Abstract:
In a fishing reel, in addition to an externally adjustable brake system, an automatic spool brake system adjusts spool braking action dependent upon spool rotation speed to provide brake control for preventing backlash and to achieve better casting distance by reducing spool braking force at low spool rotation speeds. A brake assembly has a plurality of brake shoes and speed adjust shoes and is slidably mounted on a spool shaft. An adjustable brake ring selectively engages the brake shoes to provide a braking action to the spool. A spring is provided for biasing the brake assembly away from the brake. Centrifugal force causes the speed adjust shoes to migrate outwardly in contact with a conical surface. The shoes impart an axial force to the brake assembly for moving the assembly towards the brake ring. At lower speeds, the spring pushes the brake assembly away from the brake ring.

Description:
FIELD OF THE INVENTION 
       [0001]    The present invention relates to centrifugal brake systems on fishing reels and, more particularly, to an automatic brake system wherein braking action on the spool is dependent upon the rotation speed of the spool in addition to an infinitive external adjustment brake system. 
       BACKGROUND OF THE INVENTION 
       [0002]    Centrifugal brake systems are commonly used on casting reels to prevent backlash. Backlash may frequently occur when the line-carrying spool is rotating at high velocities. Commonly, a brake mechanism is mounted on the spool for rotation therewith. The brake mechanism has an associated brake pad that is urged radially outwardly against a brake surface on the reel housing by centrifugal forces produced by the rotation of the spool. 
         [0003]    Centrifugal braking may have an adverse effect on casting distance. Therefore, with the development of easily adjustable brake systems, many fishermen set the brake control to “free” when pitching, which could result in backlash. 
         [0004]    It is, therefore, desirable to provide a system wherein additional braking is provided at high spool spin velocities, but not at lower speed velocities, so as to maximize casting distance and to minimize backlash under conditions of long casting when brake control adjustments are set to “free”. 
       SUMMARY OF THE INVENTION 
       [0005]    A reel of the invention has a spool mounted on a spool shaft. A brake assembly is mounted on the spool shaft. The brake assembly has a plurality of brake shoes and a plurality of speed adjust shoes and is slidably mounted on the spool shaft. A brake ring selectively engages the brake shoes to provide a braking action to the spool. Preferably, braking force from the brake shoes against the brake ring is infinitely adjustable. 
         [0006]    In a preferred embodiment, the spool has a conical surface for selectively engaging the speed adjust shoes. The brake assembly is slidably mounted on the spool shaft. The speed adjust shoes migrate outwardly to make contact with the conical surface when the spool and brake assembly are spun with sufficient velocity. When spun with sufficient velocity, the speed adjust shoes, acting against the conical surface, impart an axial force to the brake assembly for moving the brake assembly towards the brake ring. A speed adjust spring is provided for biasing the brake assembly away from the brake ring and towards the spool. The speed adjust shoes are sized so that the speed adjust shoes apply a centrifugal force against the conical surface at high rotational speeds of the spool and brake assembly, thereby causing the brake assembly to move towards the brake ring. At relatively lower rotational speeds of the spool, the speed adjust shoes cease to provide sufficient centrifugal force against the conical surface of the spool. Therefore, the speed adjust spring pushes the brake assembly away from the brake ring. 
         [0007]    The automatic adjustable spool brake system of the invention automatically adjusts braking action on the spool dependent upon the spool rotation speed in addition to an infinitive externally adjustable brake system. 
         [0008]    The result is better brake control to prevent backlash on casting and an ability to achieve better distance by reducing spool braking force when the spool rotation slows down, i.e., when the brake assembly returns to its original position by spring force. 
         [0009]    Another benefit of the invention relates to the pitching function and casting combination. During pitching, many users set the brake to permit free spin of the spool assembly. A “free” setting may result in backlash when pitching without the benefit of traditional brake control adjust. Therefore, the apparatus of the invention addresses this difficulty by controlling backlash when pitching with the brake control adjust set at “free” by providing additional braking at high spool rotation velocities. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0010]      FIG. 1  is a perspective view of the reel of the invention; 
           [0011]      FIG. 2  is an exploded view of palm side cover of the reel of  FIG. 1  showing the infinitely adjustable ACS mechanism of the reel of  FIG. 1 ; 
           [0012]      FIG. 3  is a cross-sectional view of the reel of  FIG. 1 ; 
           [0013]      FIG. 4  is an exploded view of the brake shoe assembly of the reel of  FIG. 1 ; 
           [0014]      FIG. 5  is a cross-sectional view of the reel of  FIG. 1  shown at a free position of the brake assembly and showing the brake shoe leveled; 
           [0015]      FIG. 6  is a cross-sectional view of the reel of  FIG. 1  showing the brake assembly moving forward due to spool momentum; 
           [0016]      FIG. 7  is a cross-sectional view of the reel of  FIG. 1  showing the brake ring assembly adjusted and moved forward due to momentum of the rotating spool; 
           [0017]      FIG. 8  is a cross-sectional view of the reel of  FIG. 1  showing the brake ring assembly adjusted and moved backwards due to slowing of the rotating spool. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0018]    Shown in  FIGS. 1-8  is a reel designated generally  10 . Reel  10  includes frame  12  having palm side  14  and gear side  16 . Palm side cover assembly  18  has outside surface  20  and inside surface  22 . Inside surface  22  of palm side cover assembly  18  is affixed to palm side  14  of frame  12 . Palm side cover assembly  18  defines dial orifice  24 . 
         [0019]    Crank shaft  26  ( FIG. 3 ) is rotatably mounted within frame  12 . Crank shaft  26  has a palm end  28  and a gear end  30 . Pinion gear  32  is affixed to palm end  28  of crank shaft  26 . 
         [0020]    Spool shaft ball bearing  36  is mounted in gear side  16  of frame  12  for supporting gear end  40  of spool shaft  38 . Spool shaft  38  has a gear end  40  and a palm end  42 . Pin  43  protrudes from a side wall of spool shaft  38 . Gear end  40  is supported by spool shaft bearing  36 . Spool shaft  38  defines a clip receptacle  44  ( FIGS. 6-8 ) proximate to palm end  42 . Pin  43  protrudes from spool shaft  38 . 
         [0021]    Palm side spool shaft ball bearing  45  supports palm end  42  of spool shaft  38 . Palm side ball bearing  34  is received within central member  84  of brake spool cover  82 , discussed below. 
         [0022]    Spool assembly  46  is mounted on spool shaft  38 . Spool assembly  46  defines conical surface  48  ( FIGS. 3 ,  5 ) on gear side  50  and defines a conical surface  52  on palm side  54 . 
         [0023]    Referring now primarily to  FIG. 4 , but also to  FIGS. 6-8 , shown is a brake assembly. “Brake assembly” refers to the combination of brake shoe retainer  56 , brake shoe holder  64 , brake shoes  74 , and speed adjust shoes  76 . Brake shoe retainer  56  defines central protuberance  58 . A plurality of speed adjust shoe retainers  60  are defined by central protuberance  58  of brake shoe retainer  56 . Central protuberance  58  defines an orifice for receiving spool shaft  38 . The orifice additionally defines pin slot  59  for receiving pin  43 . 
         [0024]    Brake shoe holder  64  is affixed to gear side  66  of brake shoe retainer  56  and surrounds spool shaft  38 . Brake shoe holder  64  has a central orifice  68  for receiving central protuberance  58  of brake shoe retainer  56 . Brake shoe holder  64  additionally defines a smooth gear side surface  70  (best seen in  FIG. 4 ). Brake shoe holder  64  and brake shoe retainer  56  define a plurality of brake shoe receptacles  72  therebetween. 
         [0025]    Brake shoes  74  are slidably retained within each of a plurality of brake shoe receptacles  72 . Brake shoes  74  are free to slide in a radial direction. Movement of brake shoes  74  is restricted in an axial or thrust direction by brake shoe holder  64  and brake shoe retainer  56 . A speed adjust shoe  76  is retained within each of the plurality of speed adjust shoe retainers  60  defined by the central protuberance  58  of brake shoe retainer  56 . Speed adjust shoes  76  have a surface in sliding contact with conical exterior surface  52  of palm side  54  of spool assembly  46 . Speed adjust shoe  76  additionally has a surface in sliding contact with smooth gear side surface  70  of brake shoe holder  64 . 
         [0026]    Speed adjust retainer clip  78  ( FIGS. 3 ,  5 ,  6 ) is located in clip receptacle  44  on spool shaft  38 . Speed adjust spring  80  is provided for biasing brake shoe retainer  56  towards gear side  16  of frame  12  so that speed adjust shoe  76  is pressed into a fully retracted position within brake shoe retainer  56  by palm side conical exterior surface  52  of spool assembly  46 . 
         [0027]    Brake spool cover  82  ( FIG. 2 ) is affixed to inside surface  22  of palm side cover assembly  18 . Brake spool cover  82  has a central member  84 . Central member  84  is raised above a lower surface of brake spool cover  82  by a plurality of legs  85 . 
         [0028]    Still referring to  FIG. 2 , brake ring support  88  has a central orifice  90  that receives central member  84  of brake spool cover  82 . Brake ring support  88  defines a cam follower  92  and a brake receiving area  94 . Cam follower  92  passes between the legs of brake spool cover  82  to make contact with cam surface  104  for moving brake spool cover  82  in an axial direction, depending upon the rotation of brake control dial  102 , discussed below. 
         [0029]    Continuing with reference to  FIG. 2 , brake ring  96  is located within brake receiving area  94  of brake ring support  88 . Brake ring  96  has a sloped brake shoe engaging surface  98  (see also  FIGS. 3 ,  5 - 8 ). Brake ring slider spring retainer  100  is affixed to a gear side of brake spool cover  82 . 
         [0030]    Infinitely adjustable brake control dial  102  defines cam surface  104  on gear side  106 . Cam surface  104  is received within a space defined in part by a palm side surface of central member  84  and in part by legs  85  to make contact with cam follower  92  of brake ring support  88 , which passes therethrough. A plurality of brake frame assembly springs  108  are in contact with brake ring slider spring retainer  100  and bias cam follower  92  of brake ring support  88  into contact with cam surface  104  of brake control dial  102 . 
         [0031]    By turning infinitely adjustable brake control dial  102 , a location of brake ring support  88  can be set to any position depending on the orientation of cam surfaces  104 . Brake ring support  88  is biased against cam surfaces  104  by springs  108 . The result is that the position of brake ring  96  may be infinitely adjustable with regard to brake shoe retainer  56 . 
         [0032]    The brake shoe assembly, including brake shoe retainer  56  and brake shoe holder  64 , is free to slide in an axial or thrust direction along spool shaft  38 . The axial movement results in pin  43  moving within pin slot  59 . The brake shoe retainer  56  is biased towards gear side  16  by speed adjust spring  80 . Therefore, brake shoe retainer  56  can slide forward when a thrust force from speed adjust shoes  76  is greater than the spring force from speed adjust spring  80 . When spool rotation speed slows and the axial thrust force generated by speed adjust shoes  76  diminishes, brake shoe retainer  56  then returns to its original position due to the spring force from speed adjust spring  80 . Auto adjusting speed adjust shoes  76  slide within adjust shoe retainers  60 , so speed adjust shoes  76  may extend in a radial direction for applying force to conical surface  52  of spool  46 . 
         [0033]    In greater detail, when spool assembly  46  over spins when casting, speed adjust shoes  76  move outwardly and push against conical surface  52  of spool assembly  46 . The outwardly directed force of auto speed adjust shoes  76  causes speed adjust shoes  76  to slide along conical surface  52  outwardly and in the direction of brake ring support  88 . Brake shoe retainer  56  is, therefore, moved when the axial vector force is greater than the spring force from speed adjust spring  80 . Braking force is then generated when brake shoes  74  move to engage brake ring support  88 . 
         [0034]    Referring now to the section views of  FIGS. 5-8 , it can be seen that  FIG. 5  shows reel  10  at a resting and full free position. In this position, speed adjust shoes  76  are in a fully retracted position within speed shoe retainers  60  by conical surface  52  of spool assembly  46 . Brake shoe retainer  56  is pressed towards gear side  16 , i.e., fully within conical surface  52  by speed adjust support spring  80  (see  FIG. 3 ). Brake shoes  74  are retracted within brake shoe receptacles  72  and do not make contact with sloped brake shoe engaging surface  98  of brake ring  96 . 
         [0035]      FIG. 6  shows reel  10  at a casted condition and full free position. In the position shown in  FIG. 6 , speed adjust shoes  76  are extended from speed shoe retainers  60 . Centrifugal force moves speed adjust shoes  76  outwardly. An outside surface of speed adjust shoes  76  are in contact with conical surface  52  of spool assembly  46 . Speed adjust shoes  76  are, therefore, providing an axial force component for moving brake shoe retainer  56  towards palm side  14 . Brake shoes  74  are likewise extended from brake shoe receptacles  72 , but do not make contact with sloped brake shoe engaging surface  98  of brake ring  96 . 
         [0036]      FIG. 7  shows the reel at a casted position and the infinite ACS dial  102  of reel  10  adjusted half way. In the position shown in  FIG. 7 , speed adjust shoes  76  are extended from speed shoe retainers  60 . An outside surface of speed adjust shoes  76  is in contact with conical surface  52  of spool assembly  46 . Speed adjust shoes  76  are, therefore, providing an axial force component for moving brake shoe retainer  56  toward palm side  14 . Brake shoes  74  are likewise extended from brake shoe receptacles  72  and make frictional braking contact with sloped brake shoe engaging surface  98  of brake ring  96  to provide a braking force. 
         [0037]      FIG. 8  shows the infinite ACS dial  102  of reel  10  adjusted halfway and shows reel  10  when the brake assembly is returning to its original position. The brake shoe retainer  56  is shown moving away from braking surface  98  when the speed of spool assembly  46  is reducing. In the position shown in  FIG. 8 , speed adjust shoes  76  are retracting into speed shoe retainers  60  and are not generating a sufficient axial force to overcome spring force from spring  80 . Brake shoe retainer  56  is, therefore, moving towards gear side  16 . Brake shoes  74  are moved out of contact with sloped brake shoe engaging surface  98  of brake ring  96 . Therefore, spool assembly  46  is in a relatively low-friction condition as the speed of spool assembly  46  is reducing. 
         [0038]    Thus, the present invention is well adapted to carry out the objectives and attain the ends and advantages mentioned above as well as those inherent therein. While presently preferred embodiments have been described for purposes of this disclosure, numerous changes and modifications will be apparent to those of ordinary skill in the art. Such changes and modifications are encompassed within the spirit of this invention as defined by the claims.