Abstract:
The brake disclosed herein provides a linear brake kinematic over a wide range of wheel rim sizes. The brake provides for the same brake feel and response to the rider throughout actuation of the brake lever. Also, the brake feel and response may be designed to be the same even if a different wheel rim size is mounted to the bicycle. In an aspect of the brake, this is accomplished by forming a curved configuration, namely, a cam profile on upper portions of left and right brake arms. These upper portions of the left and right brake arms extend away from the wheel so that the cam profiles formed in the upper portions of the left and right brake arms may be made as long as necessary to accommodate the wide range of rim sizes.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is a non-provisional patent application which claims priority to U.S. Provisional Patent Application Ser. No. 61/751,171, filed on Jan. 10, 2013, the entire contents of which is expressly incorporated herein by reference. 
     
    
     STATEMENT RE: FEDERALLY SPONSORED RESEARCH/DEVELOPMENT 
       [0002]    Not Applicable 
       BACKGROUND 
       [0003]    The various embodiments disclosed herein relate to a brake system for a bicycle. 
         [0004]    A bicycle brake serves one basic purpose, specifically, to translate the force applied by the rider by way of a brake lever into a force that drives brake pads against the rim of a bicycle. The friction between the brake pads and the rim slows down or stops the bicycle. Thus the brake lever and the brake comprise a mechanical system that amplifies the rider&#39;s effort. 
         [0005]    A key characteristic of the brake design is its brake kinematics or how the braking force behaves and feels to the rider as the rider depresses the brake lever. The brake kinematics defines the braking power of the brake as a function of depression of the brake lever. For example, the brake kinematics may provide a unit increase in brake force for unit travel of the brake lever. Moreover, riders utilize their bicycles for various purposes such as training and racing. To utilize the same bicycle for training and racing, the rider may switch out the bicycle wheels from their training wheels, typically having narrow rims, to their race wheels, which typically have wider rims. In order to do so, the rider must adjust the brake to accommodate the different rim widths. Unfortunately, current designs do not allow for simple changeovers between different rim sizes while maintaining a linear brake kinematic. 
         [0006]    Accordingly, there is a need in the art for an improved brake. 
       BRIEF SUMMARY 
       [0007]    The various embodiments of the brake disclosed herein addresses the needs discussed above, discussed below and those that are known in the art. 
         [0008]    The brake disclosed herein provides a linear brake kinematics over a very wide range of operation. In particular, the brake provides for linear brake kinematic when a wheel with a narrow rim is mounted to the bicycle. The same is also true in that the brake provides linear brake kinematics when a wheel with a wide rim is mounted to the bicycle. Moreover, the changeover from the narrow rim to the wide rim, and vice versa is quick and does not require substantial adjustments. The brake kinematic is designed so that a slope of the brake kinematic is linear and constant throughout the entire range of acceptable rim sizes for use with the brake. In an aspect this is accomplished by placing a curved configuration on the brake arm that is shaped to provide the linear brake kinematic. The brake additionally has adjustments for laterally positioning brake pads of the brake to align the brake pads to a wheel rim that is off-center (i.e. not aligned to the hub). 
         [0009]    More particularly, a brake for a bicycle is disclosed. The brake may comprise a first brake arm, a second brake arm, a cam driver and a brake lever. The first brake arm may pivot about a first pivot axis. An upper portion of the first brake arm may define a first camming surface. A lower portion of the first brake arm may be capable of receiving a first brake pad. 
         [0010]    The second brake arm may pivot about a second pivot axis. The second pivot axis may be set at a fixed distance away from the first pivot axis. An upper portion of the second brake arm may define a second camming surface. The first and second camming surfaces may have a minor configurations of each other. A lower portion of the second brake arm may be capable of receiving a second brake pad. 
         [0011]    The cam driver may be disposed between the first and second camming surfaces. The cam driver may maintain contact with the first and second camming surfaces between unactuated and actuated positions of the brake. 
         [0012]    The brake lever may be secured to a handlebar of the bicycle for actuating the brake. 
         [0013]    The first and second camming surfaces formed in the upper portions of the brake arms may have a curved configuration so that a linearly increasing brake force is applied to a rim of the bicycle for each unit of displacement of the brake lever regardless of the size of the rim. 
         [0014]    The first and second brake arms may be directly mounted to a common plate so that the first brake arm pivots about the first pivot axis and the second brake arm pivots about the second pivot axis. The common plate is mounted to a fork of the bicycle. The common plate may pivot with respect to the fork or the frame of the bicycle to laterally adjust brake pads of the brake to align the brake pads to an off center wheel rim. 
         [0015]    The cam driver may be positioned on the first and second camming surface for rim widths between 19-28 mm. A unit linear displacement of the cam driver may translate into a unit angular displacement of the lower portion of the first and second brake arms so that a unit displacement of the brake lever produces a linear rise in brake force. 
         [0016]    The lengths of the first and second camming surfaces may be sufficiently long so that a linear brake force is applied to the wheel rim for rim widths between 19 mm and 28 mm or wider, by solely changing a position of the cam driver on the first and second camming surfaces. 
         [0017]    In another aspect, a method of fabricating a brake arm for providing a linear rise in brake force for each unit displacement of a brake lever is disclosed. The method may comprise the steps of selecting first, second and third linear positions of the cam driver; selecting first, second and third angular positions of a lower portion of a brake arm or linear displacements of the brake pads wherein the spacings between the first, second and third linear positions of the cam driver are proportional the spacings between the first, second and third angular positions of the lower portion or the linear displacement of the brake pads; mapping first, second and third positions of the cam driver on an upper portion of the brake arm; and creating a spline which connects the first, second and third positions of the cam driver on the upper portion of the brake arm. 
         [0018]    The step of mapping may include the steps of positioning the cam driver at a first linear position and the brake arm at a first position; marking the cam driver on the brake arm to identify the first position of the cam driver on the brake arm; positioning the cam driver at a second linear position and the brake arm at a second rotary position; marking the cam driver on the brake arm to identify the second position of the cam driver on the brake arm; positioning the cam driver at a third linear position and the brake arm at a third rotary position; and marking the cam driver on the brake arm to identify the third position of the cam driver on the brake arm. 
         [0019]    The spline creation step may include the step of creating a curved spline defined by the marks of the cam driver representing the first, second and third positions. 
         [0020]    The marking step may include the step of outlining a contact surface of the cam driver on the brake arm. 
         [0021]    The mapping and creating steps may be accomplished with a computer aided drafting computer program having a representation of the cam driver and the brake arm. Alternatively, the creating step may be accomplished by way of a mathematical model. 
         [0022]    The creating step may include the step of defining the spline as a B-spline, P-spline, other splines known in the art or combinations thereof. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0023]    These and other features and advantages of the various embodiments disclosed herein will be better understood with respect to the following description and drawings, in which like numbers refer to like parts throughout, and in which: 
           [0024]      FIG. 1  is a perspective view of a brake; 
           [0025]      FIG. 2  illustrates the brake shown in  FIG. 1  used in conjunction with a wide rim; 
           [0026]      FIG. 3  illustrates the brake shown in  FIG. 1  used in connection with a narrow rim; 
           [0027]      FIG. 4  illustrates the brake shown in  FIG. 1  wherein brake pads are adjusted laterally by rotating the brake to account for an off-center rim; 
           [0028]      FIG. 5  illustrates left and right brake arms of the brake shown in  FIG. 1 ; 
           [0029]      FIG. 6  illustrates a return spring used to traverse the left and right brake arms to a release position when a brake lever of the brake is released; 
           [0030]      FIG. 7  illustrates a backing plate for mounting the brake to a fork or a frame (e.g., adjacent to a bottom bracket shell) of a bicycle and mounting the various components of the brake cooperatively to each other; 
           [0031]      FIG. 8  illustrates a cam driver for activating the brake upon actuation of the brake lever; 
           [0032]      FIG. 9  illustrates a cover plate of the brake shown in  FIG. 1 ; 
           [0033]      FIG. 10  graphically illustrates brake kinematic characteristics of the brake defined by or defining a cam profile formed in the left and right brake arms; 
           [0034]      FIG. 11  illustrates a first position of the brake used to define the cam profile; 
           [0035]      FIG. 12  illustrates a second position of the brake used to define the cam profile; 
           [0036]      FIG. 13  illustrates a third position of the brake used to define the cam profile; 
           [0037]      FIG. 14  illustrates a fourth position of the brake used to define the cam profile; 
           [0038]      FIG. 15  illustrates outlines of rollers of the cam driver superimposed on the brake levers shown in  FIGS. 11-14  for defining a spline of the cam profile; 
           [0039]      FIG. 16  illustrates a rear view of the brake shown in  FIG. 1 ; 
           [0040]      FIG. 17  illustrates the brake integrated into a fork and a cover disposed over the brake to increase aerodynamics; 
           [0041]      FIG. 18  illustrates the brake integrated into a frame adjacent to the bottom bracket shell of a bicycle and a cover disposed over the brake to increase aerodynamics; 
           [0042]      FIG. 19  illustrates the brake shown in  FIG. 14  for mounting to an exterior of a bicycle; and 
           [0043]      FIG. 20  illustrates the brake shown in  FIG. 19  for mounting to a fork of the bicycle. 
       
    
    
     DETAILED DESCRIPTION 
       [0044]    Referring now to the drawings, a brake  10  for a bicycle  12  is shown. The brake  10  is capable of receiving a wide rim  14   a  or a narrow rim  14   b  without significant adjustments to the brake  10  (see  FIGS. 2 and 3 ) except for (1) spreading open the brake pads  16  or closing down the brake pads  16  as the case may be and (2) adjusting for lateral positioning of the brake pads  16  which may be needed due to an off-center rim  14  (see  FIG. 4 ). Accordingly, the brake  10  provides for ease of interchangeability for different rim widths. A rider may easily switch between training wheels, typically having narrow width aluminum rims, to racing wheels, typically having wider carbon fiber rims without requiring brake pad adjustment or spacers to be added to the brake shoes and other adjustments required by the prior art. Also, the brake  10  provides for an easy method of aligning the brake pads  16  to a wheel rim that may be off-center. The brake  10  also provides for custom designable kinematics (e.g., predictable linear braking kinematics) across the entire range of rim widths useable with the brake  10 . Additionally, the brake  10  provides for a low side profile and a small frontal footprint so that the brake  10  may be integrated into a fork or frame (e.g., bottom bracket shell or seat stays) so that an aerodynamic cover may be disposed over the brake  10  while fitting within conventional boundaries of a fork or frame of a bicycle. In addition, the brake may be mounted in a conventional manner ahead of the front fork, or on behind the rear seat stays of the bicycle, where its low frontal footprint would also offer aerodynamic advantages over the typical sidepull style bicycle brake. 
         [0045]    The brake  10  has left and right brake arms  18 ,  20  that are pivotable about left and right pivot axes  22 ,  24 . Upper portions  26 ,  28  of the left and right brake arms  18 ,  20  may have left and right camming surfaces  30 ,  32  that are driven by cam driver  34 . The cam driver  34  is traversed along the length of the left and right camming surfaces  30 ,  32  under the power of a brake lever  36  or return spring  38 . In  FIGS. 2 and 3 , the cam driver is shown as being traversed vertically. However, it is also contemplated that the cam driver  34  may be traversed in other directions such as horizontally (see  FIG. 18 ) or at an angle if the brake  10  is mounted to the upper portion of the seat stays. By locating the camming surfaces  30 ,  32  on the upper portions  26 ,  28  of the left and right brake arms  18 ,  20 , the left and right camming surfaces  30 ,  32  may be fabricated to be sufficiently long to accommodate wide and narrow rims  14  as desired. The cam driver  34  can be positioned anywhere along the camming surfaces  30 ,  32  by way of a cam driver adjustment mechanism  42  to adjust the initial default position of the brake and accommodate the wheel rim. For narrow rims, the cam driver  34  is positioned higher up on the camming surfaces  30 ,  32  by way of the cam driver adjustment mechanism  42 , as shown in  FIG. 3 . For wide rims, the cam driver  34  is positioned lower down on the camming surfaces  30 ,  32  by way of the cam driver adjustment mechanism  42 , as shown in  FIG. 4 . By way of example and not limitation, the brake  10  may preferably accept rim widths between 19 mm-28 mm. It is also contemplated that the brake  10  may be designed to also accept rim widths less than 19 mm or greater than 28 mm up to about 32 mm or 35 mm. Once the position of the cam driver  34  is set on the camming surfaces  30 ,  32 , a brake lever is used to actuate the brake between a braking position and a release position (i.e., initial default position). The cam driver  34  travels a short travel distance range 40 along the length of the left and right camming surfaces  30 ,  32  in order to actuate the brake  10  between the braking position and the release position. The brake lever  36  pulls on a cable  44  to actuate the brake  10  and traverse it to the braking position and stop or slow down the bicycle. A return spring  38  traverses the brake  10  to the release position upon release of the brake lever. The camming surfaces  30 ,  32  may be designed and configured to provide a custom braking kinematics (e.g., linear, progressive, regressive, combinations thereof, etc.) within the short travel range 40. By way of example and not limitation, the kinematics of the brake may be designed to have a steeper slope at the beginning of the travel until the brake pads are brought into contact with the rim, and a smaller slope which is linear when the brake pads are pressing against the rim. 
         [0046]    Moreover, by incorporating one or more of the various features discussed herein including but not limited to the placement of the camming surfaces  30 ,  32  on the upper portions  26 ,  28  of the left and right brake arms  18 ,  20 , the brake  10  may have (1) a low side profile so that the brake  10 , a cover  116  (see  FIG. 17 ) and fork may be 80 mm or less in relation to its depth and (2) a narrower frontal footprint  126  compared to the frontal footprint of the fork (see  FIG. 4 ) or a bottom footprint for rear brakes  10 . 
         [0047]    Referring to  FIG. 4 , the brake  10  can also be rotated in order to laterally align the brake pads  16  to the wheel rim  14  in the event that the wheel rim  14  is off-center from a hub of the wheel. This lateral adjustment of the brake pads  16  may be accomplished with a standard bicycle tool, namely, an Allen wrench  46  without removal of any parts or substantial work. More particularly, centerline  130  identifies the vertical centerline of the fork of the bicycle which lines up with the brake  10  or centerline of post  84 . Centerline  132  identifies the centerline of the rim  14 . The rim  14  may be off-center from the centerline of the bicycle frame or fork, either as a result of manufacturing tolerances in the frame or fork, or in the assembly of the wheel itself. True center would result in the centerline  132  of the wheel matching up and being aligned with the centerline of the frame  130 . However, true center is typically not achieved. Rather, the rim  14  is trued to itself. As such, as shown in  FIG. 4 , instead of attempting to achieve true center of the rim  14 , the brake pads  16  are laterally shifted by rotating the brake  10  about the central post  84  by use of the Allen wrench or movement of the entire brake mechanism itself by way of the person&#39;s hands. After rotating the brake  10  to align the brake pads  16  to the rim  14 , the brake  10  remains in place as will be discussed below through the means for mounting the brake  10  to the fork or the frame. 
         [0048]    Referring now to  FIGS. 5-9 , the left and right brake arms  18 ,  20  are shown. The left and right brake arms  18 ,  20  have a mounting hole  48  about which the left and right brake arms  18 ,  20  pivot and are aligned to the pivot axes  22 ,  24 . The upper portions  26 ,  28  of the left and right brake arms  18 ,  20  incorporate the left and right camming surfaces  30 ,  32 . The left and right camming surfaces  30 ,  32  when assembled into the brake  10  have minor configurations so that as the cam driver  34  traverses along the length of the left and right camming surfaces  30 ,  32 , the brake pads  14  travel the same distance at a predefined rate (e.g., linear). The lower portions  50 ,  52  below the pivot axes  22 ,  24  and the through holes  48  secure the brake pads  16  to the brake arms  18 ,  20 . The lower portions  50 ,  52  may additionally have receiving holes  54  for receiving distal ends  56  of the return spring  38 . The return spring  38  biases the lower portions  50 ,  52  of the brake arms  18 ,  20  to the released position when the brake lever  36  is released. In the released position, the brake pads  16  do not contact the wheel rim  14 . When the user squeezes the brake lever  36 , the cable  44  (see  FIG. 2 ) traverses the cam driver  34  upward to spread the upper portions  26 ,  28  of the brake arms  18 ,  20  and squeeze the lower portions  50 ,  52  inward to apply a braking force to the wheel rim  14  by way of the brake pads  16 . This traverses the brake pads  16  to the braking position. The user may release the brake lever  36  which allows the return spring  38  to spread open the brake pads  16  to release the wheel rim  14 . This traverses the brake pads  16  to the release position or the initial default position. 
         [0049]    To assemble the brake  10 , a backing plate  60  is mounted to a fork or frame of a bicycle. The left and right brake arms  18 ,  20  are mounted to the backing plate  60 . The backing plate  60  may have two parallel posts  62 . The two posts  62  are received into the mounting holes  48  of the left and right brake arms  18 ,  20 . The posts  62  guide the brake arms  18 ,  20  about its rotational travel. Pivot bushings  64  may be mounted into the through holes  48  to facilitate rotational movement of the left and right brake arms  18 ,  20  and to prevent frictional resistance. 
         [0050]    The cam driver  34  (see  FIG. 8 ) has a body  66 . The body  66  incorporates two rollers  68 , one on each side of the body  66 . These rollers  68  contact the respective left and right camming surfaces  30 ,  32  of the left and right brake arms  18 ,  20 . The rollers  68  may be pinned to the body  66  with pins  70 . Alternatively, it is also contemplated that the body  66  may incorporate a single roller on either side of the body  66 . The body  66  may additionally have a through hole  72  which is sufficiently large to receive the cable  44  but not large enough for a crimp  74 . During assembly, the cable  44  is inserted through the through hole  72 . The distal end of the cable  44  receives a crimp  74  to prevent the exposed end of the cable  44  from fraying. The cable  44  is secured to the body  66  of the cam driver  34  via a set screw  75 . The backside of the body  66  may have a guide  76  having opposed tongues  78 . These tongues  78  are received into grooves  80  or a T-shaped channel formed in the backing plate  60 . The guide  76  limits the travel of the cam driver  34  to a linear direction defined by the grooves  80  in the backing plate  60 . The grooves  80  and the post  62  are preferably symmetrical with each other about a vertical plane  82 . The backing plate additionally has a central post  84  which extends in an opposite direction from the post  62  and is used to mount the brake  10  to the bicycle  12 . The post  84  is mounted to the fork or frame (e.g., adjacent to bottom bracket shell). A cover plate  86  (see  FIG. 9 ) is mounted over the brake arms  18 ,  20  and secured to the post  62  with countersunk screws  88 . The cam driver  34  additionally has a nose  138  (see  FIGS. 1 and 8 ) that rests on the cover plate  86  during the assembly process. The nose  138  may rest on top of the cover plate  86  (see  FIG. 1 ) to position the cam driver  34  while inserting the cable  44  into the cam driver  34 , securing the cable via a set screw  75  and finally placing a crimp  74  on the cable  44 . The center of the cover plate  86  may have a hex opening  90  to adjust the lateral position of the brake pads  16 , as shown in  FIG. 4 . An Allen wrench  92  may be received into the hex opening  90  to rotate the brake  10  and adjust the lateral position of the brake pads  16  so as to align the brake pads  16  to the wheel rim, as discussed above. 
         [0051]    Referring now to  FIGS. 10-15 , a methodology of creating the spline of the cam profiles of the left and right camming surfaces  30 ,  32  is shown. The first step is shown in  FIG. 10 , namely, the step of establishing desired brake kinematic characteristics. In the example shown in  FIG. 10 , the brake kinematic characteristic is described in relation to a brake cable pull distance as a function of brake pad travel distance. However, other ways of describing the brake kinematic characteristics are also contemplated. By way of example and not limitation, brake cable pull distance may be graphed or calculated as a function of braking force. Another example would be brake cable pull distance as a function of angular rotation of the brake arm  18 ,  20 . However, for the purposes of simplicity and in this discussion, the brake kinematic characteristic is described in relation to brake cable pull distance as a function of brake pad travel distance. In the example discussed herein, the brake kinematic is shown and described as being linear. However, other kinematics are also contemplated such as progressive, exponential, regressive or combinations thereof. 
         [0052]    Preferably, the brake kinematic characteristic is linear. This means that for each unit displacement of the brake cable, there is a unit displacement of the brake pad travel distance or a unit rotational displacement of the brake arm. In mathematical terms, the brake kinematic characteristic may be described as Y=MX. The M describes the rate at which the brake pad travel distance increases for each incremental unit of brake cable pull distance. As used herein, the linear nature of the brake kinematic characteristic would still be considered linear when the brake cable pull distance is within 10%, and more preferably within 5% of the desired brake cable pull distance utilizing the mathematical equation Y=MX. Some deviation from linear is allowed without deviating from the baseline characteristic (e.g., linear as shown in  FIG. 10 , progressive, regressive, combination, etc.). In  FIG. 10 , by way of example and not limitation, the brake kinematic characteristic is described by the equation Y=1.68X wherein 1.68 is calculated from the graph shown in  FIG. 10  as M=((16.9-8.5)/(10-5)). Accordingly, the actual brake kinematic characteristic of the brake may be anywhere between Y=1.85X and Y=1.51X which is plus or minus 10% of 1.68. As long as the brake kinematic functions within these parameters, the brake kinematic is still considered to be linear. Linear is defined as being between plus or minus 10% to plus or minus 5% of the calculated slope M in the equation Y=MX. The allowance from linear is represented by the dash lines in  FIG. 10 . Although a slope of 1.68 was used in this example, the slope may be designed to be at different slopes for industry standards or as desired. 
         [0053]    To define the profile of the camming surface  30 ,  32  that matches the desired brake kinematics characteristics shown in the graph of  FIG. 10 , various snapshots of the cam driver  34  and the brake arm  18 ,  20  are taken at different positions as shown in  FIGS. 11-14 . Thereafter, a spline is created that connects each of the snapshots of the cam drivers, as shown in  FIG. 15 . This process is explained further below. 
         [0054]    Referring now to  FIG. 10 , the slope M of the brake kinematic characteristic is determined. Once the slope M of the brake kinematic characteristic is determined, the brake kinematic is graphed as shown in  FIG. 10  and at least three points or positions based on the slope of the brake kinematic characteristic are calculated. In our example, four different positions are utilized to create the cam profile of the camming surface  30 ,  32 . These positions include a brake pad travel distance of zero (0) (see  FIG. 11 ) which defines the maximum gap between the brake pads  16  with a brake pad gap of 32 mm. Another position is taken as the smallest gap between the brake pads  16  of 16 mm (see  FIG. 14 ). In this position, the brake pad travel distance is 16 mm (see  FIG. 14 ) from the maximum gap shown in  FIG. 11 . Two additional points were chosen between these two extremes. In our example, a brake pad travel distance of 5 and 10 mm from zero (0) were chosen, as shown in  FIGS. 12 and 13 . For these four different positions, namely, 0 mm, 5 mm, 10 mm and 16 mm and the corresponding brake cable pull distance of 0 mm, 8.5 mm, 16.9 mm and 27 mm correspondingly are calculated or taken off of the graph shown in  FIG. 10 . In the example provided herein, four positions are preferably taken; however, it is contemplated that 3 or more positions may be used to create or define the cam profile. 
         [0055]    Referring now to  FIG. 11 , the brake arms  18 ,  20  are positioned to be at their maximum opening. In the example discussed herein, the brake arms are positioned so that the brake pads  16  are opened to have the maximum opening of 32 mm. The cam driver  34  is brought to its lowest position. Outlines  92  of the rollers  68  are traced on the upper portions  26 ,  28  of the brake arms  18 ,  20 . These outlines  92  are shown in  FIG. 12 . This can be done through a computer aided drafting program. Thereafter, the brake arms  18 ,  20  are rotated about pivot axis so that each of the brake pads  16  travel 5 mm inward from the zero (0) position, as shown in  FIG. 12 . The cam driver is moved upward 8.5 mm which is represented as being 14.4 mm above the rotating axis  22 ,  24  of the brake arms  18 ,  20 . Outlines  94  of the rollers  68  are traced on the upper portions  26 ,  28  of the brake arms  18 ,  20 . Next, the cam driver  34  is traversed upwards to 8.4 mm (16.9 mm-8.5 mm) which is represented as being 22.8 mm above the rotating axis  22 ,  24  of the brake arms  18 ,  20 , as shown in  FIG. 13 . Also, the brake arms  18 ,  22  are rotated so that the brake pads  16  travel inward 5 mm and are 22 mm apart, as shown in  FIG. 13 . Outlines  96  of the rollers  68  are traced on the upper portions  26 ,  28  of the brake arms  18 ,  20 . Once again, the brake arms  18 ,  20  are rotated so that the brake pads  16  are traversed 16 mm inward from the zero (0) position. Likewise, the cam driver  34  is traversed to be offset 16 mm from the zero (0) position which is represented as being 32.9 mm from the rotating axis  22 ,  24 , as shown in  FIG. 14 . Outlines  98  of the rollers  68  at this new position are traced on the upper portions  26 ,  28  of the brake arms  18 ,  20 . These adjustments correspond to the established brake kinematics characteristics. Each of the tracings  92 ,  94 ,  96  and  98  are preserved on the upper portions  26 ,  28  of the brake arms  18 ,  20 , as shown in  FIG. 15 . A spline  100  is created based on each of the tracings  92 ,  94 ,  96 ,  98  wherein the spline  100  is tangent to each of the circular tracings  92 ,  94 ,  96 ,  98 . This spline  100  defines the camming profiles which define the camming surfaces  30 ,  32 . The spline is defined as a B-spline, P-spline, or other splines known in the art or combinations thereof. 
         [0056]    The above methodology for creating the spline  100  that defines the camming surfaces  30 ,  32  may be accomplished in a variety of ways. By way of example and not limitation, instead of brake pad travel, brake arm rotation in relation to brake cable pull distance may be utilized. Other ways and functions are also contemplated within the scope of this disclosure. As a further method for creating or defining the spline  100 , the same  100  which defines the cam profile may be developed utilizing mathematical technique(s) analogous to the graphic cam development method described herein. For the purposes of illustrating an exemplary mathematical method and not for the purposes of limitation, the mathematical method may comprise establishing the X,Y Cartesian coordinates of the rollers  68 , for each of the brake arm  18 ,  20  positions as illustrated in  FIGS. 11-14 . The roller  68  positions are then rotated into each of the brake arm  18 ,  20  positions (see  FIG. 15 ) using a mathematical transformation for each position, corresponding to the brake arm angular displacement for said roller position from the fully open position. This establishes the Cartesian X, Y coordinates of the roller centers  68 , transposed into the full open brake position. Thereafter, a spline function is created through the roller  68  centers, by fitting a spline function thru the transposed roller X,Y center points. This final brake arm cam surface spline profile is then generated by offsetting the spline through the roller centers by a value equal to a radius of the roller  68 . This mathematical technique is exemplary and other techniques whether graphical or mathematical which known in the art or developed in the future are contemplated. 
         [0057]    Referring now to  FIG. 16 , a rear view of the brake  10  is shown. The brake  10  is mounted by way of a post  84 . This post  84  may be screwed into fitting  104  (see  FIG. 17 ) which may be embedded into a fork  106  or frame  108  (e.g., bottom bracket shell; see  FIG. 18 ) of a bicycle. The post  84  is freely rotatable from the backing plate  60  since the post  84  is a separate part from the backing plate  60 , as shown in  FIG. 7 . To mount the brake  10  to the fork  106  or frame  108 , the fitting  104  is embedded into the fork  106  or frame  108 . The fitting may be embedded on the frame adjacent to or on the bottom bracket shell and also adjacent to the upper side of the seat stays. The backing plate  60  is first mounted to the fork  106  or frame  108  by screwing the post  84  into the fitting  104 . After the backing plate  60  is mounted to the fork  106  or frame  108 , the rest of the brake components are mounted to the backing plate  60 . As shown in  FIG. 16 , a serrated washer  110  is disposed between the backing plate  60  and the fitting  104 . The serrated washer  110  fixes the angular position of the brake  10  with respect to an axis  112  defined by the post  84  upon tightening of the post  84  to the fitting  104 . With the brake  10  attached to the fork  106  or frame  108  (i.e. bottom bracket area shown in  FIG. 18 ), the brake  10  is received into a cutout  114  of the fork  106  for the frame  108 . A cover  116  is placed over the brake  10  and secured to the fork  106  by way of screws  118 . To align the brake pads  16  to the wheel rim, the allen wrench can be inserted into the front hole  150  to engage the hex hole in the cover plate  86 . As such, this brake  10  can accept a wide range of wheel rim sizes, provide a linear or any other custom designed brake kinematics at any slope desired and also provides for easy lateral adjustments for the brake pads  16 . 
         [0058]    The rotation of the brake  10  as described in relation to  FIG. 4  is limited by an interference between a pin  134  (see  FIG. 16 ) formed behind the backing plate  60  and the fitting  104 . In particular, the pin  134  is disposed within a protruding flange  136  of the fitting  104  when the backing plate  60  is mounted to the fork or frame. As such, when the brake  10  is rotated as shown in  FIG. 4 , the pin  134  is bounded by and limited by the protruding flange  136 . In this manner, the brake  10  is built with the safety mechanism to prevent the brake being rotated to a point where it might damage the brake cover  116  or  117 . 
         [0059]      FIGS. 17 and 18  show the brake  10  mounted in an integrated fashion to the fork  106  or the frame  108  so that the brake  10  is out of the normal exterior airflow and aerodynamics of the bicycle is improved by allowing the cover  116  to provide such decreased wind drag. The brake  10  may have a low side profile to allow the brake  10 , cover  116  and the fork  106  to fit within conventional fork depth requirements. In particular, the brake  10  may have a sufficiently low side profile to allow the brake, cover  116  and the fork  106  to be 80 mm or less deep. Also, the frontal footprint of the brake  10  may be narrower compared to the frontal footprint  126  of the brake  10 , as shown in  FIG. 4  to allow room for the cover and to mitigate interference with wind movement and facilitate aerodynamics. 
         [0060]    Although the brake  10  may be integrated into the fork  106 , it is also contemplated that the brake  10  may be attached by way of a brake nut  120  and spacer  122 . The serrated washer  110  is disposed behind the spacer  122 . When the brake  10  is mounted to the fork  106  or frame  108 , the brake nut  120  and the spacer  122  sandwiches the fork  106  or the frame  108 . The serrated washer  110  holds the angular rotation of the brake  10  with respect to the axis of the post  84 . The spacer  122  offsets the brake pads  16  so that the brake pads  16  do not interfere with the legs  124 . 
         [0061]    The various aspects of the brake  10  discussed herein relate to an brake system that is self contained. However, it is also contemplated that the brake arms may be mounted directly to the legs of the fork, chain stays or seat stays of the bicycle frame. 
         [0062]    The above description is given by way of example, and not limitation. Given the above disclosure, one skilled in the art could devise variations that are within the scope and spirit of the invention disclosed herein, including various ways of actuating the brake arms. Further, the various features of the embodiments disclosed herein can be used alone, or in varying combinations with each other and are not intended to be limited to the specific combination described herein. Thus, the scope of the claims is not to be limited by the illustrated embodiments.