIG. 15 is a sectional plan view of the mounting base taken along line XV--XV of FIG. 3; 
     FIG. 16 is a first side elevational view of the centering member; 
     FIG. 17 is a second side elevational view of the centering member taken at 90° to that of FIG. 16; and 
     FIG. 18 is a top plan view of the centering member. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Referring to FIGS. 2 and 3, a vehicle handle assembly 10 of the present invention is shown mounted to a rear tailgate panel 11 of a vehicle. Handle assembly 10 is mounted to the panel 11 by a mounting base 13 preferably by a pair of threaded studs 13a, 13b which pass through the body sheet metal and are secured with nuts or other fasteners on the opposite side of the sheet metal. A handle grip 12 is journaled in mounting base 13 for rotation between a door unlatching position (counter clockwise in FIG. 2), a window unlatching position (clockwise in FIG. 2), and a centered or neutral position wherein grip 12 is generally parallel to base 13. Handle grip 12 is centered on the mounting base 13 by a centering member 14, as explained below. Tailgate panel 11 typically is of the type including a hinged door or panel which may be unlatched to swing open via handle assembly 10. In addition, panel 11 usually also includes a hinged window which may be unlatched and opened also using assembly 10. As explained more fully below, operation of the handle grip 12 in opposite directions opens either the door or panel and window together or just the window as desired. 
     Handle grip 12 comprises a T-shaped body 15 having front and rear surfaces 15a and 15b and a neck 17 depending from rear surface 15b. Extending from the rear surface 15b of the T-shaped body 15 and through neck 17 is a shaft 18 whose longitudinal axis 19 is coextensive with the central axis of neck 17. Neck 17 includes a cylindrical base portion 20 which extends from lower surface 15b to a reduced diameter positioning collar 21, with a resilient, o-ring seal 22 positioned therebetween in a groove to provide a water resistant seal between the handle grip 12 and the mounting base 13. Preferably, the T-shaped body 15 and the neck 17 are integrally formed by injection molding from a plastic material. More preferably, the T-shaped body is formed from a resinous material, such as ABS plastic, and, most preferably, formed from CAPRON ® 8267 material available from Allied Signal of Morristown, N.J. Shaft 18 is preferably metal and, more preferably, steel and is typically insert molded within neck 17 and body 15 of grip 12. Most preferably, shaft 18 is steel with zinc plating for salt corrosion protection. 
     Handle grip 12 extends into and is journaled in mounting base 13 through a shaft opening 23 that extends through the mounting base 13. Preferably, mounting base 13 is formed by injection molding from a plastic material. More preferably, the mounting base 13 is formed from a resinous material, such as ABS plastic, and, most preferably formed from CAPRON ® 8267. As shown in FIGS. 3-7, mounting base 13 has a member, centering collar 25, projecting from its rear surface 24. Centering collar 25 cooperates with centering member 14 to align the handle grip 12 with mounting base 13 and is aligned with shaft opening 23 to define a continuous shaft passage 26 through which shaft 18 extends. Handle grip 12 is supported in passage 26 by a stop 28 and a shoulder 29 that are formed on positioning collar 21. Stop 28 and shoulder 29 rest on first, second, and third circumferentially spaced abutments 30, 31, and 32 which project radially into passage 26. As can be seen in FIGS. 13-15, first abutment 30 includes two offset planar surfaces 30a and 30b, with surface 30a positioned below surface 30b to provide support for stop 28. Surface 30b provides support for shoulder 29. Similarly planar surfaces 31a and 32a of abutments 31 and 32, which are coplanar with surface 30b, provide support at spaced circumferentially spaced locations for shoulder 29 and are circumferentially spaced from abutment 30 to support handle 12 at approximately three equally spaced points. 
     Stop 28 provides several functions. As described above, stop 28 provides a support surface for handle grip 12 in passage 26. Moreover, stop 28 provides a limit stop for the handle grip to limit the rotation of the handle grip 12 between a first rotational position wherein the tailgate is unlatched and a second position wherein the window unit in the tailgate is unlatched. As planar surface 30a is lower than planar surface 30b and the other planar surfaces 31a and 32a of the abutments 31 and 32, stop 28 is positioned between the vertical faces 30c and 31d of abutments 30 and 31 and, therefore, limits the rotation of the handle grip between vertical faces 30c and 31d of the adjacent abutments 30 and 31. The spacing between the vertical faces 30c and 31d together with the width of stop 28 control the range of rotational motion of handle grip 12. This range of motion is preferably between 0° and 120° and, more preferably, between 0° and 80° . Most preferably, the angle of rotation of the handle grip 12 between the window unlatching position and the tailgate unlatching position is approximately 76°. As will be more fully understood in reference to the discussion of the centering member, the limited rotational movement of handle grip 12 with respect to the mounting base 13 assures that the centering member properly cooperates with the mounting base 13 to center the handle grip to one preferred orientation--the orientation illustrated in FIG. 2. 
     An important aspect of assembling any handle is to provide an assembly that can be quickly and easily assembled in the proper order and with the sub-components installed in the proper orientation. To achieve this in the present invention, handle grip 12 includes positioning lugs 33, 34, and 35 (FIGS. 3 and 8-11). Positioning lugs 33, 34, and 35 extend outwardly from positioning collar 21 to provide a guide for inserting handle grip 12 into mounting base 13. Lugs 33, 34, and 35 are circumferentially spaced around collar 21 and are positioned to align with the passages 33a, 34a, and 35a formed between the vertical faces 30d and 31d, 31d and 32d, and 32d and 30d of circumferentially spaced abutments 30, 31, and 32 (FIG. 13). Once the lugs 33, 34, and 35 are aligned with passages 33a, 34a, and 35a, respectively, handle grip 12 may be inserted and rotated to releasably lock the handle grip into mounting base 13. More specifically, after handle grip 12 is fully inserted into mounting base 13, handle grip 12 is rotated so that stop 28 slides on to surface 30a of abutment 30 and lugs 33, 34, and 35, extending past vertical surfaces 30d, 31d, and 30d of the abutments, and slide over locking surfaces 30e, 31e, and 32e on the rear side of abutments 30, 31, and 32, respectively, to lock handle grip 12 against movement along the axis of passage 26 in mounting base 13. In one aspect, these locking lugs are load transferring devices. In another aspect, the locking lugs prevent the handle grip from disengaging with the mounting base while the other components of the handle are being installed. 
     To further aid in the assembly of the handle and to enable centering member 14 to impart rotation to the shaft, shaft 18 includes first and second planar surfaces 18a and 18b. Planar surfaces 18a and 18b extend substantially over the full exposed length of the shaft, with first planar surface 18a formed at a first distance from longitudinal axis 19 of shaft 18 and second planar surface 18b formed at a second distance from axis 19 of shaft 18. Preferably the first distance is less than the second distance and, as a result, the width of first surface 18a is greater than the width of the second surface 18b and the size of the shoulders 18c and 18d formed at the transitions from the fully circular cross-section of the shaft to the planar surfaces are similarly proportioned (FIG. 7). As will be more fully explained, by making planar surfaces 18a and 18b with different dimensions, centering member 14, which slips on the end of the shaft for longitudinal movement along the shaft, can be installed in only one of two orientations. 
     Centering member 14 is also preferably molded from resinous plastic and, more preferably from, acetal. Acetal (Celcon M90) is available from Celanese Products, Chattham, N.J. As shown in FIGS. 3, 16-18, centering member 14 is an annular, cup-shaped member having a base 36 and a cylindrical wall 37 extending around the base 36 to define a spring cavity 38 therein (FIGS. 3, 5 and 7). To mount the centering member on the shaft, base 36 includes shaft opening 39 to receive shaft 18 of handle grip 12. Preferably, shaft opening 39 substantially matches the cross-sectional shape of shaft 18 so that rotation of the shaft imparts rotation to centering member 14 when the handle grip 12 is rotated about longitudinal axis 19. Furthermore, since shaft opening 39 in the centering member substantially matches the cross-sectional shape of the shaft, centering member 14 is mounted on shaft 18 in only one of two orientations--the correct orientation in which spring cavity 38 faces outwardly toward the distal end of the shaft or an incorrect position in which the spring cavity faces the mounting base. As the number ways to mount the centering member is reduced to two, the odds of an improper assembly are significantly reduced. 
     In order to allow centering member 14 to urge handle grip 12 into the correct position, camming surfaces 40 are provided on cylindrical wall 37 of centering member 14 and, preferably, are formed as triangularly shaped teeth 41 which project from opposed sides of the cylindrical wall 37. Teeth 41 have sloping sides 41a and 41b that preferably form an angle with respect to each other in the range of 20° to 70°. As shown in FIGS. 3 and 14-16, the sloping sides of teeth 41 also form an angle with respect to the shaft axis, preferably an angle in the range of 10° to 35°. Centering collar 25 of mounting base 13 is also provided with matching camming surfaces 42 (FIGS. 4, 14 and 15) which cooperate with camming surfaces 40 to align the centering member 14 and, in turn the handle grip 12 with mounting base 13, as will more fully explained. Camming surfaces 42 are provided by notch recesses formed in the cylindrical side wall 25a of collar 25. 
     Preferably, centering member 14 further includes a second set of camming surfaces 43 which cooperate with the positioning collar 21 of handle grip 12 to slidably engage handle grip 12. Camming surfaces 43 are similarly formed on teeth 44 having triangular shaped distal ends 45 which project from base 36 of centering member's 14 cup-shaped body to engage camming surfaces 46 and 47 provided on handle grip 12 (FIGS. 3, 11, 16-19). Teeth 44 are positioned on base 36 about shaft opening 39 on opposed sides of opening 39 and are oriented at 90° to teeth 41. Preferably, teeth 44 are closer to shaft opening 39 than teeth 41 and have sloping sides 44a and 44b that preferably form an angle with respect to each other in the range of between about 30° to 35°. As can be seen in FIG. 11, sloping sides 44a and 44b are angled with respect to the shaft axis 19 and, preferably, form an angle in the range of 15° to 55° with respect to the shaft axis 19. Camming surfaces 46 on handle grip 12 are formed on positioning collar 21 by a notch recess 48 that extends through cylindrical wall 37 and lug 33 (FIG. 12). Camming surfaces 47 are provided by a notch recess 49 that extends through cylindrical wall 37 (FIG. 8). Preferably, notches 48 and 49 are positioned on diametrically opposed sides of the positioning collar 21. When teeth 44 are positioned in notches 48, 49, handle grip 12 is prevented from any "play" or rocking action with respect to mounting base 13 while handle grip 12 is in its neutral, centered position. 
     As best seen in FIGS. 3 and 11-13, a pair of abutment projections 50 and 51 are also provided on centering member 14. Projections 50 and 51 align with shoulders 18c and 18d on shaft 18 (FIG. 7) so that when centering member 14 is biased against centering collar 25 of mounting base 13 and positioning collar 21 of handle grip 12, projection 50 abuts shoulder 18d and projection 51 abuts shoulder 18c to provide reinforcement to base 36 and teeth 44. Moreover, projections 50 and 51 further aid the releasable coupling of centering member 14 to shaft 18 and handle grip 12, and reduce the play between handle grip 12 and the mounting base 13. 
     As best seen in FIGS. 3 and 4, a compression spring 53, preferably formed from spring steel coated with a corrosion resistant plating, such as zinc, is telescoped over shaft 18 and urges centering member 14 against centering collar 25 and positioning collar 21. The stiffness of the spring 53 is dictated by the desired "handle effort", i.e., the stiffer the spring the greater the handle effort. Preferably, spring 53 has a compression force within the range of between about 1.95 N/mm and 3.05 N/mm. By biasing centering member 14 against centering collar 25 and positioning collar 21, centering member 14 urges handle grip 12 to its neutral, centered position in which it is aligned with base 13. The preferred plastic of centering member 14 has a low coefficient of friction. Most preferably, centering member 14 is formed from an acetal material, which has a high oil content, with a very low coefficient of friction and, consequently, exhibits very little wear. In operation, after handle grip 12 is released and when spring 53 is partially compressed but in its most uncompressed position (FIGS. 4-7), spring 53 presses on base 36 of centering member 14 urging camming surfaces 40 and 43 to slide along camming surfaces 42 and 46, respectively, until the distal point of each tooth is positioned in the closed end of each notch. On the other hand, when a rotational torque is applied to handle grip 12 which produces a force sufficient to overcome the compression force of the spring 53 and the friction between the camming surfaces 40, 42, 43 and 46, in either a clockwise or counterclockwise direction, shaft 18 rotates likewise causing centering member 14 to rotate therewith and slide along camming surfaces 42 and 46 away from the centering collar and positioning collar. This camming action causes centering member 14 to move axially along shaft 18 and compress spring 53. When handle grip 12 is released, spring 53 expands pushing centering member 14 down shaft 18. As the centering member 14 slides down the shaft 18, again, camming surfaces 40 and 43 slide along camming surfaces 42 and 46, which imparts rotation to the shaft 18 and, in turn, imparts rotation to handle grip 12. When distal points 40a and 43a of the teeth 41 and 44 are aligned in the closed ends 42a and 46a of the notches 42 and 46, handle grip 12 is fully aligned with mounting base 13. Furthermore, projections 50 and 51 abut shoulders 18d and 18c. 
     To assure that the camming surfaces 40 and 43 do not completely disengage from each other, stop 28 is positioned such that the camming surfaces 40 and 43 will remain in a cooperative relationship. This cooperative relationship is best maintained if the camming surfaces 40 and 43 overlap, for example, over a minimum region of about 1/8 inch. It should be understood that the size of the over lap depends on the materials used and on the stiffness of the spring--the greater the stiffness of the spring the larger the area of overlap. Similarly, the lower the compressive and shear strength of the centering member material the smaller the required overlap. 
     Coil spring 53, as can be understood by those having ordinary skill in the art, is easily installed; it is slipped and telescoped over shaft 18 with one end of the spring extending into spring cavity 38 and the other end supported along the shaft's longitudinal axis 19 by a retaining clip 54. Retaining clip 54, preferably formed from spring steel coated with a corrosion protective material, such as zinc, slides into a groove 55 formed in shaft 18. Groove 55 provides retaining clip 54 with a shoulder so that the position of clip 54 along the longitudinal axis 19 of shaft 18 is fixed. Spring 53 is slightly compressed between spring cavity 38 and the abutment surface provided by retaining clip 54 so that centering member 14 is biased into a fully seated position where handle grip 12 and mounting base 13 are centered and aligned. 
     While the form of the invention has been described in the context of a vehicle door handle, it should be understood that handle assembly 10 can be used in numerous applications, such as furniture, appliances, and architectural components. 
     Furthermore while one form of the invention has been shown and described, other forms will now be apparent to those skilled in the art. For instance, the projections may be formed on the mounting base collar and the handle grip positioning collar for extending into notches/recesses formed in the centering member. The embodiment of the invention shown in the drawings is not intended to limit the scope of the invention which is defined by the claims which follow.