Abstract:
A heavy duty fishing reel or trolling reel is disclosed having improvements related to a unitary end assembly, a duel drag system, a preset adjust mechanism and anti-bind improvements.

Description:
FIELD OF THE INVENTION 
   The invention relates to heavy duty fishing reels. In particular, the invention relates to improvements for trolling reels including end assembly, drag system, preset adjust and anti-bind improvements. 
   BACKGROUND OF THE INVENTION 
   Saltwater fishing tackle is typically substantial to withstand the stresses imposed by landing large fish. Heavy duty components are typically employed, such as a ceramic drag system, brass alloy gears, ceramic drag discs, and a protective finish to guard against salt water corrosion. 
   Improved functionality and durability are desirable for heavy duty saltwater reels. 
   SUMMARY OF THE INVENTION 
   A heavy duty trolling reel is disclosed having improved features including an improved pre-set adjust, an attractive and functional unitary end that performs various interface functions, a double drag mechanism, a floating gear system to prevent binding of mechanisms, and a quickly adjustable two-speed mechanism. 
   An annular pre-set knob is provided with a knurled exterior surface for gripping by a user. The annular pre-set knob may be depressed by a user to engage pre-set knob pins extending from the pre-set knob with an orifice defined by a face of a first pre-set gear. Therefore, first pre-set gear may be rotated by depressing and rotating the annular pre-set knob. The first pre-set gear, in turn, engages a pre-set idle gear for rotating a second pre-set gear, which is threadably received on a spool shaft. Rotation of second pre-set gear moves second pre-set gear longitudinally along the threaded portion of the spool shaft for pressing a left drag plate assembly against a smooth portion of the bait click ratchet plate. A spool assembly and attached second drag washer are also pressed into contact with a right drag plate assembly, thereby facilitating frictional resistance on both sides of the spool, i.e., facilitating “double drag.” 
   A clamp nut is located inside of the annual pre-set knob and is substantially flush with an exterior of the annular pre-set knob. The clamp nut has an interior portion that threadably engages an end of the spool shaft. The clamp nut has an exterior side that defines a shaped recessed area for receiving a hinged retractable handle. The hinged retractable handle is preferably flush with an exterior of the clamp nut when the hinged retractable handle is in a closed position. By unfolding the hinged retractable handle to an open position, a user may use the handle to rotate the clamp nut to unscrew the clamp nut off of the end of a spool shaft, thereby enabling the reel to be disassembled, i.e., enabling a gear side cover to be removed, thereby exposing the interior of the reel. 
   A low speed pinion gear is mounted on the spool shaft and is received within a right shaped receptacle of the right drag plate assembly. A high speed pinion gear is also mounted on the spool shaft and is sized to be received within the low speed pinion gear. The high speed pinion gear is received within the right shaped receptacle of the right drag plate assembly. The high speed pinion gear has a cylindrical extension on a right end. The high speed pinion gear has an inner diameter sized to allow for a gap of preferably 0.2 mm between the inner diameter of the high speed pinion gear and the spool shaft. A ball bearing assembly surrounds the cylindrical extension of the high speed pinion gear. The ball bearing tightly engages a bearing pocket on an outer diameter of the ball bearing and tightly engages the high speed pinion gear on an inner diameter of the ball bearing. The bearing pocket is provided for receiving the ball bearing. The bearing pocket is tightly received within a central orifice of the gear side cover. The bearing pocket tightly engages the spool shaft on an inner diameter and tightly engages the gear side cover on an outer diameter. The gap between selected components or “floating gear system” reduces the chances for seizing of the mechanism over the life of the reel. 
   A low speed drive gear surrounds the crank shaft. The low speed drive gear is located to selectively engage a low speed pinion gear. The low speed drive gear has a shaped receptacle on the left side for receiving the shaped exterior of a gear shifting plate. A first spacer is provided for locating on an internal end of the crank shaft. The first spacer has a protuberance for locating in a longitudinal notch of the crank shaft. A second spacer surrounds the crank shaft. A crank shaft nut is threadably received on an internal end of the crank shaft. A gear shifting plate spring is received in shaped exterior end of the crank shaft. A shifting pin is received within the shaped exterior of the crank shaft. A shifting pin is biased exteriorly by a gear shifting plate spring. The shifting pin is threadably engaged with the gear shifting plate, which acts to bias the gear shifting plate and the attached low speed drive gear in an exterior direction for disengaging the low speed drive gear from the low speed pinion gear. A bushing is located adjacent a shifting pin. A gear shifting spring is located adjacent the bushing. By depressing a low speed shift button on the crank handle assembly, either the high speed drive gear or the low speed drive gear will interface with the corresponding high speed or low speed pinion gear, as desired. The two speed system described above allows for a user to reel in line in a low gear mode, suitable for reeling in large fish, or a high gear mode, suitable for reeling in fishing line at an increased speed. 
   As can be seen from the above description, the reel of the invention is provided with improvements that improve functionality and durability. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1A-C  is an exploded view of the trolling reel of the invention; 
       FIG. 2  is a front elevation view of the trolling reel of  FIG. 1 ; 
       FIG. 3  is a rear elevation view of the trolling reel of  FIG. 1 ; 
       FIG. 4  is a top plan view of the trolling reel of  FIG. 1 ; 
       FIG. 5  is a right side elevation view of the trolling reel of  FIG. 1 ; and 
       FIG. 6  is a left side elevation view of the trolling reel of  FIG. 1 . 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   A trolling reel  10  includes a frame assembly  12  having a substantially open end  14  and a substantially closed end  16 . Closed end  16  defines a central orifice  18 . Substantially closed end  16  defines a cavity  20  on an inside surface. Substantially open end  14  is provided with a mating surface  22 . 
   A gear side cover  26  ( FIGS. 1C , and  2 - 5 ) is removably affixed to substantially open end  14 . Gear side cover  26  defines a central orifice  28  and a crank shaft orifice  30  therein. 
   An annular pre-set knob  50  is located proximate to said central orifice  18  of substantially closed end  16  of frame assembly  12 . Pre-set knob  50  preferably is provided with a knurled exterior surface for gripping by a user. A pre-set gear washer is located adjacent an interior surface of annular pre-set knob  50 . A first pre-set gear  54  ( FIG. 1 ) is received within central orifice  18  of substantially closed end  16  of frame assembly  12  and is located behind annular pre-set knob  50 . First pre-set gear  54  has external gear teeth and defines a plurality of orifices around a face of first pre-set gear  54 . A pre-set gear washer is located adjacent to an interior side of first pre-set gear  54 . A plurality of pre-set knob springs  58  is located between annular pre-set knob  50  and first pre-set gear  54  for biasing the annular pre-set knob  50  away from the first pre-set gear  54 . Three pre-set knob pins  60  extend rearwardly from first pre-set gear  54 . Pre-set knob pins  60  are provided for selective engagement with one of the plurality of orifices around the face of first pre-set gear  54 . Pre-set knob pins  60  engage the orifices of first pre-set gear  54  when pre-set knob  50  is depressed, thereby compressing pre-set knob springs  58 . 
   Clamp nut  61  ( FIGS. 1A and 6 ) is received in the central orifice  18  of substantially closed end  16  of frame assembly  12  inside of annular pre-set knob  50 . Clamp nut  61  has an interior end and an exterior end. The interior end of clamp nut  61  defines an internally threaded extension  63 . After installation, the exterior end of clamp nut  61  is visible to a user (see  FIG. 6 ). Clamp nut retainer  62  secures the clamp nut washer, pre-set knob  50 , pre-set knob spring  58 , the second pre-set gear washer, first pre-set gear  54 , first pre-set gear washer, and a clamp nut washer onto internally threaded extension  63  of clamp nut  61 . Clamp nut  61  is provided with a pivoting handle  68  that may be extended for use by a user or may be retracted into a shaped receptacle to create a flush exterior. Pivoting handle  68  is provided to allow a user to rotate clamp nut  61 . 
   A pre-set idle gear  80  engages the external teeth of first pre-set gear  54 . Pre-set idle gear  80  is driven by first pre-set gear  54  for driving second pre-set gear  130  ( FIG. 1B ). A left end of pre-set idle gear  80  defines a pair of receptacles. Pre-set idle gear click plate  82  is located in cavity  20  defined by the inside surface of substantially closed end  16  of frame assembly  12 . A portion of a bottom of cavity  20  is open to allow for interface of first pre-set gear  54  and pre-set idle gear  80 . Pre-set idle gear click plate  82  is adjacent to a left end of pre-set idle gear  80 . A spring biased pre-set idle gear click pin  84  is located in the receptacle of pre-set idle gear  80 . The pre-set idle gear click pin  84  is provided for moving with the pre-set idle gear  80  and for engaging pre-set idle click plate  82 . Pre-set idle gear screw  86  is provided for securing the pre-set idle gear  80  to the inside surface of the substantially closed end  16  of frame assembly  12 . 
   A spool shaft  90  ( FIG. 1C ) has a first end  92  that is threadably received within internally threaded extension  63  of clamp nut  61 . Spool shaft  90  additionally has a second end  94  affixed to spool shaft lever or handle  96  that is external gear side cover  26 . 
   A bait click cam  110 ,  111  ( FIG. 1A ) is secured to an inside surface of substantially closed end  16  of frame assembly  12 . A bait click pawl  112  is in communication with bait click cam  110  wherein bait click cam  110  selectively forces the bait click pawl  112  into communication with a bait click ratchet  152  ( FIG. 1B ). A bait click spring  114  is provided for biasing bait click pawl  112  toward bait click ratchet  152 . A bait click lever  116  protrudes from the body of frame assembly  12  to allow a user to manually rotate bait click cam  110 ,  111 . 
   Second pre-set gear  130  is threadably received on spool shaft  90 . Second pre-set gear  130  has external gear teeth that engage pre-set idle gear  80 . Second pre-set gear  130  has an inwardly extending stem  132 . Rotation of second pre-set gear  130  moves second pre-set gear  130  longitudinally along spool shaft  90 . Drag stopper plate assembly  134  is located on stem  132  of second pre-set gear  130 . A drag stopper plate washer is provided between second pre-set gear  130  and drag stopper plate assembly  134 . A left drag plate assembly  138  is located adjacent to an internal face of second pre-set gear  130 . Left drag plate assembly  138  surrounds stem  132  of second pre-set gear  130 . Left drag plate assembly  138  has a raised portion  140  on a right face of left drag plate assembly  138  and a friction pad that surrounds said raised portion  140 . The raised portion  140  defines a recessed area. A first pressure relief spring  141  surrounds spool shaft  90  and is received in the recessed area of raised portion  140  of left drag plate assembly  138 . E-clip  142  is provided for affixing the left drag plate assembly  138  to stem  132  of second pre-set gear  130 . 
   A spool assembly  150  is located on spool shaft  90 . Spool assembly  150  has a left end and a right end. Base click ratchet plate  152  is secured to a left end of the spool assembly  150 . Base click ratchet plate  152  has a smooth inner portion for rubbing against the friction pad on left drag plate assembly  138 . First ball bearing assembly  154  surrounds spool shaft  90  and is located in the recessed area defined by a left end of spool assembly  150 . 
   A second ball bearing assembly  156  surrounds spool shaft  90  and is located in a recessed area on the right end of spool assembly  150 . A second pressure relief spring  158  surrounds spool shaft  90  adjacent to second ball bearing  156 . A second drag washer  164  is affixed to the right side of spool  150  with a plurality of screws. 
   Right drag plate assembly  180  is provided with a left receptacle and a right shaped receptacle. Third ball bearing assembly  182  surrounds spool shaft  90  and is received within a receptacle of the right drag plate assembly  180 . Third ball bearing assembly  182  is tightly received within a receptacle defined by right drag plate assembly  180 . Bushing  184  is tightly received on an inner diameter of third ball bearing  182 . Bushing  184  is installed in tight engagement with spool shaft  90 . 
   A high speed pinion gear  192  surrounds spool shaft  90  and has a sleeve portion with a shaped end. The shaped end of high speed pinion gear  192  is received within a shaped receptacle of right drag plate assembly  180 . Low speed pinion gear  190  is received on the sleeve portion of high speed pinion gear  192 . High speed pinion gear  192  has an inner diameter sized to allow for a gap of preferably 0.2 mm between the inner diameter of the high speed pinion gear  192  and spool shaft  90 . A fourth ball bearing  196  surrounds a cylindrical extension  194  of high speed pinion gear  192 . Fourth ball bearing  196  tightly engages bearing pocket  198  on an outer diameter and tightly engages cylindrical extension  194  of high speed pinion gear  192  on an inner diameter. Bearing pocket  198  receives fourth ball bearing  196 . Bearing pocket  198  tightly engages spool shaft  90  on an inner diameter and tightly engages gear side cover  26  on an outer diameter. 
   Four drag spring washers  210  surround spool shaft  90 . Drag spring washers  210  are adjacent a left side of bearing pocket  198 . Second drag cam  212  surrounds spool shaft  90  and is adjacent to a right end of right most drag spring washer  210 . First drag cam  214  surrounds spool shaft  90  and is adjacent to a right end of second drag cam  212 . First drag cam  214  and second drag cam  212  are provided for cooperatively expanding or contracting, depending upon the relative rotational position of second drag cam  212  with respect to first drag cam  214 . First drag cam  214  has a shaped right end for engagement with a shaped right end of handle  96  ( FIG. 1C ) that is affixed to a right end of spool shaft assembly  90 . 
   Anti-reverse pawl  220  ( FIG. 1C ) is pivotally affixed to an inside surface of gear side cover  26  for engaging low speed pinion gear  190  ( FIG. 1B ). An anti-reverse spring holder  222  is provided with a radial cavity. Anti-reverse spring  224  is located within said radial opening of said anti-reverse spring holder  222 . An anti-reverse spring post  226  surrounds anti-reverse spring  224  and is slidably received within radial opening of the anti-reverse spring holder  222 . 
   Crank shaft  230  ( FIG. 1B ) passes through crank shaft orifice  30  ( FIG. 1C ) of gear side cover  26 . Crank shaft  230  has a threaded internal end  232  defining a longitudinal notch  234 . Crank shaft  230  additionally has a shaped exterior end  236 . 
   High speed drive gear  240  is mounted on crank shaft  230  and is located to selectively engage the high speed pinion gear  192 . Gear shifting plate  242  surrounds crank shaft  230  and is located adjacent to a right side of the high speed gear drive  240 . Gear shifting plate  242  has a shaped exterior and defines a threaded orifice. 
   Low speed drive gear  244  surrounds crank shaft  230  and is located to selectively engage low speed pinion gear  190 . Low speed drive gear  244  has a shaped receptacle for receiving the shaped exterior of gear shifting plate  242 . First spacer  246  is provided for locating on an internal end  232  of crank shaft  230 . First spacer  246  has a protuberance for locating in longitudinal notch  234  of crank shaft  230 . Second spacer  247  surrounds crank shaft  230 . A crank shaft nut  248  is threadably received on internal end  232  of crank shaft  230 . A gear shifting plate spring  250  is received in shaped exterior end  236  of crank shaft  230 . A shifting pin  252  is received within the shaped exterior  236  of crank shaft  230 . Shifting pin  252  is biased exteriorly by gear shifting plate spring  250 . Shifting pin  252  is threadably engaged with gear shifting plate  242 , which acts to bias gear shifting plate  242  and the attached low speed drive gear  244  an in exterior axial direction for disengaging low speed drive gear  244  from the low speed pinion gear  190 . Bushing  254  is located adjacent shifting pin  252 . Gear shifting spring  256  is located adjacent bushing  254 . 
   Curved quadrant  270  ( FIG. 1C ) is affixed to an external side of gear side cover  26 . Quadrant  270  has a first orifice proximate a first end and a second orifice proximate a second end. Quadrant spacers  272  are adjacent to the orifices of quadrant  270 . Quadrant anchors  274  are adjacent to the quadrant spacers  272  for affixing quadrant  270  to gear side cover assembly  26 . 
   A riser defines crank shaft orifice  30  on gear side cover  26 . Handle assembly  280  defines an orifice for engaging the shaped exterior end  236  of crank shaft  230 . Handle collar  282  is adjacent an exterior end of handle  280 . Handle collar  282  defines an outwardly facing receptacle. Button screw  284  is received within the receptacle of the handle collar  282 . Button screw  284  has an outwardly facing extension. Handle nut  286  is provided for threadably affixing handle  280  to crank shaft  230 . Handle nut  286  has a central through-hole. Handle nut retainer  288  has a shaped interior orifice for surrounding and engaging handle nut  286 . Handle nut retainer  288  further has a button receptacle and a spring backstop defining an interior surface. 
   High speed shift button assembly  290  is located in the button receptacle of the handle nut retainer  288 . Shifting button spring  292  is located adjacent to the spring backstop of handle nut retainer  288  for biasing a high speed shift button assembly  290  radially outward from a longitudinal axis of crank shaft  230 . Button cover  294  is provided for securing the high speed shift button assembly  290  to the handle nut retainer  288 . Handle nut cap  296  defines a central orifice and is secured to handle assembly  280  and covers button screw  284 , handle nut  286 , handle nut retainer  288 , shifting button spring  292 , and button cover  294 . 
   A low speed shift button  300  is inserted within the central orifice of handle nut cap  296  and through button cover  294 , handle nut retainer  288 , handle nut  286  and through crank shaft orifice  30  of gear side cover  26 . Low speed shift button  300  has a stem  302  having a planar surface defined thereon for selective locking engagement by the high speed shifting button assembly  290 . High speed shift button assembly  290  has a terminal end for engaging shift button spring  292  which biases the high speed shift button assembly  290  in an exterior direction, and for depressing shifting pin  252  which compresses gear shifting plate spring  250 . 
   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.