Patent Publication Number: US-9415285-B1

Title: Breakaway basketball rim assembly

Description:
FIELD OF THE INVENTION 
     The present disclosure relates to basketball goals, more specifically a basketball rim which is capable of deflecting in one or more directions upon application of sufficient force, such as from, but is not limited to, a dunk shot, to prevent damage to the rim and associated backboard to which the rim is mounted. In particular, it relates to such a rim that may automatically return to an original position upon removal of the force. 
     BACKGROUND 
     Breakaway basketball rim assemblies typically include a spring energy basketball goal/backboard unit incorporated into a conventional vertically aligned backboard and horizontally aligned goal, i.e., the rim. The rim can be spring mounted to pivot relative to the backboard forwardly and downwardly out of its normal horizontal plane when a predetermined excess force is applied such as when a player dunks the basketball and slaps, hits or pulls the rim with his hands, wrists, or arms. The rim may then return to its original position with the spring energy of the return motion being dissipated by the spring portion. Provision can also be made for the rim to deflect sideward. The spring portion providing the return forces may be mounted in front of the backboard and connected to the rim. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       In the drawings, like reference characters generally referred to the same parts throughout the different views. Also, the drawings are not necessarily to scale, emphasis instead generally being placed upon illustrating the principals of the invention. 
         FIG. 1  is a perspective view of a basketball rim assembly mounted to a backboard in a rest position. 
         FIG. 2  is a top view of the basketball rim assembly of  FIG. 1 . 
         FIG. 3  is a side view of the basketball rim assembly of  FIG. 1  in a rest position. 
         FIG. 4  is a cross-sectional view taken along line  4 - 4  of  FIG. 2 , or the midplane of the rim assembly. 
         FIG. 5  is an enlarged cross-sectional view as indicated in  FIG. 4  taken along line  4 - 4 . 
         FIG. 6  is a cross-sectional view with the basketball rim assembly being deflected downward away from a rest position into a displaced position. 
         FIG. 7  is a cross-sectional view taken along line  7 - 7  of  FIG. 3  of the basketball rim assembly in a rest position. 
         FIG. 8  is a rear view of the basketball rim assembly in a rest position. 
         FIG. 9  is a cross-sectional view taken along line  9 - 9  of  FIG. 7  of the basketball rim assembly with the cam surface removed. 
         FIG. 10  is an exploded view of the basketball rim assembly of  FIG. 1 . 
         FIG. 11  is a perspective view of the rolling cam and biasing member removed from the longitudinal carrier illustrating a first overall length of the shaft. 
         FIG. 12  is a perspective view of the rolling cam illustrating a second overall length of the shaft, with the biasing element removed. 
         FIG. 13  is a perspective view of the longitudinal carrier of the basketball rim assembly. 
         FIG. 14  is a perspective view of the longitudinal carrier of  FIG. 13  with a through opening receiving the rolling cam of  FIG. 11 . 
         FIG. 15  is a perspective view of the mounting frame of the basketball rim assembly of  FIG. 1 . 
         FIG. 16  is an enlarged cross-sectional view taken along line  16 - 16  of  FIG. 15  illustrating a first position of a wedge relative to the mounting plate, or more specifically the inclined surface of the mounting plate, with a mounting bolt removed. 
         FIG. 17  is an enlarged cross-sectional view taken along line  16 - 16  of  FIG. 15  illustrating a second position of a wedge relative to the mounting plate, or more specifically the inclined surface of the mounting plate, with a mounting bolt removed. 
         FIG. 18  is an enlarged cross-sectional view taken along line  18 - 18  of  FIG. 7  illustrating the clearance between pin and cylinder in a first position with the rim in a horizontal position of  FIG. 1 . 
         FIG. 19  is an enlarged cross-sectional view taken along line  18 - 18  of  FIG. 7  illustrating the pin in a different or second position within the clearance between the pin and the cylinder with the rim in a deflected or non-horizontal position, and further illustrating the cylinder is in substantially the same position against the cam surface of the mounting plate of  FIG. 18 . 
     
    
    
     DETAILED DESCRIPTION OF EMBODIMENTS WITH THE DRAWINGS 
     Where like reference numerals are used throughout the figures to designate like component, the figures depict a basketball rim assembly  20 . In  FIG. 1 , the basketball rim assembly or apparatus  20  may be mounted to a vertical backboard  10  so that a rim  24  of the assembly  20  is in the conventional horizontal position. A net, not shown, can be suspended from the rim  24  in the typical manner. The rim  24  can be fixed to a top plate  26 , which may extend from a back segment  25  of the rim to the front surface  18  of the backboard  10 . Opposing side plates  21  can be fixed to the top plate  26  to extend downward over, and outside of, bracket plates  32  of a mounting frame  30 , which can be fixed to the backboard  10 . An arcuate reinforcement  22  can be provided depending from the rim  24  to ensure that the rim has the desired stability with respect to the top plate  26  and side plates  21 . One or more, or portions thereof, of rim  24 , longitudinal carrier  50 , rolling cam  40 , and/or biasing element  49  can be joined together to form a unitized structure that can move or pivot as a movable portion  20   a  in relation to the backboard  10 , mounting frame  30 , and/or other structure, described below, that is fixed to the backboard  10 . 
       FIGS. 2-5, 10 and 15  illustrate the mounting frame  30  that may have bracket plates  32  that can be fixed to each other by a mounting plate  38  and a base plate  31 . The mounting plate  38  can be fixed to the backboard  10  by suitable fasteners, not shown, that extend in one or more through openings  33  formed in the mounting plate  38 . For example, the fasteners may be, but are not limited to, bolts. The mounting plate  38  can have a forward extending portion  34  along the top portion thereof that extends away from a general planar portion  36  to which the bracket plates  32  can be fixed. The forward extending portion  34  can be angled away from the planar portion  36  by an angle A in the range of about 10-30 degrees, and preferably about 20 degrees. A cam surface  39  can be formed or as shown in one embodiment attached to the mounting plate  38 . The cam surface  39  may include an angled surface, relative to the horizontal, configured to guide a rolling cam  40 . 
     As shown in  FIGS. 4-12 and 14 , a rolling cam  40  operably engages the cam surface  39  of the mounting plate  38 . The rolling cam  40  is tensioned in one embodiment by a spring and screw to apply the force or pressure desired to have the rim  24  urge back to the rest or horizontal position. The rolling cam  40  pivots with the rim  24 . 
     The rolling cam  40  is slideable within a tubular body  52  of a longitudinal carrier  50 , such that the rolling cam  40  and the force it applies to the cam surface  39  is perpendicular to the pivot axis P in a direction along its longitudinal axis Lr. The force intersects the pivot axis P in the embodiment shown. The rolling cam  40  and/or the biasing element  49  slides or is in a sliding engagement with the carrier  50  at least during the movement of the rim  24  from the rest position ( FIG. 3 ) to the displaced position ( FIG. 6 ) and pivots about the pivot axis P. The rolling cam  40  slides within the through opening  58  of the longitudinal carrier body  52  along the longitudinal axis Lc of the carrier  50 . Therefore the longitudinal axis Lr of the rolling cam  40  is coaxially aligned with the longitudinal axis Lc of the carrier  50  when assembled. The rolling cam  40  translates along the midplane M of the rim assembly  20 . The rolling cam  40  is in a rolling engagement with the cam surface  39  of the mounting plate  38 . The rolling engagement allows the cylinder  70  to have a rolling contact of its circumferential surface with the cam surface  39  when the carrier  50  with rolling cam  40  pivots between the rest position and the displaced position. As opposed to an object that is pushed on its exterior surface to slide across a surface, the rolling engagement between the rolling cam  40  and the rotating cylinder  70  may, but is not limited to, reduce friction and may reduce the amount of lubricant that may be used and/or reduce the frequency lubricant is applied. 
     As shown in  FIGS. 11 and 12 , the rolling cam  40  includes an elongated shaft  60  having a first or proximal end  60   a  and second or distal end  60   b . Shaft  60  is slidably positioned within the through opening  58  of the carrier  50 . The proximal end  60   a  of the shaft  60  engages a biasing element  49 , one embodiment of the biasing element  49  is a tension spring as shown. The biasing element  49  is adjustable to either increase or decrease the pressure or tension applied between the cylinder  70  and the cam surface  39 . The distal end  60   b  includes the cylinder or first cylinder member  70  rotating relative to the shaft  60  about a rotational axis R that may be substantially perpendicular to the longitudinal axis Lr of the shaft  60 . Also, a longitudinal axis of the cylinder  70  may be described as perpendicular to the longitudinal axis Lr of the shaft  60 . One embodiment shown includes the cylinder  70  rotating about a second cylinder or second cylinder member  80 . The second cylinder  80  embodiment shown is a pin. The pin  80  interconnects the cylinder  70  to the shaft  60 . The pin  80  may be received by the distal end  60   b  of the shaft  60  by a yoke. The yoke may include a first side  60   ba  and opposing second side  60   bb  adjacent the longitudinal ends of the cylinder  70  and pin  80 . A respective through opening  61  of each one of the first and second sides  60   ba ,  60   bb  receives the opposing ends of the pin  80 . The first and second sides  60   ba ,  60   bb  define a receiving slot  62  for the cylinder  70  such that the cylinder  70  extends past the distal end  50   b  of the carrier  50  to make rolling contact with the cam surface  39 . One or more of the longitudinal ends or a portion of the cylindrical pin  80  may also include a first and second flat sides  81 ,  82 . The longitudinal end with first and second flat sides  81 ,  82  extends outwardly beyond the outer diameter of the shaft  60  to extend into a longitudinal slot  53  of the carrier  50 . The first and second flat sides  81 ,  82  are parallel to the longitudinal axis Lr of the shaft  60 . The opposing first and second flat sides  81 ,  82  are slideably engaged to the longitudinal slot  53  of the distal end  50   b  of the carrier  50  to not allow rotation of the rolling cam  40  relative to the carrier  50  about the longitudinal axis Lc while still allowing sliding of the rolling cam  40  in the longitudinal direction along the longitudinal axis Lc. Further shown in the embodiments, the pin  80  may not rotate within the through openings  61  because of being rotationally held by the carrier  50 . 
     As illustrated in  FIGS. 4-6 , the rolling cam  40  is longitudinal biased within the through opening  58  of the carrier  50 . The biasing element  49  in the through opening  58  adjacent the proximal end  50   a  of the carrier  50  pivots with the carrier  50  between the rest position and displaced position. The biasing element  49  extends between the arcuate reinforcement  22  of the rim assembly  20  and the proximal end  60   a  of the shaft  60 . The biasing force increases from the rest position to the displaced position since the cam surface  39  of the mounting plate  38  forces the rolling cam  40  towards the proximal end  50   a  of the carrier  50 , or stated alternatively the distance between the rim arcuate reinforcement  22  or proximal end  49   a  of the biasing element  49  and the cam surface  39  decreases when the carrier  50  is pivoted out of the rest position. 
     To adjust the force to breakaway or pivot the movable portion  20   a  of the rim assembly  20  relative to the fixed portion  20   b , the overall length of the shaft  60  can be adjusted by an actuator  42 . In the embodiment shown, the actuator  42  is a threaded bolt accessible through an opening  27   a  in the rim arcuate reinforcement  22  of the rim  24  to allow for adjustment of the tension without removing structure or disassembly of rim components. The shaft  60  may include a first member  63  and a second member  64  in a telescoping engagement, with the first member  63  slideably engaging the second member  64 . The second member  64  at the distal end  60   b  of the shaft  60  may include the rotating cylinder  70  while the first member  63  may be adjacent the biasing element  49 . The first member  63  may not rotate relative to the second member  64  about the longitudinal axis Lr. One embodiment to limit rotation may be a ball and longitudinal groove engagement between contacting surfaces of the shaft first member  63  and second member  64 . In one embodiment, the longitudinal groove  63   a  is in the outer cylindrical surface of the first member  63  and receives at least a portion of a ball or ball bearing  64   a  retained by a lateral opening  64   b  the second member. The ball  64   a  longitudinally travels within the groove  63   a  when adjusting the overall length of the shaft  60 . However, the ball and groove engagement does not allow rotation of the first member  63  relative to the second member  64  when the actuator  42  is rotated. The actuator  42  is threaded within the first member  63  and one end contacts a bottom surface  64   c  of a longitudinal opening  64   d  facing the biasing element  49 . The biasing element  49  extends between the outwardly facing end or radially extending flange  63   b  of the first member  63  or proximal end  60   a  of the shaft  60  and the arcuate reinforcement  22  of the rim  24 . As shown, the actuator  42  extends through the biasing element  49 . By actuating or threading the actuator  42  in one direction, for example clockwise, the actuator  42  drives or slides the first member  63  away from the second member  64  and thus increases the overall length of the shaft to a first overall length L 1  ( FIG. 12 ) thereby increasing the tension applied from the rolling cam  40  to the cam surface  39 . Alternatively, if the actuator  42  is threaded along the longitudinal axis in the opposite direction, for example counter clockwise, the first member  63  slides or telescopes towards the second member  64  and thus reducing the overall length to a second overall length L 2  ( FIG. 11 ) of the shaft  60  and thereby reducing the tension. As a result, the second overall length L 2  is smaller than the first overall length L 1 . 
     At least shown in  FIG. 6 , the longitudinal carrier  50  pivots about its pivoting axis P perpendicular to the longitudinal axis Lc. The carrier  50  can have a longitudinal tubular body  52  that slidable engages the rolling cam  40  and the biasing element  49 . A pair of lateral tubular projections  56  extend laterally from the tubular body  52  and have a left end opening  54   a  and a right end opening  54   b . The left and right end openings  54   a ,  54   b  can be in alignment with side openings  32   a  formed in the bracket plates  32  for receiving one or more fasteners  55 . When the carrier  50  is coupled to the bracket plates  32 , the lateral tubular projections  56  define the pivot axis P of pivot of the rim assembly. The end openings  54   a ,  54   b  can be threaded in order to be threadably attached with the fasteners  55 . The pair of opposing fasteners  55  extends from threaded receiving end openings  54   a ,  54   b  along the pivot axis P laterally away from the outer diameter of the carrier tubular body  52 . The fasteners  55  engage the mounting frame  30  that is fixed to the backboard  10  and allows at least the carrier  50 , rim  24 , biasing element, and rolling cam  40  to pivot about pivot axis P. The carrier  50  allows the rolling cam  40  to pivot along the midplane M of the rim assembly  20  perpendicular to the pivot axis P without rotation about the longitudinal axis Lc. The through opening  58  within the tubular body  52  crosses the pivot axis P aligning the biasing element  49 , shaft  60 , and cylinder  70  along the longitudinal axis Lc. The inner diameter of the through opening  58  may include a grease port  57  allowing for grease to lubricate the sliding engagement between the exterior diameter of the shaft  60  and the carrier through opening  58 . The exterior surface of the carrier tubular body  52  may be substantially cylindrical with each of the proximal end  50   a  and distal end  50   b  being of a lesser outer diameter than the remainder therebetween. The proximal end  50   a  and distal end  50   b  each receive one of a pair of cylindrical eyelets  27 ,  28  fixed to the rim  24 . The larger diameter exterior may provide an inwardly abutment surface  50   c  for each respective eyelet  27 ,  28  to rest upon or align when assembled. In the embodiment shown, the eyelets  27 ,  28  are not rotational fixed to the carrier  50  to allow rim rotation about the longitudinal axis Lc of the carrier  50 . However, it should be understood that the eyelets or mechanism engaging the rim  24  to the carrier  50  may not allow relative rotation about longitudinal axis Lc in additional embodiments. Further as shown in the figures, the longitudinal slot  53  in the carrier distal end  50   b  extends through the distal end  50   b  portion having the smaller exterior diameter and the portion of the carrier  50  having the larger exterior diameter. 
     In use, any change in position of the rim  24 , which might occur as a result of a downward force on the rim  24 , such as from a dunk shot or a player hanging on the rim, may result in a corresponding change in position of the rim  24  and the movable portion  20   a .  FIG. 6  depicts an instance where a downward force being applied approximately at the front of the rim  24  to move the rim  24  to a displaced position away from the horizontal position. The carrier  50  can pivot about the pivot axis P, whereby the proximal end  50   a  is moved downward relative to a horizontal plane formed by the pivot axis P, and the distal end  50   b  can be moved upward relative to the horizontal plane. As a result of the repositioning of the distal end  50   b , the cylinder  70  at the second end of the shaft rolls upward along the cam surface  39  of the mounting plate  38 , with biasing element  49  applying the biasing force in a linear path against the cam surface  39 . The degree of angularity of the forward extending portion  34  and/or the cam surface  39  can permit an increasingly larger resistance to the breakaway of the rim due to the rolling cam  40  being displaced farther in the forward direction. 
     In response, the rolling cam  40  and biasing element  49  can reactively pivot about the pivot axis P so that the biasing element  49  is farther compressed between the shaft  60  and the arcuate reinforcement  22 , which can increase the resistance. Further, the rear eyelet  28  may move the lower end  88  of the tension members  84 ,  86  in an upward direction, and may further extend the tension members to increase the resistance caused thereby. 
     Upon release of the rim  24  from its displaced position ( FIG. 6 ), the biasing force provided by the tension members  84 ,  86  and/or the biasing element  49  can cause the cylinder  70  of the rolling cam  40  to roll to the lower end of the cam surface  39  thereby bringing the carrier&#39;s longitudinal axis Lc and the rim  24  substantially parallel to the horizontal plane. To this end, the carrier  50  is returned to its original rest position and the rim is returned to its horizontal position. This return of the carrier  50  to its rest position may allow the top plate  26  to also return to its original position. 
     As shown in  FIG. 1 , the rim  24  may be able to not only pivot relative to the fixed portion  20   b , but alternative embodiments may also rotate about the longitudinal axis Lc for a predetermined degree of rotation. With the eyelets  27 ,  28  engaging the carrier  50 , the rim  24  with fixed eyelets  27 ,  28  are able to rotate about the longitudinal axis Lc of the carrier  50 . The rotation of the rim  24  about the longitudinal axis Lc may occur at a variety of orientations of the carrier  50  relative to the fixed portion  20   b . The rotation of the rim  24  about the longitudinal axis Lc of the carrier  50  may occur, but is not limited to, when the rim  24  or movable portion  20   a  is out of the rest position. However for example, the rim may rotate when in the rest position as well as when out of the rest position. For another example the rim  24  may rotate about the longitudinal axis Lc of the carrier  50  when in the rest position and then continue to increase the range of rotation when traveling away from the rest position. As such, the mounting frame  30  may stop the degree of pivoting and/or rotating of the rim. 
     As is shown in the figures, at least the rim  24  may be coupled to tension members  84 ,  86 , such as tension springs, configured to bias the rim  24  in a predefined orientation. For example, a pair of springs may be attached to the rear eyelet  28  at the distal end  50   b  of the carrier  50 . The left and right tension members  84 ,  86  are preferably spaced equidistant from a midplane M defined by the longitudinal axis Lr of the rolling cam  40 , as shown in  FIG. 7 . As shown in  FIG. 5 , a lower end  88 , opposite the hook end  87 , such as a spring coil portion, of the tension members  84 ,  86  can be coupled to the base plate  31 . The lower end  88  can be coupled to the base plate  31  so that the tension members  84 ,  86  are vertically oriented. In one example, the base plate  31  includes an opening  31   a  for receiving and mounting a guiding rod  31   b , such as a threaded screw, that extends upright from the base plate  31 . An upper end portion of the guiding rod  31   b  can be inserted through an aperture defined by the lower end  88  of the tension member  84 ,  86 . It is contemplated that the tension members  84 ,  86  can be situated as compression members as appreciated by those skilled in the art. In use, the tension members  84 ,  86  can resist rotational effects of the rim  24  about the longitudinal axis Lc. If used, the tension members  84 ,  86  may also assist to urge or to pivot the movable portion  20   a  back to the rest position. It is also shown that the one or more rubber stops or pads  32   b  may be positioned between the fixed portion  20   b  and movable portion  20   a  to prevent metal to metal contact during a range of relative motion between the fixed and movable portions. In particular, the pads  32   b  may dampen the rim  24  return from the displaced position to the rest position. It can also be shown in the figures that the rotation of the rim  24  about the longitudinal axis Lc may be independent of the rolling cam  40 . As a result, the cylinder  70  of the rolling cam  40  rolls in a substantially linear path regardless of the rotation of the rim  24  about the longitudinal axis Lc. As such the rim  24  may be constructed without rotational movement if desired. 
     As illustrated in  FIGS. 16 and 17 , the rim assembly  20  may include a leveling mechanism  90  to allow for leveling of the rim  24  to a substantially horizontal orientation relative to the substantially vertical basketball backboard  10 . Instead of washers previously used to level typical rims, the mounting frame  30  includes a leveling mechanism  90  having one or more inclined surfaces  91  slidingly engaging a corresponding one or more wedges  92 . Each set of inclined surface  91  and wedge  92  may define the through opening  33  for receiving a bolt to secure the rim assembly  20  to the backboard  10 . The mounting plate  38  includes the inclined surface  91  spaced from the abutment surface  36   a  of the planar portion  36 . The wedge  92  engages the inclined surface  91  and may be driven by an actuator  94  from a first position ( FIG. 16 ) to a second position ( FIG. 17 ). One embodiment of the actuator  94  is a set screw as shown. The actuator  94  may operably position the wedge  92  in relation to the inclined surface  91 . The actuator  94  can drive the wedge  92  up the inclined surface  91  to the second position and/or allow the wedge  92  to travel down to the first position. When in the first position ( FIG. 16 ), the wedge  92  and inclined surface  91  engagement creates a first thickness T 1 . When in the second position ( FIG. 17 ), the wedge  92  and inclined surface  91  engagement creates a second thickness T 2 , wherein the second thickness T 2  is larger than the first thickness T 1 . When having a second thickness T 2 , the wedge  92  may project past the abutment surface  36   a  as shown in  FIG. 17  spacing the abutment surface  36   a  from the backboard  10 . With the one or more leveling mechanisms  90  shown in one embodiment at the lower end of the mounting plate  38 , in use the user can raise portions of or the front of the rim  24  by increasing the thickness to the second thickness T 2  in one or more of the leveling mechanisms  90 . Further in use, by decreasing the thickness to the first thickness T 1 , the front of the rim  24  or portions thereof can be lowered in relation to the vertical backboard  10 . It may also be advantages to have adhesive tape (not shown) to temporarily hold the wedge  92  in contact with the inclined surface  91  before mounting the rim assembly  20  to the backboard  10 . However, a variety of embodiments, other than adhesive, may have additional structure to maintain capture of the wedge in relation to the mounting plate  38  for handling purposes. 
     An additional embodiment is shown in  FIGS. 18 and 19 , if desired an engagement between the pin  80  and the cylinder  70  may provide for the rim  24  to be bumped or moved relative to pivot axis P without operating the breakaway feature of the basketball rim assembly  20 . Stated alternatively, the rim assembly  20  may distinguish between the force of a basketball shot hitting the rim  24  as compared the forces of a dunk upon the rim  24  that results in the rim breaking away. The movable portion  20   a  or rolling cam  40  may include a second cam surface  72  in the linkage between the pivot axis P and the outer cylindrical surface  74 , or could be said to be in series with the first cam surface  39 . In the embodiment shown, the second cam surface  72  is the inner cylindrical surface of the cylinder  70 . The inner cylindrical surface  72  of the cylinder  70  includes an inner diameter. As opposed to a friction fit or press fit between pin  80  and the cylinder  70 , the pin  80  may change positions in relation to the inner through opening defined by the inner cylindrical surface  72  of the cylinder  70 , or more specifically travel upon the inner cylindrical surface  72 . The pin  80  includes an outer cylindrical surface  83  with an outer diameter. The cylinder&#39;s  70  inner diameter is larger than an outer diameter of the pin  80  whereby a space or clearance is defined therebetween. This space or clearance may be exaggerated in  FIGS. 18 and 19  to illustrate the available relative movement. A longitudinal axis of the pin  80  is out of alignment with a longitudinal axis of the cylinder  70 , this is more readily shown when in the rest position of  FIG. 18 . In the embodiment shown in  FIG. 18 , a crescent shape clearance is defined when pin  80  applies the straight-line pressure along the longitudinal axis Lc to the inner cylindrical surface  72  of the cylinder  70  and subsequently to the cam surface  39 . As a result, the clearance therebetween allows for the pin  80  and connected shaft  60 , carrier  50 , and rim  24  to have a degree of freedom to pivot about the pivot axis P without pivoting the cylinder  70  out of the rest position. The pin  80  and cylinder  70  in the rest position is shown in  FIG. 18 . Any adjustment of the biasing element  49  does not change the respective clearance available with respect to the second cam surface  72 , and alternatively changing the amount of clearance between the pin  80  and cylinder  70  does not affect the pressure that can be applied. Therefore, the first displacement of pin  80  in relation to the second cam surface  72  or cylinder  70  at a variety of pressures may result in a corresponding movement or pivot of the rim  24  depending on the amount of clearance provided. Further if the second cam surface  72  is used with the clearance between the pin  80  and cylinder  70 , the first displacement of the pin  80  and subsequent rim  24  movement occurs before the rolling contact of the cylinder  70  and first cam surface  39  occurs, if and when this breakaway and rolling contact even occurs. Stated alternatively, if the pin  80  cannot travel further within the clearance or relative to the second cam surface  72 , the force applied to the rim may be sufficient enough to pivot the cylinder  70  from the rest position ( FIGS. 5 and 18 ) to the displaced position ( FIG. 6  in order to provide the breakaway. The breaking away of the rim  24  results in a larger second displacement that encompasses the first displacement of the rim  24  due to the pin clearance relative to the second cam surface  72 . As mentioned above, it may also be desired to adjust the first displacement or rim bump by selecting a predetermined variance between the outer diameter of the pin  80  and the inner diameter of the cylinder  70  to obtain varying degree of first displacements or clearance to achieve different results or degree of rim movement and/or pivot before the breakaway occurs. Stated alternatively, the larger the difference in diameters the more displacement of the rim before the rim breaks away. 
     While several inventive embodiments have been described and illustrated herein, those of ordinary skill in the art will readily envision a variety of other means and/or structures for performing the function and/or obtaining the results and/or one or more of the advantages described herein, and each of such variations and/or modifications is deemed to be within the scope of the invent of embodiments described herein. More generally, those skilled in the art will readily appreciate that all parameters, dimensions, materials, and configurations described herein are meant to be exemplary and that the actual parameters, dimensions, materials, and/or configurations will depend upon the specific application or applications for which the inventive teachings is/are used. Those skilled in the art will recognize, or be able to ascertain using no more than routine experimentation, many equivalents to the specific inventive embodiments described herein. It is, therefore, to be understood that the foregoing embodiments are presented by way of example only and that, within the scope of the appended claims and equivalents thereto, inventive embodiments may be practiced otherwise than as specifically described and claimed. Inventive embodiments of the present disclosure are directed to each individual feature, system, article, material, kit, and/or method described herein. In addition, any combination of two or more such features, systems, articles, materials, kits, and/or methods, if such features, systems, articles, materials, kits, and/or methods are not mutually inconsistent, is included within the inventive scope of the present disclosure. Further, it is to be understood that continuously or substantially continuously may include one or more interruptions, delays, etc. in controlling characteristics such as but not limited to the quantities, rates, measurements disclosed herein and still be within the scope of the embodiments. Alternatively, control or adjustments may be considered or provided intermittently. 
     All definitions, as defined and used herein, should be understood to control over dictionary definitions, definitions in documents incorporated by reference, and/or ordinary meanings of the defined terms. The indefinite articles “a” and “an,” as used herein in the specification and in the claims, unless clearly indicated to the contrary, should be understood to mean “at least one.” When used in this description and the claims as an adjective rather than a preposition, “about” means “approximately” and comprises the stated value and every value within 10% of that value. For example, “about 100%” would include measurements of 90% and 110%, as well as every value in between. The phrase “and/or,” as used herein in the specification and in the claims, should be understood to mean “either or both” of the elements so conjoined, i.e., elements that are conjunctively present in some cases and disjunctively present in other cases. 
     Multiple elements listed with “and/or” should be construed in the same fashion, i.e., “one or more” of the elements so conjoined. Other elements may optionally be present other than the elements specifically identified by the “and/or” clause, whether related or unrelated to those elements specifically identified. Thus, as a non-limiting example, a reference to “A and/or B”, when used in conjunction with open-ended language such as “comprising” can refer, in one embodiment, to A only (optionally including elements other than B); in another embodiment, to B only (optionally including elements other than A); in yet another embodiment, to both A and B (optionally including other elements); etc. 
     As used herein in the specification and in the claims, “or” should be understood to have the same meaning as “and/or” as defined above. For example, when separating items in a list, “or” or “and/or” shall be interpreted as being inclusive, i.e., the inclusion of at least one, but also including more than one, of a number or list of elements, and, optionally, additional unlisted items. Only terms clearly indicated to the contrary, such as “only one of” or “exactly one of,” or, when used in the claims, “consisting of,” will refer to the inclusion of exactly one element of a number or list of elements. In general, the term “or” as used herein shall only be interpreted as indicating exclusive alternatives (i.e. “one or the other but not both”) when preceded by terms of exclusivity, such as “either,” “one of,” “only one of,” or “exactly one of” “Consisting essentially of,” when used in the claims, shall have its ordinary meaning as used in the field of patent law. 
     As used herein in the specification and in the claims, the phrase “at least one,” in reference to a list of one or more elements, should be understood to mean at least one element selected from any one or more of the elements in the list of elements, but not necessarily including at least one of each and every element specifically listed within the list of elements and not excluding any combinations of elements in the list of elements. This definition also allows that elements may optionally be present other than the elements specifically identified within the list of elements to which the phrase “at least one” refers, whether related or unrelated to those elements specifically identified. Thus, as a non-limiting example, “at least one of A and B” (or, equivalently, “at least one of A or B,” or, equivalently “at least one of A and/or B”) can refer, in one embodiment, to at least one, optionally including more than one, A, with no B present (and optionally including elements other than B); in another embodiment, to at least one, optionally including more than one, B, with no A present (and optionally including elements other than A); in yet another embodiment, to at least one, optionally including more than one, A, and at least one, optionally including more than one, B (and optionally including other elements); etc. 
     It should also be understood that, unless clearly indicated to the contrary, in any methods claimed herein that include more than one step or act, the order of the steps or acts of the method is not necessarily limited to the order in which the steps or acts of the method are recited. 
     In the claims, as well as in the specification above, all transitional phrases such as “comprising,” “including,” “carrying,” “having,” “containing,” “involving,” “holding,” “composed of,” and the like are to be understood to be open-ended, i.e., to mean including but not limited to. Only the transitional phrases “consisting of” and “consisting essentially of” shall be closed or semi-closed transitional phrases, respectively, as set forth in the United States Patent Office Manual of Patent Examining Procedures, Section 2111.03. 
     The foregoing description of several methods and embodiments have been presented for purposes of illustration. It is not intended to be exhaustive or to limit the precise steps and/or forms disclosed, and obviously many modifications and variations are possible in light of the above teaching. It is intended that the scope and all equivalents be defined by the claims appended hereto.