Abstract:
A motor vehicle disc brake assembly comprises a caliper having a cavity, a brake disc rotatable relative to the caliper, a brake lining mounted to the caliper, a piston mounted in the cavity for displacing the brake lining against the brake disc, and an electromechanical actuator for supporting the piston. The electromechanical actuator has a drive assembly operably connected to a spindle, a rotationally restrained spindle nut threaded on the spindle, and an anti-rattle clip coupling together the piston and spindle nut. Rotation of the spindle by the drive assembly moves the spindle nut to support the piston.

Description:
BACKGROUND OF INVENTION 
       [0001]    This invention relates in general to vehicle disc brake assemblies and in particular to an improved structure for an electric parking brake actuator for use in such a disc brake assembly. 
         [0002]    Most vehicles are equipped with a brake system for slowing or stopping movement of the vehicle in a controlled manner. A typical brake system for an automobile or light truck includes a disc brake assembly for each of the front wheels and either a drum brake assembly or a disc brake assembly for each of the rear wheels. The brake assemblies are actuated by hydraulic or pneumatic pressure generated when an operator of the vehicle depresses a brake pedal. The structures of these drum brake assemblies and disc brake assemblies, as well as the actuators therefore, are well known in the art. 
         [0003]    A typical disc brake assembly includes a brake rotor which is secured to a wheel of the vehicle for rotation therewith. The disc brake assembly further includes a caliper assembly that is slidably supported on pins secured to an anchor bracket. The anchor bracket is secured to a non-rotatable component of the vehicle, such as the axle flange or steering knuckle, which is connected to the vehicle frame. The caliper assembly includes a pair of brake pads which are disposed on opposite sides of the brake rotor. The brake pads are connected to one or more hydraulically or pneumatically actuated pistons for movement between a non-braking position and a braking position, wherein they are moved into frictional engagement with the opposed braking surfaces of the brake rotor. For example, when an operator of the vehicle depresses the brake pedal, the piston urges the brake pads from the non-braking position to the braking position so as to frictionally engage the opposed braking surfaces of the brake rotor and thereby slow or stop rotation of the associated wheel of the vehicle. 
         [0004]    The disc brake assembly may also include an electromechanical actuating device that is used to realize a parking brake function of the disc brake assembly. The electromechanical actuating device may comprise a rotationally restrained nut threaded onto a motor driven spindle. As the spindle is rotationally driven, the nut axially translates to move the piston and urge the brake pads between the braking and non-braking positions. The piston may be hollow with the nut and spindle located inside the piston. However, the electromechanical actuating device may produce an undesirable noise or rattle from the nut contacting and/or moving the piston. Therefore, it would be desirable to reduce or minimize any noise or rattle in the electromechanical actuating device for the disc brake assembly. 
       SUMMARY OF INVENTION 
       [0005]    This invention relates to an anti-rattle clip for use in a disc brake assembly and a disc brake assembly including such an anti-rattle clip. 
         [0006]    According to one embodiment, a disc brake assembly for a motor vehicle may comprise, individually and/or in combination, one or more of the following features: a caliper having a cavity, a brake lining mounted to the caliper, a piston mounted in the cavity for displacing the brake lining, and an electromechanical actuator for supporting the piston. The electromechanical actuator has a drive assembly configured to be operatively connected to a spindle, a spindle nut configured to be operatively coupled to the spindle, and an anti-rattle clip configured to couple together the piston and spindle nut. Rotation of the spindle by the drive assembly axially moves the spindle nut to engage and move the piston. 
         [0007]    According to another embodiment, an electromechanical actuator for a disc brake assembly may comprise, individually and/or in combination, one or more of the following features: a spindle, a spindle nut, and an anti-rattle clip. The spindle nut is configured to be operatively coupled to the spindle. The anti-rattle clip is fixed to the spindle nut. 
         [0008]    According to another embodiment, an anti-rattle clip for a motor vehicle disc brake assembly may comprise, individually and/or in combination, one or more of the following features: a curved central portion, a first web portion, and a first flange. The curved central portion is configured to couple to a spindle nut of an electromechanical actuator. The first web portion extends from the curved central portion. The first flange extends perpendicularly from the first web portion and is configured to exert a load against a piston of the disc brake assembly. 
         [0009]    A potential advantage of an embodiment of the anti-rattle clip is reduced rattle in the electromechanical actuating device for the disc brake assembly. 
         [0010]    Other advantages of this invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiments, when read in light of the accompanying drawings. 
     
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         [0011]      FIG. 1  is a partial sectional view of a prior art electromechanical actuator for a disc brake assembly. 
           [0012]      FIG. 2  is a sectional perspective view of an electromechanical actuator for a disc brake assembly using a first embodiment of an anti-rattle clip in accordance with the present invention. 
           [0013]      FIG. 3  is a sectional view taken along line  3 - 3  of  FIG. 2 . 
           [0014]      FIG. 4  is a sectional view taken along line  4 - 4  of  FIG. 3 . 
           [0015]      FIG. 5  is a perspective view of a second embodiment of an anti-rattle clip in accordance with the present invention. 
           [0016]      FIG. 6  is a sectional perspective view of an electromechanical actuator for a disc brake assembly using the second embodiment of the anti-rattle clip illustrated in  FIG. 5 . 
           [0017]      FIG. 7  is a sectional view of an electromechanical actuator for a disc brake assembly using the second embodiment of the anti-rattle clip illustrated in  FIG. 5   
           [0018]      FIG. 8  is a perspective view of a third embodiment of an anti-rattle clip in accordance with the present invention. 
           [0019]      FIG. 9  is a sectional perspective view of an electromechanical actuator for a disc brake assembly using the third embodiment of the anti-rattle clip illustrated in  FIG. 8 . 
           [0020]      FIG. 10  is a sectional view of an electromechanical actuator for a disc brake assembly using the third embodiment of the anti-rattle clip illustrated in  FIG. 8 . 
           [0021]      FIG. 11  is a perspective view of a fourth embodiment of an anti-rattle clip in accordance with the present invention. 
           [0022]      FIG. 12  is a sectional view of an electromechanical actuator for a disc brake assembly using a fifth embodiment of an anti-rattle clip in accordance with the present invention. 
           [0023]      FIG. 13  is a perspective view of a sixth embodiment of an anti-rattle clip in accordance with the present invention. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0024]    Referring now to  FIG. 1 , there is illustrated a portion of a prior art disc brake assembly, indicated generally at  10 . The disc brake assembly  10  is well known to those skilled in the art and may be, for example, such as is disclosed by U.S. Pat. No. 8,844,683 to Sternal et al, the disclosure of which is hereby incorporated by reference in entirety herein Although this invention will be described and illustrated in connection with the particular prior art disc brake assembly  10  disclosed herein, it will be appreciated that this invention may be used in connection with other types or kinds of disc brake assemblies, if so desired. 
         [0025]    The prior art disc brake assembly  10  includes a brake caliper  12 , which is mounted in a floating manner by means of a brake carrier (not illustrated) in a manner known to those skilled in the art, and which spans a brake disc  14  that is coupled to a vehicle wheel (not illustrated) in a rotationally fixed manner. Provided in the brake caliper  12  is a brake lining assembly, which has an outboard brake lining  16  that bears on the brake caliper  12 , and an inboard brake lining  18  that bears on an actuating piston  22 . The outboard and inboard brake linings  16  and  18 , respectively, face towards each other and, in a release position illustrated in  FIG. 1 , are disposed with a small air clearance on both sides of the brake disc  14 , such that no significant residual drag moments occur. A brake lining carrier  20  is disposed between the inboard brake lining  18  and the piston  22  for the inboard brake lining  18  and actuating piston  22  to move jointly. The piston  22  is mounted in a movable manner in a cylindrical cavity  24  in the brake caliper  12 . 
         [0026]    In addition, it can be seen in  FIG. 1  that the piston  22  is realized so as to be hollow. Accommodated in the piston  22  is a rotationally restrained spindle nut or thrust piece, indicated generally at  32 , of an electromechanical actuator, indicated generally at  34 . The actuator  34  includes a drive assembly  36  having an electric motor and transmission assembly. An output shaft  38  of the drive assembly  36  drives a drive spindle  42 , which is supported via an axial bearing  40  and which is accommodated in a threaded manner in a threaded receiver  44  of the spindle nut  32 . 
         [0027]    The spindle nut  32  has a conical portion  46 , which can be brought into bearing contact with a complementarily conical inner surface  48  of the piston  22 . In the release position shown in  FIG. 1 , there is a clearance S 1  between the conical portion  46  and conical inner surface  48 . 
         [0028]    If service braking is desired for a vehicle having the disc brake assembly  10 , the disc brake assembly  10  is hydraulically actuated. For example, the disc brake assembly may be hydraulically actuated by a driver via a brake pedal or via a drive assistance system. When the disc brake assembly  10  is hydraulically actuated, hydraulic fluid is pressurized (by a suitable means known to those skilled in the art) in the cavity  24  such that the piston  22  is displaced leftward along a longitudinal axis A. As a consequence, and as is known to those skilled in the art, the inboard brake lining  18  is pressed onto the brake disc  14  by means of the brake caliper  12  and, at the same time, a corresponding displacement of the brake caliper  12  on an opposite side of the brake disc  14  causes the outboard brake lining  16  to be drawn against the opposite side of the brake disc  14 . 
         [0029]    As a result of the application of the pressurized hydraulic fluid to the cavity  24 , the piston  22  is displaced leftward in  FIG. 1 , along the longitudinal axis A towards the brake disc  14 . The spindle nut  32  remains unactuated, and therefore remains at an initial axial position illustrated in  FIG. 1 . 
         [0030]    For activating the parking brake, in a manner similar to service braking, the piston  22  is first put into an active braking position through application of hydraulic pressure. Actuation of the actuator  34  then causes the spindle nut  32  to be displaced towards the brake disc  14 , until the clearance S 1  has been used up and the conical portion  46  bears on the corresponding conical inner surface  48  inside the piston  22 . As a result, the piston  22  is axially supported, via the spindle nut  32  and the axial bearing  40 , on the housing of the brake caliper  12  in a parking brake state. 
         [0031]    Once the piston  22  is axially supported, the hydraulic pressure in the cavity  24  can be removed. The parking brake state is maintained because of the position of the spindle nut  32  and because of self-arresting (for example, by a self-arresting transmission between the spindle  42  and the receiver  44 ). The outboard and inboard brake linings  16  and  18 , respectively, pressing against the brake disc  14  are supported via the spindle nut  32 . 
         [0032]    If the parking brake state is to be released, then pressurized hydraulic fluid is again introduced into the cavity  24 . As a result, the piston  22  is displaced slightly leftward, in the axial direction A, towards the brake disc  14  such that the spindle nut  32  is relieved of axial load. Through control of the actuator  34 , the spindle nut  32  can be displaced back into the initial position as illustrated in  FIG. 1 . 
         [0033]    Referring now to  FIGS. 2-4 , there is illustrated a first embodiment of an anti-rattle clip, indicated generally at  160 , produced in accordance with the present invention and for use with a disc brake assembly, indicated generally at  110  in  FIGS. 2 and 3 . The general structure and operation of the disc brake assembly  110  is well known in the prior art. For example, the disc brake assembly  110  may be similar to the prior art disc brake assembly  10  illustrated and discussed above in connection with  FIG. 1 . Alternatively, the particular anti-rattle clip  160  of the present invention, and the alternate embodiments thereof, may be used in connected with other types or kinds of disc brake assemblies, if so desired. 
         [0034]    The disc brake assembly  110  includes a brake caliper  112 , which is mounted in a floating manner by means of a brake carrier (not illustrated) in a manner known to those skilled in the art, and which spans a brake disc  114  that is coupled to a vehicle wheel (not illustrated) in a rotationally fixed manner. Provided in the brake caliper  112  is a brake lining assembly, which has an outboard brake lining  116  that bears on the brake caliper  112 , and an inboard brake lining  118  that bears on an actuating piston  122 . The outboard and inboard brake linings  116  and  118 , respectively, face towards each other and, in a release position shown in  FIG. 3 , are disposed with a small air clearance on both sides of the brake disc  114 , such that no significant residual drag moments occur. A brake lining carrier  120  is disposed between the inboard brake lining  118  and the piston  122  for the inboard brake lining  118  and piston  122  to move jointly. The piston  122  is mounted in a movable manner in a preferably cylindrical cavity  124  in the brake caliper  112 . 
         [0035]    In addition, it can be seen that the piston  122  is realized so as to be hollow. Accommodated in the piston  122  is a rotationally restrained spindle nut, indicated generally at  132 , of an electromechanical actuator, indicated generally at  134 . The actuator  134  preferably includes a drive assembly  136  having a suitable electric motor and transmission assembly known to those skilled in the art. An output shaft  138  of the drive assembly  136  drives a drive spindle  142 , which is supported via an axial bearing  140  and which is accommodated in a threaded manner in a threaded receiver  144  of the spindle nut  132 . An external surface  150  of the spindle nut  132  is preferably cylindrical. 
         [0036]    The spindle nut  132  has a conical portion  146 , which can be brought into bearing contact with a complementarily conical inner surface  148  of the piston  122 . In the release position, there is a clearance S 1  between the conical portion  146  and conical inner surface  148 . The construction, shape, configuration, and/or make-up of the conical portion  146  and complementary inner surface  148  may be other than illustrated and described, if so desired. For example, the conical portion  146  and inner surface  148  may have other, non-conical complimentary shapes. 
         [0037]    If service braking is desired for a vehicle having the disc brake assembly  110 , the disc brake assembly  110  is hydraulically actuated. For example, the disc brake assembly may be hydraulically actuated by a driver via a brake pedal or via a drive assistance system. When the disc brake assembly  110  is hydraulically actuated, hydraulic fluid is pressurized (by a suitable means known to those skilled in the art) in the cavity  124  such that the piston  122  is displaced leftward along a longitudinal axis A. As a consequence, and as is known to those skilled in the art, the inboard brake lining  118  is pressed onto the brake disc  114  by means of the brake caliper  112  and, at the same time, a corresponding displacement of the brake caliper  112  on an opposite side of the brake disc  114  causes the outboard brake lining  116  to be drawn against the opposite side of the brake disc  114 . 
         [0038]    As a result of the application of the pressurized hydraulic fluid to the cavity  124 , the piston  122  is displaced leftward in  FIG. 3 , along the longitudinal axis A towards the brake disc  114  and into an active braking position. The spindle nut  132  remains unactuated, and therefore remains at an initial axial position illustrated in  FIG. 3 . 
         [0039]    For activating the parking brake, in a manner similar to service braking, the piston  122  is first put into the active braking position through application of hydraulic pressure. Actuation of the actuator  134  then causes the spindle nut  132  to be displaced towards the brake disc  114 , until the clearance S 1  has been used up and the conical portion  146  bears on the corresponding conical inner surface  148  inside the piston  122 . As a result, the piston  122  is axially supported, via the spindle nut  132  and the axial bearing  140 , on the housing of the brake caliper  112  in a parking brake state. 
         [0040]    Once the piston  122  is axially supported, the hydraulic pressure in the cavity  124  can be removed. The parking brake state is maintained because of the position of the spindle nut  132  and because of self-arresting (for example, by a self-arresting transmission between the spindle  142  and the receiver  144 ). The outboard and inboard brake linings  116  and  118 , respectively, pressing against the brake disc  114  are supported via the spindle nut  132 . 
         [0041]    If the parking brake state is to be released, pressurized hydraulic fluid is again introduced into the cavity  124 . As a result, the piston  122  is displaced slightly leftward, in the axial direction A, towards the brake disc  114  such that the spindle nut  132  is relieved of axial load. Through control of the actuator  134 , the spindle nut  132  can be displaced back into the initial axial position illustrated in  FIG. 3 . 
         [0042]    As best shown in  FIG. 4 , the actuator  134  includes the first embodiment of the anti-rattle clip  160 . In the illustrated embodiment, the anti-rattle clip  160  includes a curved central portion  162 , first and second web or leg portions  164  and  166 , respectively, and first and second “end” flanges  168  and  170 , respectively. In the illustrated embodiment, the central portion  162  is preferably an arc of preferably around 180 degrees and the first and second web portions  164  and  166  extend from the central portion  162  in opposing directions towards an internal surface  172  of the piston  122 . The first flange  168  extends generally perpendicular from the first web portion  164  at the internal surface  172 . The second flange  170  extends generally perpendicular from the second web portion  166  at the internal surface  172 . As illustrated, the first and second flanges  168  and  170 , respectively, extend in opposing directions. The first and second flanges  168  and  170 , respectively, may each be planar or may be curved to fit the internal surface  172 . Alternatively, the construction, shape, configuration, and/or make-up of the anti-rattle clip  160  may be other than illustrated and described, if so desired. For example, the first and second flanges  168  and  170 , respectively, may extend in other than opposing directions or be omitted. Also, the clip  160  may include only the central portion  162  and only one of the first and second web portions  164  and  166 , respectively, and its associated first or second flange  168  or  170 , respectively. 
         [0043]    In the illustrated embodiment, the anti-rattle clip  160  couples the piston  122  and the spindle nut  132  by exerting a tuned load on the piston  122  and spindle nut  132 . As will be discussed below, the anti-rattle clip  160  preferably exerts the tuned load on both the external surface  150 , via the central portion  162 , and on the internal surface  172 , via the first and second flanges  168  and  170 , respectively. The first and second flanges  168  and  170 , respectively, exert the tuned load against the internal surface  172  but are not fixed to the internal surface  172 . As such, the anti-rattle clip  160  moves with the spindle nut  132  as the spindle nut  132  is displaced and the first and second flanges  168  and  170 , respectively, are free to move along the internal surface  172 . 
         [0044]    The central portion  162  is fixed to the external surface  150  such that the anti-rattle clip  160  moves with the spindle nut  132 . In the illustrated embodiment, the central portion  162  is preferably welded to the spindle nut  132 . Alternatively, the central portion  162  may be otherwise fixed to the external surface  150 . For example, the central portion  162  may be fixed to the external surface  150  by an interference fit. 
         [0045]    The first and second flanges  168  and  170 , respectively, exert a spring load against the internal surface  172 . In the illustrated embodiment, the spring load is produced by the first flange  168  being bent generally perpendicular from the first web portion  164  and the second flange  170  being bent generally perpendicular from the second web portion  166 . The anti-rattle clip  160  is produced from a resilient material such that the first flange  168  desires to return in line with the first web portion  164  and the second flange  170  desires to return in line with the second web portion  166 . 
         [0046]    The first and second flanges  168  and  170 , respectively, desiring to return in line with the first and second web portions  164  and  166 , respectively, produces the spring load against both the internal surface  172  and the external surface  150 . The spring load may be adjusted to produce the tuned load. The tuned load may be adjusted to compensate for specific vibration frequencies of the piston  122 , spindle nut  132 , and/or the disc brake assembly  110 . 
         [0047]    Alternatively the anti-rattle clip  160  may be fixed to the internal surface  172  such that the anti-rattle clip  160  moves with the piston  122 . For example, the first and second flanges  168  and  170 , respectively, may be welded to the internal surface  172 . The central portion  162  may then be fitted to the external surface  150  by an interference fit that permits the spindle nut  132  to move relative to the anti-rattle clip  160 . When the anti-rattle clip  160  is fixed to the internal surface  172  such that the anti-rattle clip  160  moves with the piston  122 , the first flange  168  being bent generally perpendicular from the first web portion  164  and the second flange  170  being bent generally perpendicular from the second web portion  166  still produces the spring load which in turn produces the tuned load. 
         [0048]    The anti-rattle clip  160  is produced from a resilient material. For example, the anti-rattle clip  160  may be produced from a metal strip using a bending operation. Alternatively, the anti-rattle clip  160  may be produced from other suitable materials, such as plastic, using a molding or casting operation. The anti-rattle clip  160  may be produced with a plurality of openings  174 . 
         [0049]    As illustrated, the anti-rattle clip  160  and the actuator  134  are part of the disc brake assembly  110  having an electric parking brake system. Alternatively, as one skilled in the art will readily understand, the anti-rattle clip  160  and the actuator  134  may be part of other types of brake assemblies. For example, the anti-rattle clip  160  and the actuator  134  may be incorporated into a drum-in-hat disc brake assembly having a parking brake, such as is disclosed by U.S. Pat. No. 8,011,482 to Boyle et al, the disclosure of which is hereby incorporated by reference in entirety herein. 
         [0050]    Referring now to  FIGS. 5-7  there is illustrated a second embodiment of an anti-rattle clip, indicated generally at  260 , produced in accordance with the present invention and for use with a disc brake assembly  210 . Because the anti-rattle clip  260  is a variation of the anti-rattle clip  160  of  FIGS. 2-4 , like reference numerals, increased by 100, designate corresponding parts in the drawings and detailed description thereof will be omitted. 
         [0051]    The anti-rattle clip  260  includes a curved central portion  262 , first and second bends  276  and  278 , respectively, first and second webs  264  and  266 , respectively, and first and second flanges  268  and  270 , respectively. The central portion  262  is preferably an arc of preferably greater than 180 degrees. The first bend  276  connects the central portion  262  to the first web  264  such that the first web  264  aligns with a vertical axis  280 . For example, the vertical axis  280  may radially extend through a spindle nut  232 . As illustrated, the vertical axis  280  passes through a center point  280 A of the spindle nut  232 . The second bend  278  connects the central portion  262  to the second web  266  such that the second web  266  aligns with the vertical axis  280 . 
         [0052]    Referring now to  FIGS. 8-10  there is illustrated a third embodiment of an anti-rattle clip, indicated generally at  360 , produced in accordance with the present invention and for use with a disc brake assembly  310 . Because the anti-rattle clip  360  is a variation of the anti-rattle clip  260  of  FIGS. 5-7 , like reference numerals, increased by 100, designate corresponding parts in the drawings and detailed description thereof will be omitted. 
         [0053]    The anti-rattle clip  360  includes a first flange  368 A, second flange  368 B, third flange  370 A, and fourth flange  370 B. The first and second flanges  368 A and  368 B, respectively, extend from a first web portion  364  and the third and fourth flanges  370 A and  370 B, respectively, extend from a second web portion  366 . As illustrated, the first and second flanges  368 A and  368 B, respectively, are in opposing directions and the third and fourth flanges  370 A and  370 B, respectively, are in opposing directions. The construction, shape, configuration, and/or make-up of the anti-rattle clip  360  may be other than illustrated and described, if so desired. For example, the first and second flanges  368 A and  368 B, respectively, and the third and fourth flanges  370 A and  370 B, respectively, may be in other than opposing directions. For example, the first and second flanges  368 A and  368 B, respectively, or the third and fourth flanges  370 A and  370 B, respectively, may be in a common direction. 
         [0054]    Referring now to  FIG. 11  there is illustrated a fourth embodiment of an anti-rattle clip, indicated generally at  460 , produced in accordance with the present invention and for use with a disc brake assembly. Because the anti-rattle clip  460  is a variation of the anti-rattle clip  160  of  FIGS. 2-4 , like reference numerals, increased by 300, designate corresponding parts in the drawings and detailed description thereof will be omitted. 
         [0055]    The anti-rattle clip  460  is fabricated from an elongated, resilient material. For example, the anti-rattle clip  460  may be produced from a metal wire using a bending operation. 
         [0056]    As illustrated, the anti-rattle clip  460  has a shape of the anti-rattle clip  160  illustrated in the first embodiment. Alternatively, the anti-rattle clip  460  may have the shape of the anti-rattle clips  260  or  360  of the second or third embodiments, respectively. 
         [0057]    Referring now to  FIG. 12  there is illustrated a fifth embodiment of an anti-rattle clip, indicated generally at  560 , produced in accordance with the present invention and for use with a disc brake assembly  510 . Because the anti-rattle clip  560  is a variation of the anti-rattle clip  160  of  FIGS. 2-4 , like reference numerals, increased by 400, designate corresponding parts in the drawings and detailed description thereof will be omitted. 
         [0058]    An internal surface  572  of an actuating piston  522  has a radial slot  582 . The radial slot  582  extends substantially parallel to the spindle nut  532  and for a length that is at least as long as the spindle nut  532  is displaceable. A second web portion  566  of the anti-rattle clip  560  is seated in the slot  582 . The construction, shape, configuration, and/or make-up of the anti-rattle clip  560  may be other than illustrated and described, if so desired. For example, a first web portion  564  may also be seated in a second slot. 
         [0059]    Furthermore, as illustrated, the anti-rattle clip  560  has a shape of the anti-rattle clip  160  illustrated in the first embodiment. Alternatively, the anti-rattle clip  560  may have the shape of the anti-rattle clip  260  of the second embodiment, the anti-rattle clip  360  of the third embodiment, or the anti-rattle clip  460  of the fourth embodiment. 
         [0060]    Referring now to  FIG. 13  there is illustrated a sixth embodiment of an anti-rattle clip, indicated generally at  660 , produced in accordance with the present invention and for use with a disc brake assembly. Because the anti-rattle clip  660  is a variation of the anti-rattle clip  160  of  FIGS. 2-4 , like reference numerals, increased by 500, designate corresponding parts in the drawings and detailed description thereof will be omitted. 
         [0061]    The anti-rattle clip  660  has a looped central portion  662 . The looped central portion  662  secures the anti-rattle clip  660  to an external surface of a spindle nut—e.g., the external surface  150  of the spindle nut  132 . The anti-rattle clip  660  is fabricated from an elongated, resilient material. For example, the anti-rattle clip  660  may be produced from a metal wire using a bending operation. The looped central portion  662  is sized smaller than a diameter of the spindle nut. 
         [0062]    To install the anti-rattle clip  660  on the spindle nut, first and second web portions  664  and  666 , respectively, are pushed towards the looped central portion  662  to expand a diameter of the looped central portion  662  to greater than the diameter of the spindle nut. The expanded looped central portion  662  is slid onto the spindle nut and the first and second web portions  664  and  666 , respectively, are released. The expanded looped central portion  662  then contracts and secures the anti-rattle clip  660  to the spindle nut. 
         [0063]    In accordance with the provisions of the patent statutes, the principle and mode of operation of this invention have been described and illustrated in its preferred embodiments. However, it must be understood that this invention may be practiced otherwise than as specifically explained and illustrated without departing from its spirit or scope.