Patent Publication Number: US-7722417-B2

Title: Trolling motor mount with mono main arm

Description:
BACKGROUND 
     The present invention relates to trolling motors, and more particularly to a mounting device for securing a trolling motor to a watercraft. 
     Watercraft, especially fishing boats, often employ a trolling motor. The trolling motor may be used to maneuver or to hold the watercraft in position while the vessel operator fishes. Trolling motors may be interconnected with the watercraft via a mount secured to the bow of the vessel. Often conventional bow mounts include a base plate and several movable arms, which are configured to retain the trolling motor and interlock with the base plate. The movable arms are generally configured to pivot between a stowed position, where the trolling motor is on-board the vessel, and a deployed operation position, where the trolling motor extends into the water. 
     Although many conventional pivoting bow mounts effectively stow and deploy trolling motors, the durability of the multiple pivoting joints used by the movable arms is limited. After a period of use, the joints of the bow mount may loosen and begin to develop play. This joint play causes the bow mount to rattle or make other unpleasant noises during the operation of the watercraft. With many conventional bow mounts, removing the trolling motor from or attaching the trolling motor to the mount also presents some inconvenience for the operator. This process is inconvenient because the conventional bow mount&#39;s actuation rope (which is used to lift and rotate the bow mount&#39;s movable arms from the stowed or deployed position) runs through the mount&#39;s movable arms and through the portion of the mount that is configured to couple with the trolling motor. In this configuration, the actuation rope must be untied from the interior of the bow mount&#39;s movable arms before the portion of the mount that couples with the trolling motor can be removed from the remainder of the mount. 
     SUMMARY 
     In one aspect, a mount for securing a trolling motor to a watercraft has a base, a main arm, a motor coupling, and a linkage. The motor coupling is configured to rotatably retain the trolling motor. The main arm is pivotally coupled to the base. The linkage is pivotally coupled with the base and the main arm and extends within the main arm to contact the motor coupling for actuating rotation of the motor coupling between a first position when the main arm is in a stowed position, and a second position when the main arm is in a deployed position. 
     In another aspect, an apparatus for coupling a trolling motor to a mount includes a motor coupling assembly and a linkage assembly. The motor coupling assembly includes a sleeve configured to couple to the trolling motor. The linkage assembly is configured to interconnect to the mount. The motor coupling assembly and the linkage assembly have male and female interlocking surface profiles. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1A  is a perspective view of an exemplary embodiment of a mount shown in a deployed position securing a trolling motor to the bow of a watercraft. 
         FIG. 1B  is a perspective view of the mount from  FIG. 1A  securing the trolling motor to the bow of a watercraft in a stowed position with base side plates removed. 
         FIG. 2  is an exploded view of the mount from  FIG. 1A , viewed from the rear. 
         FIG. 3  is an exploded view of the base assembly from  FIG. 2 , viewed from the front. 
         FIG. 4A  is a perspective view of the base extrusion from  FIG. 2 , viewed from the front. 
         FIG. 4B  is a top view of the base extrusion from  FIG. 4A . 
         FIG. 4C  is a side view of the base extrusion from  FIG. 4A . 
         FIG. 5A  is a top view of the motor ramp from  FIG. 2 . 
         FIG. 5B  is a side view of the motor ramp from  FIG. 5A . 
         FIG. 6  is an exploded view of the arm assembly from  FIG. 2 , viewed from the front. 
         FIG. 7A  is a perspective view of the main arm from  FIG. 2 , viewed from the front. 
         FIG. 7B  is a side view of the main arm from  FIG. 7A . 
         FIG. 7C  is a bottom view of the main arm from  FIG. 7A . 
         FIG. 7D  is an front end view of the main arm from  FIG. 7A . 
         FIG. 8A  is a perspective view of the yoke from  FIG. 2 , viewed from the front. 
         FIG. 8B  is a side view of the yoke from  FIG. 8A . 
         FIG. 8C  is a bottom view of the yoke from  FIG. 8A . 
         FIG. 8D  is a front view of the yoke from  FIG. 8A . 
         FIG. 9A  is a perspective view of the rear pivot bracket from  FIG. 2 , viewed from the rear. 
         FIG. 9B  is a side view of the rear pivot bracket from  FIG. 9A . 
         FIG. 9C  is a rear view of the rear pivot bracket from  FIG. 9A . 
         FIG. 10A  is a side view of the rear pivot bushing from  FIG. 2 . 
         FIG. 10B  is a sectional view of the rear pivot bushing from  FIG. 10A . 
         FIG. 11A  is a side view of the leaf spring from  FIG. 2 . 
         FIG. 11B  is a bottom view of the leaf spring from  FIG. 11A . 
         FIG. 12A  is a perspective view of the rope guide from  FIG. 2 , viewed from the side. 
         FIG. 12B  is a side sectional view of the rope guide from  FIG. 12A . 
         FIG. 13A  is a side view of the safety latch from  FIG. 2 . 
         FIG. 13B  is a front end view of the safety latch from  FIG. 13A . 
         FIG. 14A  is a perspective view of the rear latch bracket from  FIG. 2 , viewed from the front. 
         FIG. 14B  is a side view of the rear latch bracket from  FIG. 14A . 
         FIG. 15A  is a perspective view of the latch strap bracket from  FIG. 2 , viewed from the front. 
         FIG. 15B  is a top view of the latch strap bracket from  FIG. 15A . 
         FIG. 15C  is a side view of the latch strap bracket from  FIG. 15A . 
         FIG. 16A  is a perspective view of the latch bar from  FIG. 2 , viewed from the top front. 
         FIG. 16B  is a perspective view of the latch bar from  FIG. 16B , viewed from the bottom rear. 
         FIG. 17A  is a top view of the bias mechanism from  FIG. 2 . 
         FIG. 17B  is a side view of the bias mechanism from  FIG. 17A . 
         FIG. 18  is an exploded view of the motor coupling assembly from  FIG. 2 , viewed from the rear. 
         FIG. 19  is a view of the mount from  FIG. 1A  with the motor coupling assembly, the washer, and the fastener removed from an interlocking position with the mount. 
         FIG. 20  is a perspective view of the motor coupling assembly from  FIG. 19  in an interlocking position with the linkage assembly from  FIG. 19 , viewed from the rear. 
         FIG. 21A  is a perspective view of the mount from  FIG. 1A  with the main arm and the base assembly suppressed to show the linkage assembly, the motion control device, and the latch system, viewed from the side. 
         FIG. 21B  is a perspective view of the mount from  FIG. 1B  with the main arm and the base assembly suppressed to show the linkage assembly, the motion control device, and the latch system, viewed from the side. 
         FIG. 22  is an elevated perspective view of the mount from  FIG. 1A , viewed from the rear. 
         FIG. 23  is a perspective view of the mount shown between the deployed position and the stowed position, viewed from the side. 
     
    
    
     DETAILED DESCRIPTION 
     1. Overview of the Assembly  10   
       FIGS. 1A and 1B  show an embodiment of a trolling motor assembly  10 , which is secured to the gunnels or other suitable surface(s) of a watercraft  12 . The trolling motor assembly  10  includes a rope  14 , a trolling motor  16 , and a mount  18 . The trolling motor  16  includes a head  20 , a shaft  22 , a propulsion unit  24  and a propeller  26 . The mount  18  includes a base assembly  28 , a main arm assembly  30 , and a motor coupling assembly  32 . 
     In  FIG. 1A , the trolling motor assembly  10  is shown in the deployed position with the trolling motor  16  entering the water. In  FIG. 1B , the trolling motor assembly  10  is shown in the stowed position with the trolling motor  16  retained aboard the watercraft  12 , generally parallel with the gunnels of the watercraft  12 . In both positions, the trolling motor  16  is secured by the mount  18  to the watercraft  12 . 
     In  FIGS. 1A and 1B , the base assembly  28  secures the remainder of the mount  18  and the trolling motor  16  to the watercraft  12 . The rear of the main arm assembly  30  pivotally couples with the rear of the base assembly  28 . The front of the main arm assembly  28  pivotally couples with the motor coupling assembly  32 , which rotatably couples with the shaft  22  of the trolling motor  16 . The main arm assembly  30  is adapted to rotate relative to the base assembly  28  between the stowed position and the deployed position. The main arm assembly  30  is configured to releasably latch to the base assembly  28  in the stowed position and in the deployed position. In one embodiment, the rope  14  enters the interior of the main arm assembly  30  and is used by the operator to unlatch the main arm assembly  30  from the base assembly  30  in the stowed position and in the deployed position. In another embodiment, the rope  14  is used to rotate the main arm assembly  30  between the stowed position and the deployed position. Simultaneous with the rotation of the main arm assembly  30  from the stowed position to the deployed position, the main arm assembly  30  is adapted to rotate the motor coupling assembly  32  from a first generally vertical position to a second generally horizontal position. The pivotal rotation of the motor coupling assembly  32  allows the trolling motor  16  to be disposed generally vertically in the water for operational use in deployed position, and allows the trolling motor  16  to be disposed generally horizontal to the gunnels for “non-use” in the stowed position. 
     In the deployed position illustrated in  FIG. 1A , the trolling motor assembly  10  operates to control the velocity and direction of the watercraft  12 . The watercraft  12  may be any make, model, or size; and may be a recreational or commercial vessel. To drive the watercraft  12 , the propulsion unit  24  must be positioned below the surface of the water. The trolling motor  16  exerts mechanical propulsion by converting electrical current into thrust of the propeller  26  while the propulsion unit  24  is in the water. The shaft  22  is coupled with the mount  18  and the mount  18  is secured to a surface of the watercraft  12 . The interconnected components allow the propulsion unit  24  to transfer the thrust of the propeller  26  to the watercraft  12 . The trolling motor  16  (and watercraft  12 ) may be directionally controlled by the operator via a steering mechanism (such as a foot pedal or remote control) or by a handle on the head  20 . 
     2. The Exploded Assembly  18   
       FIG. 2  shows an exploded view of an embodiment of the mount  18 , viewed from the rear. The base assembly  28  is comprised of a base extrusion  34 , a motor ramp  36 , side plate supports  38 , and side plates  40 . The base extrusion  34  includes a base plate  42 , and side walls  44 . 
     The main arm assembly  30  includes a main arm  46 , a rear pivot mechanism  48 , a linkage assembly  50 , a latch system  52 , and a motion control device  54 . The main arm  46  is comprised of a bottom wall  56 , a top wall  58 , side walls  60 , rear pivot mechanism apertures  62 , and lower front apertures  64 . The rear pivot mechanism  48  includes a yoke  66 , rear pivot brackets  68 , rear pivot bushings  70 , a rear pivot pin  72 , and fasteners  74 . The linkage assembly  50  includes a leaf spring  76 , bushings  77 , a leaf spring stop  78 , an upper pin  80 , front side links  82 , linkage projections  84 , bushings  86 , a rope guide  88 , a rope hole  90 , a lower pin  92 , a torsion spring  94 , a safety latch  96 , and a washer  98 . The latch system  52  includes a rear latch assembly  100 , latch straps  101 , and a front latch assembly  102 . The rear latch assembly  100  includes a rear latch bracket  104 , a pivot pin  106 , e-clips  108 , and extension springs  110 . The front latch assembly  102  is comprised of a latch strap bracket  112  and a latch bar  114 . The motion control device  54  includes a bias mechanism  116 , a rear knurled pin  118 , a front pivot pin  120 , and fasteners  122 . 
     The motor coupling assembly  32  includes an upper cover  124 , an upper bushing  126 , an upper sleeve  128 , a spring  130 , a lower sleeve  132 , a lower bushing  134 , a lower cover  136  and a fastener  138 . The upper cover  124  includes an orifice  140 , recesses  142 , and tracks  144 . 
     A. Overview of the Exploded Assembly  18   
     In  FIG. 2 , the base assembly  28  extends symmetrically from a front portion to a rear portion, and is adapted to be secured to a surface. The rear portion of the base assembly  28  pivotally couples with the main arm  46  via the rear pivot mechanism  48 . The open frame rigid main arm  46  extends from a rear portion coupled to the base assembly  28  to a front portion. The linkage assembly  50  is disposed adjacent to (and is pivotally coupled with) the front portion of the main arm  46 , and extends through the main arm  46  to pivotally couple to the rear pivot mechanism  48 . The linkage assembly  50  and the motor coupling assembly  32  are adapted to removably interconnect. The latch system  52  is disposed inside the frame of the main arm  46  and interconnects to the rear portion of the main arm  46 . The latch system  52  extends within the main arm  46  from the rear portion to the front portion where it engages the linkage assembly  50 . The main arm  46  is adapted to allow the front portion of the latch system  52  to releasably engage the base assembly  28  in the deployed position, and is adapted to allow the rear portion of the latch system  52  to releasably engage the rear pivot mechanism  48  in the stowed position. The motion control device  54  is disposed within the frame of the main arm  46 , and pivotally couples with the main arm  46  and the rear pivot mechanism  48 . 
     In the stowed position, the main arm  46  cantilevers rearward from the rear portion of the base assembly  28 . The linkage assembly  50  holds the motor coupling assembly  32  in a generally vertical position so that the trolling motor  16  is disposed generally horizontal to the gunnels. The latch system  52  releasably engages the rear pivot mechanism  48 . 
     Between the stowed position and the deployed position, the main arm  46  pivotally rotates relative to the base assembly  28  on the rear pivot mechanism  48 . The linkage assembly  50  actuates pivotal rotation of the motor coupling assembly  32  about the pivot coupling between the main arm  46  and the linkage assembly  50 . The linkage assembly  50  pivotally rotates the motor coupling assembly  32  from the generally vertical position when in the stowed position, to a generally horizontal position in the deployed position. The latch system  52  is actuated out of engagement with the base assembly  28  or the rear pivot mechanism  48 . The motion control device  54  assists, impedes, or biases the movement of the main arm  46  between the stowed position and the deployed position. The motion control device  54  actuates rotation of a portion of the rear pivot mechanism  48 . 
     In the deployed position, the main arm  46  is received in the U-shaped channel of the base assembly  28 . The linkage assembly  50  holds the motor coupling assembly  32  in a generally horizontal position. The latch system  52  releasably engages the front portion of the base assembly  28 . 
     B. Overview of the Exploded Base Assembly  28   
     In  FIG. 2 , the base extrusion  34  is a U-shaped channel adapted to be secured to the surface(s) of the watercraft  12 . The motor ramp  36  is spade shaped interconnects to the front portion of the base extrusion  34  in a cantilevered fashion. The sides of the base extrusion  34  are adapted to secure to the side plate supports  38  and side plates  40 , which extend along the sides of the base extrusion  34  from the front to the rear. The side walls  44  of the base extrusion  34  extend generally vertically from the base plate  42  and are adapted to receive the main arm  46  between them when the main arm  46  is in the deployed position. The rear pivot mechanism  48  secures to the rear portion of the side walls  44 . 
     C. Overview of the Exploded Main Arm  46   
     In  FIG. 2 , the bottom wall  56 , side walls  60  and top wall  60  interconnect to form the open frame of the main arm  46 . The walls  56 ,  58 ,  60  extend from the rear portion of the main arm  46  to the front portion. The rear portion of the side walls  60  are adapted to extend further rearward than the bottom wall  56  or the top wall  60 . This cantilevered rear portion is adapted with rear pivot mechanism apertures  62 , which allow the main arm  46  to rotatably receive the rear pivot mechanism  48 . The lower front apertures  64  rotatably receive the linkage assembly  50 . 
     D. Overview of the Exploded Rear Pivot Mechanism  48   
       FIG. 2  shows the major components of the rear pivot mechanism  48  including the yoke  66 . The yoke  66  is symmetrically disposed between the side walls  44  toward the rear portion of the base extrusion  34 . The yoke  66  couples with the motion control device  54 . The yoke  66  is adapted to receive a hub portion of the rear pivot brackets  68  and to pivotally rotate on this portion. The rear pivot bushings  70  interface with the rear pivot brackets  68  and with the edge of the rear pivot apertures  62 . The rear pivot brackets  68  have triangular rearward projections adapted to receive the rear pivot pin  72 . The fasteners  74  fix the rear pivot brackets  68  to the side walls  44  of the base extrusion  34 . 
     E. Overview of the Exploded Linkage Assembly  50   
     In  FIG. 2 , the leaf spring  76  is adapted to receive the bushings  77 , which pivotally couple the leaf spring  76  to the rear pivot pin  72 . The leaf spring  76  extends through the interior of the main arm  46  from the rear end to the front end. In one embodiment, the central portion of the leaf spring  76  engages the leaf spring stop  78  when the main arm  46  is in the stowed position. The front portion of the leaf spring  76  is adapted to receive the bushings  77 , which pivotally couple the leaf spring  76  to the upper pin  80 . 
     The ends of the upper pin  80  extend into the front side links  82 . The linkage projections  84  on the outer side surface of the front side links  82  are adapted to interface and connect the motor coupling assembly  32  to the linkage assembly  50 . The bushings  86  receive the upper pin  80  and space the front side links  82  from the rope guide  88 . The rope guide  88  rotatably mounts to the upper pin  80  to either side of the leaf spring  76  and is adapted to receive the rope  14  via the rope hole  90 . 
     The front side links  82  and the rope guide  88  extend downward and forward to interconnect to the lower pin  92 . The lower pin  92  is received by the lower front apertures  64  of the main arm  46 . The lower pin  92  pivotally couples the linkage assembly  50  to the main arm  46 . In the front interior portion of the main arm  46 , the torsion spring  94 , safety latch  96  and washer  98  are configured to receive the lower pin  92 . The torsion spring  94  is configured to engage the lower portion of the rope guide  88  and the safety latch  96 . 
     F. Overview of the Exploded Latch System  52   
     In  FIG. 2 , the latch system  52  is disposed within the main arm  46 . The rear latch assembly  100  is disposed toward the rear portion of the main arm  46 . The rear latch assembly  100  pivotally interconnects with the latch straps  101 , which extend forward to pivotally interconnect with the front latch assembly  102 . More specifically, the upper portion of the rear latch bracket  104  pivotally couples with the latch straps  101 . The lower portion the rear latch bracket  104  pivotally couples to the main arm  46  via the pivot pin  106 . The e-clips  108  are disposed on the pivot pin  106  interfacing the rear latch bracket  104 . The springs  110  interconnect the latch bracket  104  to the bottom surface  56  of the main arm  46 . 
     The latch straps  101  pivotally couple to the latch strap bracket  112 . The latch strap bracket  112  is configured to slottedly receive the lower pin  92  at the front portion of the main arm  46 . The latch strap bracket  112  is adapted to receive the rope  14 , which enters the front interior portion of the main arm  46  through the rope hole  90  in the rope guide  88 . The latch strap bracket  112  is adapted to securely receive and interconnect with the latch bar  114 , which extends symmetrically through the latch strap bracket  112  and the side walls  60  to releasably engage the front portion of the base extrusion  34  when the main arm  46  is in the deployed position. 
     G. Overview of the Exploded Motion Control Device  54   
       FIG. 2  illustrates the major components of the motion control device  40  including the bias mechanism  116 , which extends into the main arm  46  from the rear. The rear and front portions of the bias mechanism  116  are adapted to pivotally couple with the rear knurled pin  118  and the front pivot pin  120 . The rear knurled pin  118  couples the bias mechanism  116  to the yoke  66 . The front pivot pin  120  extends generally horizontally between the side walls  60  of the main arm  46  and couples the bias mechanism  116  to the main arm  46 . In one embodiment, the ends of the front pivot pin  120  may be treaded to securely receive fasteners  122 , which extend through the side walls  60 . 
     H. Overview of the Exploded Motor Coupling Assembly  32   
     In  FIG. 2 , the upper cover  124  extends over and interfaces with the upper bushing  126 , and extends around and over a portion of the upper sleeve  128 . The upper sleeve  128  rotatably interfaces with the upper bushing  126  and the spring  130 . The spring  130  interfaces with the lower sleeve  132 . The lower sleeve  132  rotatably interfaces with the spring  130  and the lower bushing  134  and extends through the lower cover  136 . The lower cover  136  interconnects with the upper cover  124 . In one embodiment, the fastener  138  removably secures the motor coupling assembly  32  to the linkage assembly  50 . The sleeves  128 ,  132  may be adapted to rotatably interface with and couple to the shaft  22  of the trolling motor  16 , which is inserted into the interior of the motor coupling assembly  32  through an orifice  140  in the upper cover  124 . In another embodiment of the motor coupling assembly  32 , the upper cover  124  may include the recesses  142  and/or the tracks  144 , which are adapted to interface with and secure the motor coupling assembly  32  to the front side links  82 . 
     3. The Base Assembly  28   
       FIG. 3  shows an exploded front perspective view of an embodiment the base assembly  28 , which includes the base extrusion  34 , the motor ramp  36 , the side plate supports  38 , and the side plates  40 . Additionally, the base assembly  28  includes motor ramp fasteners  146 , side plate support fasteners  148 , and side plate fasteners  150 . 
     In  FIG. 3 , the base extrusion  34  is a U-shaped channel adapted to be secured to surface(s) such as the gunnels. The motor ramp fasteners  146  secure the motor ramp  36  to the lower front portion of the base extrusion  34 . The side walls  44  run along the length of the base extrusion  34 . The side walls  44  are adapted to receive the side plate support fasteners  148 , which mount the side plate supports  38  to the side walls  44 . The side plate supports  38  are adapted to receive the side plate fasteners  150 , which mount the side plates  40  to the side plate supports  38 . The side plates  40  cover the side surfaces of the base extrusion  34  for cosmetic purposes. 
       FIGS. 4A to 4C  show different views of an embodiment of the base extrusion  34 . In addition to the side walls  44  and the base plate  42 , the base extrusion  34  includes side plate support apertures  152 , pivot mechanism apertures  154 , slots  156 , front edges  157 , locking notches  158 , thru holes  160 , and motor ramp apertures  162 . 
       FIGS. 4A to 4C  show the two spaced apart side walls  44  that extend generally vertically upward from the base plate  42  and extend generally parallel to one another along the edge of the base plate  42 . The side walls  44  define a recess capable of receiving the main arm  46  in the deployed position. In a one embodiment, the side walls  44  are configured with side plate support apertures  152  to receive the side plate support fasteners  148 , which mount the side plate supports  38  to the side walls  44 . 
     The countersunk pivot mechanism apertures  154  in the rear portion of the side walls  44  receive the fasteners  74 , which secure the rear pivot brackets  68  to the base extrusion  34 . Likewise, the slots  156  are configured to receive a projecting portion of the rear pivot brackets  68 . The slots  156  retain the rear pivot brackets  68  from pivotally rotating. 
     The diagonal front edges  157  of the side walls  44  interconnect the top edges of the side walls  44  with the locking notches  158 . In one embodiment, each locking notch  158  is disposed at a 7.5 degree angle to the base plate  42 . The lower edge of each locking notch  158  extends forward past the forward termination point of the front edges  157 . The lower edges of the locking notches  158  are configured to catch the latch bar  114 . The angle of the locking notches  158  draws the latch bar  114  into releasable engagement with the locking notches  158  when the main arm  46  is in the deployed position. In other embodiments, means including apertures, recesses, tabs, or slots may be used to engage the main arm  46  with the base assembly  28 . 
     In  FIGS. 4A to 4C , the base plate  42  is generally flat for ease of mounting, and rectangular in shape. The base plate  42  extends from a rear end generally near the rear pivot mechanism  48  to a front end, which interconnects with the motor ramp  36 . The base plate  42  is configured with thru holes  160 , which receive fasteners that secure the trolling motor assembly  10  to the surface of the watercraft  12 . The motor ramp apertures  162  extend through the base plate  42  and receive the motor ramp fasteners  146 , which secure the motor ramp  36  to the base plate  42 . 
       FIGS. 5A and 5B  show an embodiment of the motor ramp  36 , which includes a base interconnection portion  164 , apertures  166  and a motor engaging portion  168 . 
     The base interconnection portion  164  of the motor ramp  36  is adapted to be inserted on the front portion of the base plate  42  between the side walls  44 . The base interconnection portion  164  has apertures  166 , which align with the motor ramp apertures  162  when the motor ramp  36  is disposed on the base plate  42 . The motor ramp apertures  162  and the apertures  166  receive the motor ramp fasteners  146 , which secure the motor ramp  36  to the base plate  42 . In one embodiment, when the motor ramp  36  is disposed on the base plate  42 , the motor engaging portion  168  cantilevers off the front end of the base plate  42  and over the edge of the watercraft  12 . In  FIGS. 5A and 5B , the motor engaging portion  168  is spade shaped with two angled surfaces connecting at one forward end point. The motor engaging portion  168  is adapted to rotate the propulsion unit  24  of the trolling motor  16  as the unit  24  comes into contact with the motor ramp  36  at a position between stow and deploy. The motor ramp  36  reduces the likelihood of contact between the propulsion unit  24  and the watercraft  12 . 
     4. The Main Arm Assembly  30   
       FIG. 6  is an exploded front perspective view of an embodiment of the main arm assembly  30 , which includes the main arm  46 , the rear pivot mechanism  48 , the linkage assembly  50 , the latch system  52  and the motion control device  54 . 
     A. The Main Arm  46   
       FIGS. 7A to 7D  show different views of an embodiment of the main arm  46 . In addition to the bottom wall  56 , the top wall  58 , the side walls  60 , the rear pivot mechanism apertures  62 , and the lower front apertures  64 , the main arm  46  includes a lower cutaway  170 , spring apertures  172 , a stop aperture  174 , a safety latch slot  176 , stop portions  178 , front latch slots  180 , latch thru holes  182 , motion control device thru holes  184 , and cutouts  186 . 
     In  FIGS. 7A to 7D , the main arm  46  is a single piece extrusion with a rigid open frame comprised of four interconnected walls. In one embodiment, the main arm  46  is formed of a metallic such as aluminum. The main arm  46  is capable of housing most of the other components of the main arm assembly  36 . The bottom wall  56  is disposed below the top wall  58  when the main arm  46  is in the deployed position. The bottom wall  56  is generally rectangular and extends from a rear end adjacent the rear pivot mechanism  48  to a front end adjacent the motor coupling assembly  32 . The bottom wall  56  has a number of apertures. 
     The generally square shaped lower cutaway  170  extends through the rear portion of the bottom wall  56  and receives the yoke  66 . The rear portion of the bottom wall  56  extends to either side of the lower cutaway  170  and has spring apertures  172 , which receive the extension springs  110 . The extension springs  110  connect the rear latch assembly  100  to the main arm  46 . The threaded stop aperture  174  extends through the center middle portion of the bottom wall  56 . The stop aperture  174  receives a fastener, which secures the leaf spring stop  78  to the interior surface of the bottom wall  56 . The safety latch slot  176  extends into the front portion of the bottom wall  56 . The safety latch slot  176  is adapted to receive a portion of the safety latch  96  when the motor coupling assembly  32  is removed from the linkage assembly  50 . 
     The bottom wall  56  interconnects with a pair of generally rectangular shaped side walls  60 . The side walls  60  extend generally perpendicularly from the bottom wall  56 . The side walls  60  extend from the rear of the main arm  46  to the front. The rear portion of the side walls  60  are cantilevered off the end of the bottom wall  56  and the top wall  58 . The cantilevered portion has the rear pivot mechanism apertures  62 , which receive the rear pivot bushings  70  and rear pivot brackets  68 . In a one embodiment, the rear pivot mechanism apertures  62  are between about 1 inch and about 4 inches (about 25.4 mm and about 101.6 mm) in diameter. The pivot mechanism apertures  62  allow the main arm  46  to pivotally rotate about the stationary rear pivot brackets  68 . 
     The side walls  60  include features which allow the main arm  46  to couple with the linkage assembly  50 , the front latch assembly  102 , and the motion control device  54 . More specifically, in one embodiment the stop portion  178  of the upper top front edge of the side walls  60  is adapted to abuttably interface with the upper pin  80  when the main arm  46  is in the deployed position. The front latch slot  180  in the lower front portion of the sidewalls  60  is adapted to receive the latch bar  114 , which extends through the front latch slot  180  from the interior of the main arm  46 . The front latch slot  180  allows the latch bar  114  to releasably slide into and out of engagement with the locking notch  158  when the main arm  46  is in the deployed position. In  FIGS. 7A to 7D , the side walls  60  are configured with latch thru holes  182  and motion control device thru holes  184 , which receive pins  106  and  120  to pivotally couple the rear latch assembly  100  and the motion control device  54  to the main arm  46 , respectively. In one embodiment, the latch thru holes  182  or motion control device thru holes  184  may be counter bored to receive the head of a fastener (such as fastener  122 ), which allows the fastener head to be generally flush with the exterior surface of the side walls  60 . The lower front portion of the side walls  60  are configured with the lower front apertures  64  to receive the lower pin  92 , which pivotally couples the linkage assembly  50  to the main arm.  46 . In one embodiment, the side walls  60  have cutouts  186  separated by struts. The cutouts  186  allow the operator to view the interior components of the mount  18 , increase the cosmetic appeal of the mount  18 , and decrease the weight of the main arm  46 . 
     The side-walls  60  interconnect with the top wall  58 . As shown in  FIG. 2 , the top wall  58  is generally rectangular, and extends longitudinally from an end adjacent the rear pivot mechanism  48  to an end adjacent the motor coupling assembly  32 . The walls  50 ,  52 ,  54  surround and protect the interior components from damage during operation. The components that extend into or are located in the interior compartment  56  may include the leaf spring  76 , the rear latch assembly  100 , the front latch assembly  102 , and the motion control device  54 . In other embodiments of the invention, all or some of these components may be disposed outside the main arm  46 . 
     B. The Rear Pivot Mechanism  48   
       FIG. 6  shows an exploded front perspective view of the rear pivot mechanism  48 , which includes the yoke  66 , the rear pivot brackets  68 , the rear pivot bushings  70 , the rear pivot pin  72 , and the fasteners  74 . The rear pivot mechanism  48  is secured between the side walls  44  at the rear portion of the base extrusion  46  and pivotally couples the main arm  46  to the base extrusion  46 . The rear pivot mechanism  48  also pivotally couples the leaf spring  76  to the base extrusion  46 . In one embodiment, the rear pivot mechanism  48  allows the main arm  46  to be rotated approximately 177 degrees between the stowed position and the deployed position. 
       FIGS. 8A to 8D  show an embodiment of the yoke  66 , which includes hub receiving portions  186 , yoke pivot apertures  188 , channels  190 , a base portion  192 , shaft receiving arms  194  and apertures  196 . 
     In one embodiment, the yoke  66  is symmetrically disposed between the side walls  60  toward the rear portion of the main arm  46 . The yoke  66  is configured with two symmetric hub receiving portions  186  having yoke pivot apertures  188 . The yoke pivot apertures  188  extend through the hub receiving portions  186 , and are adapted to rotatably receive a portion of the rear pivot brackets  68 . The yoke  66  is configured to allow the yoke pivot apertures  188  to align with the rear pivot apertures  62  when the main arm  46  is in the deployed position. The outer surfaces of two hub receiving portions  186  are adapted with channels  190 , which are capable of receiving the rear pivot bushings  70 . The base portion  192  of the yoke  66  contacts the base plate  42  when the main arm  46  is in the deployed position. The base portion  192  is adapted with two symmetric shaft receiving arms  194 , which contact the base plate  42  when the main arm  46  is in the deployed position. When the main arm  46  is in the stowed position, the shaft receiving arms  194  project generally vertically and are adapted to receive and retain the shaft  22  of the trolling motor  16 . The apertures  196  extend through the base portion  192  and receive the rear knurled pin  118 , which interconnects the yoke  66  with the motion control device  54 . In one embodiment, the motion control device  54  actuates pivotal rotation of the yoke  66  about an axis defined by the rear pivot brackets  68  during a portion of the rotation of the main arm  46  between the stowed position and the deployed position. In one embodiment, this rotation occurs when the main arm  46  is between the stowed position and about 90 degrees. 
       FIGS. 9A to 9C  show an embodiment of the rear pivot brackets  68 , which include fins  198 , cylindrical hubs  200 , apertures  202 , keys  204 , rear apertures  206 , and retention apertures  208 . 
     In one embodiment, each rear pivot bracket  68  is disposed generally parallel to the other between hub receiving portions  186  of the yoke  66 , and each extends outward over the rear end of the base extrusion  34 . The fins  198  form the base of the rear pivot brackets  68 . The fins  198  interconnect with the cylindrical hubs  200  and taper rearward. The cylindrical hubs  200  allow the rear pivot brackets  68  to extend through the yoke pivot apertures  188  and the rear pivot mechanism apertures  62  such that the exterior surface of the cylindrical hubs  200  are roughly flush with the interior surface of the side walls  44 . In one embodiment, the circular projections  138  on the rear pivot brackets  68  (and the pivot apertures  62 ,  188 ) are between about 1 inch in diameter and about 4 inches in diameter (about 25.4 mm and about 101.6 mm). The larger diameter of the pivot coupling (the typical mount utilizes pivot pin with a typical diameter of 0.25 inch or 0.50 inch (6.4 mm or 12.7 mm)) between the main arm  46  and the base assembly  28  increases the durability of the pivot coupling. The increased durability of the pivot coupling reduces the likelihood that the coupling may loosen and cause the mount  18  to rattle or make other unpleasant noises during operation of the watercraft  12 . 
     The cylindrical hubs  200  are adapted with threaded apertures  202  to receive the fasteners  74 , which fix the rear pivot brackets  68  to the base extrusion  34 . The keys  204  extend outward from the cylindrical hubs  200 . The keys  204  are adapted to fit into and engage with the slots  156  on the rear side walls  44 . The rear apertures  206  extend through the rearward tapered portion of the fins  198 . The rear apertures  206  receive the rear pivot pin  72 , which allows the leaf spring  76  to pivotally couple to the rear pivot mechanism  48 . 
     The fins  198  may be configured to retain the rear pivot pin  72  non-pivotally or pivotally. In the embodiment shown in  FIG. 9C , the rear outward edge of the fin  198  is adapted with a threaded retention aperture  208 , which receives a fastener that engages the rear pivot pin  72 . The fastener retains the rear pivot pin  72  from pivotally rotating with the leaf spring  76 . The bushings  77  allow the leaf spring  76  to pivot on the stationary rear pivot pin  72  as the main arm  46  pivots on the rear pivot brackets  68 . 
       FIGS. 10A and 10B  show an embodiment of the rear pivot bushing  70 , which includes a lip  210  and an interior projection  212 . 
     The split ring rear pivot bushings  70  are disposed in the rear pivot mechanism apertures  62  on the main arm  46  between the edge of the rear pivot mechanism apertures  62  and the cylindrical hubs  200 . More specifically, the annular lip  210  engages the outer surface of the side walls  60 . The interior projection  212  interfaces with the edge of the rear pivot mechanism apertures  62  and the annular cylindrical hubs  200 . The rear pivot bushing  70  allows the main arm  46  to be pivotally rotated relative to the stationary rear pivot bracket  68 . 
     C. The Linkage Assembly  50   
       FIG. 6  shows an exploded front perspective view of the linkage assembly  50 , which includes the leaf spring  76 , the bushings  77 , the leaf spring stop  78 , the upper pin  80 , the front side links  82 , the linkage projections  84 , the bushings  86 , the rope guide  88 , the rope hole  90 , the lower pin  92 , the torsion spring  94 , the safety latch  96 , and the washer  98 . The linkage assembly  50  is disposed adjacent to (and pivotally couples with) the front portion of the main arm  46 , and extends through the main arm  46  to pivotally couple to the rear pivot mechanism  48 . The linkage assembly  50  and the motor coupling assembly  32  are adapted to removably interconnect. 
       FIGS. 11A and 11B  show the leaf spring  76 , which includes a rear portion  214 , a rear aperture  216 , a member  218 , a front portion  220 , and a front aperture  222 . 
     The rear portion  214  is adapted with the rear aperture  216  to receive the rear pivot pin  72  and the bushings  77 , which pivotally couple the leaf spring  76  to the rear pivot mechanism  48 . The member  218  interconnects with the rear portion  214  and extends through the open frame of the main arm  46 . In one embodiment, the member  218  may flexibly bow to contact the leaf spring stop  78  when the main arm  46  is in the stowed position. The front portion  220  interconnects with the member  218  and is adapted with the front aperture  222  to receive the upper pin  80  and the bushings  77 , which pivotally couple the leaf spring  76  to the remainder of the linkage assembly  50 . The leaf spring  76  actuates pivotal rotation of the remainder of the linkage assembly  50  (and the motor coupling assembly  32 ) about the pivot coupling between the main arm  46  and the linkage assembly  50 . The leaf spring  76  rotates the remainder of linkage assembly  50  (and the motor coupling assembly  32 ) from the generally vertical position when in the stowed position, to the generally horizontal position in the deployed position. 
       FIG. 6  shows the front side links  82 , which include the linkage projections  84 . The two front side links  82  receive the ends of the upper pin  80  and extend downward and forward generally parallel to each other to receive the lower pin  92 . More specifically, the longitudinally and vertically offset trapezoidal linkage projections  84  are adapted to receive the lower and upper pins  80 ,  92 . The linkage projections  84  extend outwards from the exterior side surface of the front side links  82 . In one embodiment, the linkage projections  84  are selectively sized and geometrically disposed to interlock with the recesses  142  on the motor coupling assembly  32 . 
       FIGS. 12A and 12B  show an embodiment of the rope guide  88 , which in addition to the rope hole  90 , includes an upper portion  224 , upper apertures  226 , lower members  228 , a motor coupling aperture  230 , and lower apertures  232 . 
     The upper portion  224  of the rope guide  88  is separated from the front side links  82  along the length of the upper pin  80  by the bushings  86 . The upper apertures  226  pivotally receive the upper pin  80 . The upper portion  224  is disposed symmetrically over the front portion  220  and extends down to receive the upper pin  80  to either side of the front portion  220  of the leaf spring  76 . The rope hole  90  extends downward through the upper portion  224 . The rope hole  90  is adapted to receive the rope  14 . The upper portion  224  extends forward and interconnects with the lower members  228 . The two lower members  228  extend downward generally parallel to each other to receive the lower pin  92 . In one embodiment, the threaded motor coupling aperture  230  receives the fastener  138 , which secures the motor coupling assembly  32  to the linkage assembly  50 . The lower apertures  232  receive the lower pin  92 , which allows the rope guide  88  to pivotally couple with the main arm  46 . 
       FIGS. 13A and 13B  show front and side views of an embodiment of the safety latch  96 , which includes a main body  234 , an aperture  236 , a rearward nose  238 , and a forward nose  240 . 
     In one embodiment, the safety latch  96  is disposed on the lower pin  92  adjacent one of the lower members  228 . The cylindrical main body  234  surrounds the lower pin  92 . The aperture  236  pivotally receives the lower pin  92 . The rearward nose  238  extends from the main body  234  and engages the torsion spring  94 . The forward nose  240  extends from the main body  234  and engages the motor coupling assembly  32  when the motor coupling assembly  32  is mounted on the linkage assembly  50 . The torsion spring  94  engages the adjacent lower member  228  to bias the rearward nose  238  into the safety latch slot  176  when the motor coupling assembly  32  is not interconnected with the linkage assembly  50 . 
     D. The Latch System  52   
       FIG. 6  shows an exploded front perspective view of the latch system  52 , which includes the rear latch assembly  100 , the latch straps  101 , and the front latch assembly  102 . The rear latch assembly  100  includes the rear latch bracket  104 , the pivot pin  106 , the e-clips  108 , and the extension springs  110 . The front latch assembly  102  is comprised of the latch strap bracket  112  and the latch bar  114 . The latch system  52  is configured to releasably engage with the base extrusion  34  to lock the main arm  46  in the deployed position, and to releasably engage with the rear pivot mechanism  48  to lock the main arm  46  in the stowed position. In one embodiment, the operator must actuate the latch system by pulling on the rope  14  before rotating the main arm  46  from either the stowed position or the deployed position. The latch system  100  protects against unintended and potentially harmful rotation of the main arm  46 . 
       FIGS. 14A and 14B  show an embodiment of the rear latch bracket  104 , which includes side surfaces  242 , a member  244 , a cutout  246 , spring apertures  248 , pivot apertures  250 , notches  252 , and upper apertures  254 . 
     The rear latch bracket  104  has two symmetrical side surfaces  242  disposed generally parallel to each other. In one embodiment, the side surfaces  242  are disposed adjacent the interior surface of the side walls  60 . The side surfaces  242  are interconnected by the member  244 . The half circular cutout  246  extends symmetrically through the lower portion of the member  244 . The cutout  246  accommodates the barrel of the bias mechanism  116  when the main arm  46  is in the deployed position. 
     The spring apertures  248  on the lower rear portion of each side surface  242  receive the extension springs  110 , which connect the rear latch bracket  104  to the main arm  46  via the apertures  172 . The extension springs  110  bias the rear latch assembly  100  and the front latch assembly  102  into releasable engagement. To unlatch the rear latch assembly  100  and the front latch assembly  102  this bias must be overcome by the force of the operator&#39;s pull on the rope  14 . In one embodiment, the extension springs  110  have an outside diameter of 0.375 inches (9.5 mm), a length of 1.25 inches (31.8 mm), and a spring rate of 30.26 pounds/inch (5.3 N/mm). 
     The pivot apertures  250  are disposed through the lower rear of the side surfaces  242  and receive the pivot pin  106 , which pivotally couples the rear latch bracket  104  to the main arm  46 . In one embodiment, the side surfaces  242  are contacted by the e-clips  108 , which retain the rear latch bracket  104  symmetrically on the pivot pin  106 . 
     The notches  252  extend through rear edge side surfaces  242  and are configured to engage with the rear pivot pin  72  of the rear pivot mechanism  48  when the main arm  46  is in the stowed position. The notches  252  remain in engagement (biased by the extension springs  110 ) with the rear pivot pin  72  in the stowed position until the rear latch assembly  100  is pivotally actuated out of engagement by the operator. 
     The upper apertures  254  receive fasteners, which pivotally couple the rear latch bracket  104  to the latch straps  101 . The latch straps  101  interconnect the rear latch bracket  104  with the latch strap bracket  112  (and the rear latch assembly  100  with the front latch assembly  102 ). The latch straps  101  are adapted to pivotally couple to both the rear latch bracket  104  and latch strap bracket  112 . Thus, both the rear latch assembly  100  and the front latch assembly  102  may be actuated simultaneously by the pull of the rope  14 . 
       FIGS. 15A to 15C  show an embodiment of the latch strap bracket  112 , which includes side walls  256 , a base platform  258 , thru holes  260 , square apertures  262 , slots  264 , an front wall  266 , a rope aperture  270 , and a groove projection  272 . 
     The latch strap bracket  112  is disposed in the interior of the main arm  46  adjacent the front end of the main arm  46 . The symmetrical side walls  256  of latch strap bracket  112  interconnect generally vertically with the base platform  258 . Thru holes  260  receive the fasteners, which pivotally couple the latch straps  101  to the latch strap bracket  112 . The square apertures  262  are adapted to receive the latch bar  114 , which extends outward to either side of the side walls  256 . The slots  264  receive the lower pin  92 , which allows the latch system  52  to be slidably linearly actuated into and out of engagement with the base extrusion  34  or the rear pivot mechanism  48 . 
     The front wall  266  interconnects to the side walls  256 . The rope aperture  270  extends through the front wall  266  and is adapted to receive the rope  14 , allowing the rope  14  to interconnect with the latch strap bracket  112 . This interconnection may occur, for example, by looping the rope  14  around the aperture  270  and then tying a knot, or by extending the rope  14  through the aperture  270  and then tying a knot that is larger than the rear side of the aperture  270 . 
     The groove projection  272  extends generally vertically from the central portion of the base platform  258  generally parallel with the side walls  256 . The groove projection  272  generally aligns horizontally with the square apertures  262 . The groove projection  272  engages the latch bar  114  and retains the latch bar  114  from side-to-side movement. 
       FIGS. 16A and 16B  show an embodiment of the latch bar  114 , which includes a groove  274  and end portions  276 . 
     The latch bar  114  is generally square in cross section, and in one embodiment is made of a polymer material, which reduces vibratory noise and can be cost effectively replaced after a period of use. The latch bar  114  extends through the latch strap bracket  112  from one side wall  256  to the other. The groove  274  extends across the center of the bottom surface of the latch bar  114  and engages the groove projection  272 . The end portions  276  of the latch bar  114  are rounded and extend from the side walls  256  through the slots  132  in the main arm  46  to engage the locking notches  158  in the base extrusion  34  when the main arm  46  is in the deployed position. The latch bar  114  remains in engagement (biased by the extension springs  110 ) with the locking notches  158  in the deployed position until the front latch assembly  102  is actuated by the operator. By applying a pulling force to the rope  14  the operator causes the latch strap bracket  112  to slide forward moving the latch bar  114  out of engagement with the locking notches  158 . 
     E. The Motion Control Device  54   
       FIG. 6  shows an exploded front perspective view of the motion control device  54 , which includes the bias mechanism  116 , the rear knurled pin  118 , the front pivot pin  120 , and fasteners  122 . The motion control device  54  pivotally couples with the main arm  46  and extends within the main arm  46  to pivotally couple with the rear pivot mechanism  48 . The motion control device  54  may be configured to assist, impede, or otherwise bias the movement of the main arm  46  from the stowed position to the deployed position. In one embodiment, the motion control device  54  is configured to assist the operator when the main arm  46  rotates through a part of its movement from the deployed position to the stowed position. In one embodiment, this assisting force is exerted by the motion control device  54  from the deployed position to about 90 degrees. In another one embodiment, the motion control device  54  is configured to impede the rotate of the main arm  46  through a part of its movement from the stowed position to the deployed position. In one embodiment, this impeding force is exerted by the motion control device  54  from about 90 degrees to the deployed position. The motion control device  54  may be configured to exert biasing forces (whether assisting or impeding) on the main arm  46  during other portions of the rotation path of the main arm  46  between the stowed position and the deployed position in other embodiments of the invention. 
       FIGS. 17A and 17B  show an embodiment of the bias mechanism  116 , which includes a rear portion  278 , a rear aperture  280 , a main body  282 , a front portion  284 , and a front aperture  286 . 
     The rear portion  178  has the rear aperture  280 , which extends through it. The rear aperture  280  receives the rear knurled pin  118 , which allows the bias mechanism  116  to the pivotally couple with the rear pivot mechanism  48 . The main body  282  interconnects with the rear portion  278 , and in the embodiment shown is extendable and retractable from the rear portion  278 . In one embodiment, the main body  282  is extendable and retractable only during a portion of the rotation of the main arm  46  between the stowed position and the deployed position. In one embodiment, the bias mechanism  116  exerts its biasing force on the main arm  46  only during the extendable or retractable movement of the main body  282 . The main body  282  interconnects with the front portion  284 . The front aperture  286  extends through the front portion  284 . The front aperture  284  receives the front pivot pin  120 , which allows the bias mechanism  116  to pivotally couple with the main arm  46 . In one embodiment, the front pivot pin  120  is fixed to the main arm  46  by the fasteners  122 . 
     In one embodiment, the bias mechanism  116  is a gas spring that provides assistance or resistance to the main arm  46 . According to an exemplary embodiment, the device  40  is a type of commercially available gas spring (Part No. 15F100260TT) from Engineered Components Products Hardware, LLC. In other embodiments, the bias mechanism may be an air, an elastomer, a spring, a hydraulic device, or a mechanical device. 
     5. The Motor Coupling Assembly  32   
       FIG. 18  shows an embodiment of the motor coupling assembly  32 , which includes the upper cover  124 , the upper bushing  126 , the upper sleeve  128 , the spring  130 , the lower sleeve  132 , the lower bushing  134 , the lower cover  136  and the fastener  138 . Additionally, the lower cover  132  includes a second orifice  287 , and the upper cover  128  includes an aperture  288 . The motor coupling assembly  32  is removable from the linkage assembly  50  and the remainder of the mount  18  and is configured to couple with, retain, and guide the shaft  22  of the trolling motor  16 . 
     In  FIG. 18 , the upper cover  124  extends over and interfaces with the upper bushing  126 , and extends around and over the lower portion of the upper sleeve  128 . The upper sleeve  128  rotatably interfaces against and aligns with the upper bushing  126  and the spring  130 . The upper sleeve  128  rotatably couples with the shaft  22  of the trolling motor  16  when the shaft  22  is inserted in the assembly  32 . In one embodiment, the upper sleeve  128  may be configured to selectively tighten and loosen on the: shaft  22 . 
     The spring  130  aligns with and interfaces against both the upper sleeve  128  and the lower sleeve  132 . The spring  130  protects and absorbs some of the shock incurred during operation of the trolling motor  16 . The lower sleeve  132  aligns with and rotatably interfaces against the spring  130  and the lower bushing  134 . The lower sleeve  132  rotatably couples with the shaft  22  of the trolling motor  16 . In one embodiment, the lower sleeve  132  may be configured to selectively tighten and loosen on the shaft  22 . 
     The lower cover  136  interconnects with and is fastened to the upper cover  124  to surround the interior components. The orifices  140 ,  287  in the upper and lower covers  124 ,  136  vertically align. The other components including the upper bushing  126 , the upper sleeve  128 , the spring  130 , the lower sleeve  132 , the lower bushing  134  also vertically align with the orifices  140 ,  287 . The aligned components allow the second orifice  287  to receive the shaft  22  of the trolling motor  16 . 
     In one embodiment, the fastener  138  may be received by the aperture  288 , which aligns with the motor coupling aperture  230 . In one embodiment, the fastener  138  threads into the motor coupling aperture  230  to removably secure the motor coupling assembly  32  to the linkage assembly  50 . Alternatively, (or in addition to the fastener  138 ) the upper cover  124  may include the recesses  142  and/or the tracks  144  adapted to interface with and mount the motor coupling assembly  32  to the front side links  82 . 
     6. The Mounting of the Motor Coupling Assembly  32   
       FIG. 19  shows the mount  18  and the features that allow the motor coupling assembly  32  to be removable from the linkage assembly  50  and the mount  18 . These features and components include the front side links  82 , the linkage projections  84 , the fastener  138 , the recesses.  142  and the tracks  144 . These features and components allow the motor coupling assembly  32  to be quickly disconnected from or connected to the linkage assembly  50  and the mount  18 . 
     In  FIG. 19 , the motor coupling assembly  32  is adapted with the single aperture  288  which receives the single fastener  138 . The fastener  138  passes through the aperture  288  and engages the motor coupling aperture  230  in the rope guide  88  to connect the motor coupling assembly  32  to the linkage assembly  50  and the mount  18 . Because conventional linkages between the trolling motor and the mount utilize multiple fasteners, the single fastener  138  allows the operator to more quickly and easily remove or connect the motor coupling assembly  32  to or from the mount  18 . In one embodiment, the fastener  138  is the only means used to interconnect the motor coupling assembly  32  with the linkage assembly  50 . 
     By locating the rope hole  90  in the rope guide  88 , the motor coupling assembly  32  and trolling motor  16  can be quickly and easily disconnected from or connected to the mount  18  when compared with the conventional bow mount assembly. This is because in the conventional bow mount assembly the rope runs through the main arms to the motor coupling assembly. With the conventional configuration, therefore, the rope must be untied from the interior of the bow mount assembly&#39;s main arms before the motor coupling assembly and the trolling motor can be removed from the remainder of the mount. 
     In  FIG. 19 , the fastener  138  is not the only means of interconnecting the motor coupling assembly  32  to the linkage assembly  50 . In  FIG. 19 , the fastener  138  is supplemented by the upper cover  124  and the front side links  82 , which are configured to interlock using male and female surface profiles. In the embodiment shown in  FIG. 19 , the interior surface of the upper cover  124  has longitudinally and vertically offset recesses  142 . The symmetry of the recesses  142  is mirrored by longitudinally and vertically offset trapezoidal linkage projections  84 , which extend outwards from the side surfaces of the front side links  82 . 
     The linkage projections  84  are selectively sized to interlock with the recesses  142 . The linkage projections  84  and the recesses  142  interlock to retain the motor coupling assembly  32  from side-to-side or vertical motion when the motor coupling assembly  32  is interconnected to the linkage assembly  50 . In other embodiments of the invention, the male and female interlocking surface profiles may be the only means of retaining the motor coupling assembly  32  and connecting the assembly  58  to the mount  18 . In other embodiments, the male profile may be on the motor coupling assembly  32  and the female profile may be on the front side links  82 . The male/female interlocking profiles allow the operator to quickly remove or connect the motor coupling assembly  32  to or from the mount  18 . 
     In  FIG. 19 , the interior side surfaces of the upper cover  124  may have generally vertical depressed surfaces that form the tracks  144 . The tracks  144  may be used to guide the upper rear linkage projections  84  into interlocking contact with the recesses  142 . Thus, to connect the motor coupling assembly  32  to the front side links  82 , the motor coupling assembly  32  must initially be disposed above the front side links  82 . The upper rear linkage projections  84  are aligned with the tracks  144 . The motor coupling assembly  32  is moved vertically downwards toward the front side links  82  until the upper rear linkage projections  84  contact the tracks  144 . The tracks  144  guide the linkage projections  84  into interlocking contact with the recesses  142  as the motor coupling assembly  32  is moved downwards onto the front side links  82 . The process is reversed to remove the motor coupling assembly  32  from the front side links  82 . 
     7. The Assembled Rear Pivot Mechanism  48   
       FIG. 19  shows the assembled rear pivot mechanism  48  disposed at the rear of the base assembly  28  and main arm assembly  30 . In  FIG. 19 , the main arm assembly  30  is shown in the deployed position. 
     In the deployed position, the base portion  192  of the yoke  66  contacts the base plate  42 . The yoke  66  is disposed symmetrically between the side walls  44 . The yoke  66  receives the cylindrical hubs  200  of the rear pivot bracket  68 . The yoke  66  is configured to pivotally rotate on the cylindrical hubs  200  of the rear pivot brackets  68 . The rear pivot bushings  70  interface the outer annular surface of the cylindrical hubs  200  and the circular edge of the rear pivot apertures  62 . The rear pivot bushings  70  allow the main arm  46  to pivot relative to the fixed rear pivot brackets  68  between the stowed position and the deployed position. 
     The fasteners  74  (received by the pivot mechanism apertures  154  and threaded into the apertures  202  in rear pivot bracket  68 ) and slot projection  204  secure the rear pivot brackets  68  in a stationary position to the side walls  44  of the base extrusion  34 . The two rear pivot brackets  68  cantilever rearward off the rear end of the side walls  44  generally parallel to one another, and receive the rear pivot pin  72 . The rear portion  214  of the leaf spring  76  pivotally couples to the rear pivot pin  72  between the rear pivot brackets  68 . 
     8. The Operation of the Latching System  52   
       FIG. 19  shows the latch bar  114  extending from the side surfaces  60  of the main arm  46  to releasably engage the locking notches  158 . While the first arm  46  is in the deployed position the latch bar  114  remains in locked releasable engagement with the locking notches  158  until the operator actuates the latching system  52  forward by pulling on the rope  14 . As will be discussed in greater detail subsequently, while the motor coupling assembly  32  is removed from the linkage assembly  50  (as shown in  FIG. 19 ) the latching system  52  cannot be actuated by the operator&#39;s pulling on the rope  14 . In  FIG. 19 , the rope  14  enters the interior of the linkage assembly  50  via the rope hole  90 . 
     In  FIG. 20 , the rope  14  is shown entering the interior of the linkage assembly  50 , which is engaged with the motor coupling assembly  32 . The rope  14  extends generally vertically downward between the lower members  228  of the rope guide  88 . The rope  14  wraps over the front facing portion of the lower pin  92  before entering the interior compartment of the main arm  46  to connect generally horizontally to the latch strap bracket  112 . 
       FIG. 20  shows the “latch system lockout,” which includes the torsion spring  94  and safety latch  96 . In  FIG. 20 , the motor coupling assembly  32  is mounted on the linkage assembly  50 , and the safety latch  96  is disposed on the lower pin  92  adjacent one of the lower members  228 . Because the motor coupling assembly  32  is mounted on the linkage assembly  50 , the rearward nose  238  of the safety latch  96  engages the torsion spring  94  and points generally rearward in a raised position. In  FIG. 20 , the forward nose  240  engages the motor coupling assembly.  32  and points generally forward. The torsion spring  94  engages the adjacent lower member  228  and the rearward nose  238  to bias the safety latch  96 . If the motor coupling assembly  32  was not mounted to the linkage assembly  50  and engaging the forward nose  240 , the safety latch  96  would rotate downward to dispose the rearward nose  238  in the safety latch slot  176 . While received in the safety latch slot  176 , the rearward nose  238  interferes with the sliding movement of the latch strap bracket  112  so that the main arm  46  cannot be unlatched from either the stowed position or the deployed position. 
       FIG. 21A  shows the components of the latching system  52  in the deployed position with the base assembly  28  and main arm  46  suppressed (i.e. not shown). In  FIG. 21A , the rope  14  generally horizontally interconnects with the latch strap bracket  112 . The slots  264  engage the lower pin  92  to transfer the pulling motion that the operator exerts on the rope  14  to a generally horizontal linear motion. When the main arm  46  is in the deployed position and the operator has not actuated the rope  14 , the extension springs  110  bias the latch bar  114  into engagement with the locking notches  158 . When actuated, the horizontal (relative to the deck of the watercraft  12 ) linear motion of the rope  14  overcomes the bias of the extension springs  110  to unlock the front latch assembly  102  by disengaging the latch bar  114  from the locking notches  158  on the base extrusion  34 . 
       FIG. 21B  shows the components of the latching system  52  in the stowed position. In this position, the rear latch bracket  104  notches  252  engage the rear pivot pin  72 . The locking notches  98  remain in engagement (biased by the extension springs  110 ) with the rear pivot pin  72  in the stowed position until the rear latch assembly  100  is pivotally actuated out of engagement by the operator. The rear latch assembly  100  may be actuated out of engagement by a pull of the rope  14 ; which slides the front latch assembly  102  forward. The sliding motion of the front latch assembly  102  pulls the latch straps  101  forward. The latch straps  101  pivotally couple to the rear latch bracket  104 . The rear latch assembly  100  is pulled pivotally forward out of engagement with the rear pivot pin  72  by the latch straps  101 . 
     9. The Operation of the Linkage Assembly  50   
       FIGS. 21A and 21B  show the linkage assembly  50  with the main arm  46  and base assembly  28  suppressed (i.e. not shown). In  FIG. 21A , the linkage assembly  50  is shown in the deployed position. In this position, the upper pin  80  couples the leaf spring  76  to the remainder of the linkage assembly  50 . To clarify, when this document refers to “the remainder of the linkage assembly” or to “the front portion of the linkage assembly” it is intended to refer to the components of the linkage assembly  50  excluding the leaf spring  76  and the bushings  77 . The front portion of the linkage assembly  50  is configured to pivotally couple with the main arm  46  via the lower pin  92 . The leaf spring  76  and the main arm  46  are configured to place the upper pin  80  into interference with the stop portions  178  of the main arm  46  when the main arm  46  is in the deployed position. In the deployed position, the main arm  46  and the rear pivot mechanism  48  are configured to place the leaf spring  76  in tension. This tension force causes the leaf spring  76  to exert a resistive force moment on the linkage assembly  50 . The force moment actuates the interference engagement between the linkage assembly  50  and the main arm  46 , and impedes the rotation of the front portion of the linkage assembly  50  out of the interference engagement (and the motor coupling assembly  32  out of the generally horizontal position). The force moment generated by the leaf spring  76  reduces play at the coupling joint between the linkage assembly  50  and the main arm  46 . The reduction in joint play reduces the likelihood of vibratory noise when the mount  18  is in the deployed position. 
     In another embodiment, the leaf spring  76  and/or the main arm  46  may be selectively configured to position the linkage assembly  52  (and the motor coupling assembly  32 ) in a position other than the one shown in  FIG. 21A . The leaf spring  76  actuates pivotal rotation of the linkage assembly  50  about an axis defined by the lower pin  92  as the main arm  46  rotates between the stowed position and the deployed position. 
     In  FIG. 21B , the linkage assembly  50  is shown in the stowed position. In addition to the main arm  46  and base assembly  28 , the guide member  68  has also been suppressed to better show the leaf spring  76 . In the stowed position, the front portion of the linkage assembly  50  (and the motor coupling assembly  32 ) is rotated to the generally vertical position shown. The leaf spring  76  actuates the pivotal rotation of the front portion of the linkage assembly  50  from the interference engagement when the mount  18  is in the deployed position, to the generally vertical position when the mount  18  is in the stowed position. In the stowed position, the upper pin  80  which couples the front portion of the linkage assembly  50  to the front portion  214  of the leaf spring  76  is now disposed near the lower rear portion of the mount  18 . In the stowed position, the main arm  46  and the rear pivot mechanism  48  are configured to place the leaf spring  76  in compression. This compressive force causes the leaf spring  76  to exert a resistive force moment on the remainder of the linkage assembly  50 . This force moment holds the motor coupling assembly  32  in the generally vertical position shown while the mount  18  remains in the stowed position. The force moment impedes rotation of the front portion of the linkage assembly  50  (and the motor coupling assembly  32 ) out of the generally vertical position. The force moment generated by the leaf spring  76  reduces play at the coupling joint between the linkage assembly  50  and the main arm  46 . The reduction in joint play reduces vibratory noise when the mount  18  is in the stowed position. 
     In other embodiments, the leaf spring  76  and/or the main arm  46  may be selectively configured to position the front portion of the linkage assembly  50  (and the motor coupling assembly  32 ) in a position other than the generally vertical position. In one embodiment, the position of the linkage assembly  50  in the stowed position may be determined by the leaf spring stop  78 , which acts as a spacer to halt the rotation of the leaf spring  76  inside the main arm  46 . In another embodiment, the leaf spring stop  78  may retain the leaf spring  76  from flexibly bowing when the main arm  46  is in the stowed position. In another embodiment of the invention, the leaf spring  76  and/or the leaf spring stop  78  may be disposed outside the interior compartment  56  of the main arm  46 . 
     10. The Operation of the Motion Control Device  54   
       FIGS. 21A and 21B  show the motion control device  54 , which extends forward from the rear pivot mechanism  48  toward the motor coupling assembly  32 . In  FIG. 21A , the bias mechanism  116  pivotally couples to the yoke  66  via the rear knurled pin  118 . The bias mechanism  116  extends forward from the yoke  66  to pivotally couple with the front pivot pin  120 . In  FIG. 21A  the bias mechanism  116  is retracted. 
     In one embodiment, the bias mechanism  116  rotates with the movement of the main arm  46  from the deployed position shown in  FIG. 21A  to the stowed position shown in  FIG. 21B . In one embodiment, the bias mechanism  116  extends for a portion of the movement of the main arm  46  from the deployed position to the stowed position. In one embodiment, the extension of the bias mechanism  116  aids the operator in lifting and rotating the main arm  46 . As the main arm  46  reaches about 90 degrees, the bias mechanism  116  becomes fully extended and no longer exerts a biasing force on the main arm  46 . After the bias mechanism  116  becomes fully extended the bias mechanism  116  actuates rotation of the yoke  66 , which is configured to pivotally rotate on a portion of the rear pivot brackets  68 . In one embodiment, when the yoke  66  is not contacting the base plate  42 , the bias mechanism  116  exerts no biasing force on the main arm  46 . 
     In the stowed position shown in  FIG. 21B , the yoke  66  is not in contact with the base plate  42 , and the receiving members  194  of the yoke  66  extend generally vertically. As the main arm  46  begins to rotate from the stowed position to the deployed position, the bias mechanism  116  actuates rotation of the yoke  66  downward toward the base plate  42 . In one embodiment, the bias mechanism  116  begins to retract and exert a biasing force on the main arm  46  when the base of the yoke  66  with the receiving members  194  contacts the base plate  42 . In another embodiment, the retraction of the bias mechanism  116  exerts a resistive force on the main arm  46 . The bias mechanism  116  continues to exert the biasing force while retracting. In one embodiment, the yoke  66  remains in contact with the base plate  42  and the bias mechanism  116  continues to exert the biasing force from about 90 degrees to the deployed position. 
     11. The Operation of the Rear Pivot Mechanism  48   
       FIGS. 21A and 21B  show the rear pivot mechanism  48  in the stowed position and the deployed position, viewed from the same perspective. In  FIG. 21A  the receiving members  194  of the yoke  66  are in horizontal contact with the base plate  42 , and the yoke  66  is configured to pivotally rotate about and axis defined by the rear pivot brackets  68 . As main arm  46  rotates from the deployed position in  FIG. 21A , to the stowed position in  FIG. 21B , the receiving members  194  pivotally rotate upward off the base plate  42 . The pivotal rotation of the yoke  66  is actuated by the motion control device  54 . In  FIG. 21B , the receiving members  194  of the yoke  66  extend generally vertically to receive the shaft  22  of the trolling motor  16 . In  FIGS. 21A and 21B , the rear pivot brackets  68  remain in a stationary position fixed to the base extrusion  34 . The annular portion of the rear pivot brackets  68  interface with the rear pivot bushings  70 , which allows the main arm  46  to pivotally rotate from the deployed position to the stowed position. The rear pivot brackets  68  retain the rear pivot pin  72 , which pivotally couples the leaf spring  76  to the rear pivot brackets  68 . 
     12. The Overall Assembly  18   
       FIG. 22  further illustrates the disposition of some of the components of the motor coupling assembly  32 , the rear pivot mechanism  48 , the linkage assembly  50 , the latching system  52 , and the motion control device  54 , when the main arm  46  is in the deployed position. In  FIG. 22 , the side plates  40 , main arm  46 , and leaf spring  76  are suppressed (i.e. not shown). 
     In  FIG. 22 , the motor coupling assembly  32  is mounted to the front portion of the linkage assembly  50 . The front latch assembly  102  is slightly disengaged from the locking notches  158 . More specifically, the latch strap bracket  112  has been slidably actuated forward on the slots  264  around the lower pin  92  such that the latch bar  114  is not in full engaging contact with the locking notches  158 . 
       FIG. 22  also shows some of the improvements to the mount  18 . One of these improvements is the large diameter of the rear pivot mechanism  48 , which increases the durability of the pivot coupling between the main arm  46  and the base assembly  28 . More specifically, in one embodiment of the invention, the hub receiving portions  186  of the yoke  66 , the cylindrical hubs  200  of the rear pivot bracket  68 , the rear pivot bushings  70 , and the rear pivot mechanism apertures  62  of the main arm  46  may all be over about 1 inch (25.4 mm) in diameter. These components are configured to interconnect to form the pivot coupling between the main arm  46  and the base assembly  28 . The larger diameter pivot coupling (the typical mount utilizes pivot pin with a typical diameter of 0.25 inch or 0.50 inch (6.4 mm or 12.7 mm)) between the main arm  46  and the base assembly  28  increases the durability of the pivot coupling. The increased durability of the pivot coupling reduces the likelihood that the coupling may loosen and cause the mount  18  to rattle or make other unpleasant noises during operation of the watercraft  12 . 
       FIG. 22  also shows the improved interconnection between the motor coupling assembly  32  and the linkage assembly  50 . By locating the rope hole  90  in the rope guide  88 , the motor coupling assembly  32  and trolling motor  16  can be quickly and easily disconnected from or connected to the linkage assembly  50  via the single fastener  138  and/or the recesses  142  and/or the tracks  144 . The connection and disconnection process is easier than that of the conventional bow mount assembly. This is because in the conventional bow mount assembly the actuation rope runs through the main arms to the motor coupling assembly, and because multiple fasteners are used to connect the motor coupling assembly to the main arms. With the conventional configuration, therefore, the rope must be untied from the interior of the bow mount assembly&#39;s main arms and the fasteners loosened and removed before the motor coupling assembly and the trolling motor can be removed from the remainder of the mount. 
       FIG. 23  shows the rotation of the of the main arm assembly  30 , the motor coupling assembly  32  and the yoke  66  as the main arm  46  rotates between the stowed position and the deployed position.  FIG. 23  shows some of the improvements to the mount  18 . The rigid open frame main arm  46  provides durable light weight protection for the other components of the main arm assembly  30 . 
     The leaf spring  76  is one component of the main arm assembly  30  which extends within the open frame of the main arm  46 . The leaf spring  76  provides smooth constant rotational actuation force to the remainder of the linkage assembly  50  as the main arm  46  rotates between the stowed position and the deployed position. The remainder of the linkage assembly  50  interconnects with motor coupling assembly  32  to provide the motor coupling assembly  32  with smooth constant pivotal rotation between the stowed position and the deployed position. In the deployed position and the stowed position, the leaf spring  76  exerts “down pressure” (from the force moment it exerts) on the remainder of the linkage assembly  50  (and motor coupling assembly  32 ). This “down pressure” reduces play at the coupling joint between the linkage assembly  50  and the main arm  46 . The reduction in joint play reduces the likelihood of vibratory noise when the mount  18  is in the stowed and deployed position. 
     Although the present invention has been described with reference to one embodiments, workers skilled in the art will recognize that changes may be made in form and detail without departing from the spirit and scope of the invention.