Trolling motor mount with mono main arm

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.

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's actuation rope (which is used to lift and rotate the bow mount's movable arms from the stowed or deployed position) runs through the mount'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'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.

DETAILED DESCRIPTION

1. Overview of the Assembly10

FIGS. 1A and 1Bshow an embodiment of a trolling motor assembly10, which is secured to the gunnels or other suitable surface(s) of a watercraft12. The trolling motor assembly10includes a rope14, a trolling motor16, and a mount18. The trolling motor16includes a head20, a shaft22, a propulsion unit24and a propeller26. The mount18includes a base assembly28, a main arm assembly30, and a motor coupling assembly32.

InFIG. 1A, the trolling motor assembly10is shown in the deployed position with the trolling motor16entering the water. InFIG. 1B, the trolling motor assembly10is shown in the stowed position with the trolling motor16retained aboard the watercraft12, generally parallel with the gunnels of the watercraft12. In both positions, the trolling motor16is secured by the mount18to the watercraft12.

InFIGS. 1A and 1B, the base assembly28secures the remainder of the mount18and the trolling motor16to the watercraft12. The rear of the main arm assembly30pivotally couples with the rear of the base assembly28. The front of the main arm assembly28pivotally couples with the motor coupling assembly32, which rotatably couples with the shaft22of the trolling motor16. The main arm assembly30is adapted to rotate relative to the base assembly28between the stowed position and the deployed position. The main arm assembly30is configured to releasably latch to the base assembly28in the stowed position and in the deployed position. In one embodiment, the rope14enters the interior of the main arm assembly30and is used by the operator to unlatch the main arm assembly30from the base assembly30in the stowed position and in the deployed position. In another embodiment, the rope14is used to rotate the main arm assembly30between the stowed position and the deployed position. Simultaneous with the rotation of the main arm assembly30from the stowed position to the deployed position, the main arm assembly30is adapted to rotate the motor coupling assembly32from a first generally vertical position to a second generally horizontal position. The pivotal rotation of the motor coupling assembly32allows the trolling motor16to be disposed generally vertically in the water for operational use in deployed position, and allows the trolling motor16to be disposed generally horizontal to the gunnels for “non-use” in the stowed position.

In the deployed position illustrated inFIG. 1A, the trolling motor assembly10operates to control the velocity and direction of the watercraft12. The watercraft12may be any make, model, or size; and may be a recreational or commercial vessel. To drive the watercraft12, the propulsion unit24must be positioned below the surface of the water. The trolling motor16exerts mechanical propulsion by converting electrical current into thrust of the propeller26while the propulsion unit24is in the water. The shaft22is coupled with the mount18and the mount18is secured to a surface of the watercraft12. The interconnected components allow the propulsion unit24to transfer the thrust of the propeller26to the watercraft12. The trolling motor16(and watercraft12) 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 head20.

FIG. 2shows an exploded view of an embodiment of the mount18, viewed from the rear. The base assembly28is comprised of a base extrusion34, a motor ramp36, side plate supports38, and side plates40. The base extrusion34includes a base plate42, and side walls44.

The main arm assembly30includes a main arm46, a rear pivot mechanism48, a linkage assembly50, a latch system52, and a motion control device54. The main arm46is comprised of a bottom wall56, a top wall58, side walls60, rear pivot mechanism apertures62, and lower front apertures64. The rear pivot mechanism48includes a yoke66, rear pivot brackets68, rear pivot bushings70, a rear pivot pin72, and fasteners74. The linkage assembly50includes a leaf spring76, bushings77, a leaf spring stop78, an upper pin80, front side links82, linkage projections84, bushings86, a rope guide88, a rope hole90, a lower pin92, a torsion spring94, a safety latch96, and a washer98. The latch system52includes a rear latch assembly100, latch straps101, and a front latch assembly102. The rear latch assembly100includes a rear latch bracket104, a pivot pin106, e-clips108, and extension springs110. The front latch assembly102is comprised of a latch strap bracket112and a latch bar114. The motion control device54includes a bias mechanism116, a rear knurled pin118, a front pivot pin120, and fasteners122.

The motor coupling assembly32includes an upper cover124, an upper bushing126, an upper sleeve128, a spring130, a lower sleeve132, a lower bushing134, a lower cover136and a fastener138. The upper cover124includes an orifice140, recesses142, and tracks144.

A. Overview of the Exploded Assembly18

InFIG. 2, the base assembly28extends symmetrically from a front portion to a rear portion, and is adapted to be secured to a surface. The rear portion of the base assembly28pivotally couples with the main arm46via the rear pivot mechanism48. The open frame rigid main arm46extends from a rear portion coupled to the base assembly28to a front portion. The linkage assembly50is disposed adjacent to (and is pivotally coupled with) the front portion of the main arm46, and extends through the main arm46to pivotally couple to the rear pivot mechanism48. The linkage assembly50and the motor coupling assembly32are adapted to removably interconnect. The latch system52is disposed inside the frame of the main arm46and interconnects to the rear portion of the main arm46. The latch system52extends within the main arm46from the rear portion to the front portion where it engages the linkage assembly50. The main arm46is adapted to allow the front portion of the latch system52to releasably engage the base assembly28in the deployed position, and is adapted to allow the rear portion of the latch system52to releasably engage the rear pivot mechanism48in the stowed position. The motion control device54is disposed within the frame of the main arm46, and pivotally couples with the main arm46and the rear pivot mechanism48.

In the stowed position, the main arm46cantilevers rearward from the rear portion of the base assembly28. The linkage assembly50holds the motor coupling assembly32in a generally vertical position so that the trolling motor16is disposed generally horizontal to the gunnels. The latch system52releasably engages the rear pivot mechanism48.

Between the stowed position and the deployed position, the main arm46pivotally rotates relative to the base assembly28on the rear pivot mechanism48. The linkage assembly50actuates pivotal rotation of the motor coupling assembly32about the pivot coupling between the main arm46and the linkage assembly50. The linkage assembly50pivotally rotates the motor coupling assembly32from the generally vertical position when in the stowed position, to a generally horizontal position in the deployed position. The latch system52is actuated out of engagement with the base assembly28or the rear pivot mechanism48. The motion control device54assists, impedes, or biases the movement of the main arm46between the stowed position and the deployed position. The motion control device54actuates rotation of a portion of the rear pivot mechanism48.

In the deployed position, the main arm46is received in the U-shaped channel of the base assembly28. The linkage assembly50holds the motor coupling assembly32in a generally horizontal position. The latch system52releasably engages the front portion of the base assembly28.

B. Overview of the Exploded Base Assembly28

InFIG. 2, the base extrusion34is a U-shaped channel adapted to be secured to the surface(s) of the watercraft12. The motor ramp36is spade shaped interconnects to the front portion of the base extrusion34in a cantilevered fashion. The sides of the base extrusion34are adapted to secure to the side plate supports38and side plates40, which extend along the sides of the base extrusion34from the front to the rear. The side walls44of the base extrusion34extend generally vertically from the base plate42and are adapted to receive the main arm46between them when the main arm46is in the deployed position. The rear pivot mechanism48secures to the rear portion of the side walls44.

C. Overview of the Exploded Main Arm46

InFIG. 2, the bottom wall56, side walls60and top wall60interconnect to form the open frame of the main arm46. The walls56,58,60extend from the rear portion of the main arm46to the front portion. The rear portion of the side walls60are adapted to extend further rearward than the bottom wall56or the top wall60. This cantilevered rear portion is adapted with rear pivot mechanism apertures62, which allow the main arm46to rotatably receive the rear pivot mechanism48. The lower front apertures64rotatably receive the linkage assembly50.

D. Overview of the Exploded Rear Pivot Mechanism48

FIG. 2shows the major components of the rear pivot mechanism48including the yoke66. The yoke66is symmetrically disposed between the side walls44toward the rear portion of the base extrusion34. The yoke66couples with the motion control device54. The yoke66is adapted to receive a hub portion of the rear pivot brackets68and to pivotally rotate on this portion. The rear pivot bushings70interface with the rear pivot brackets68and with the edge of the rear pivot apertures62. The rear pivot brackets68have triangular rearward projections adapted to receive the rear pivot pin72. The fasteners74fix the rear pivot brackets68to the side walls44of the base extrusion34.

E. Overview of the Exploded Linkage Assembly50

InFIG. 2, the leaf spring76is adapted to receive the bushings77, which pivotally couple the leaf spring76to the rear pivot pin72. The leaf spring76extends through the interior of the main arm46from the rear end to the front end. In one embodiment, the central portion of the leaf spring76engages the leaf spring stop78when the main arm46is in the stowed position. The front portion of the leaf spring76is adapted to receive the bushings77, which pivotally couple the leaf spring76to the upper pin80.

The ends of the upper pin80extend into the front side links82. The linkage projections84on the outer side surface of the front side links82are adapted to interface and connect the motor coupling assembly32to the linkage assembly50. The bushings86receive the upper pin80and space the front side links82from the rope guide88. The rope guide88rotatably mounts to the upper pin80to either side of the leaf spring76and is adapted to receive the rope14via the rope hole90.

The front side links82and the rope guide88extend downward and forward to interconnect to the lower pin92. The lower pin92is received by the lower front apertures64of the main arm46. The lower pin92pivotally couples the linkage assembly50to the main arm46. In the front interior portion of the main arm46, the torsion spring94, safety latch96and washer98are configured to receive the lower pin92. The torsion spring94is configured to engage the lower portion of the rope guide88and the safety latch96.

F. Overview of the Exploded Latch System52

InFIG. 2, the latch system52is disposed within the main arm46. The rear latch assembly100is disposed toward the rear portion of the main arm46. The rear latch assembly100pivotally interconnects with the latch straps101, which extend forward to pivotally interconnect with the front latch assembly102. More specifically, the upper portion of the rear latch bracket104pivotally couples with the latch straps101. The lower portion the rear latch bracket104pivotally couples to the main arm46via the pivot pin106. The e-clips108are disposed on the pivot pin106interfacing the rear latch bracket104. The springs110interconnect the latch bracket104to the bottom surface56of the main arm46.

The latch straps101pivotally couple to the latch strap bracket112. The latch strap bracket112is configured to slottedly receive the lower pin92at the front portion of the main arm46. The latch strap bracket112is adapted to receive the rope14, which enters the front interior portion of the main arm46through the rope hole90in the rope guide88. The latch strap bracket112is adapted to securely receive and interconnect with the latch bar114, which extends symmetrically through the latch strap bracket112and the side walls60to releasably engage the front portion of the base extrusion34when the main arm46is in the deployed position.

G. Overview of the Exploded Motion Control Device54

FIG. 2illustrates the major components of the motion control device40including the bias mechanism116, which extends into the main arm46from the rear. The rear and front portions of the bias mechanism116are adapted to pivotally couple with the rear knurled pin118and the front pivot pin120. The rear knurled pin118couples the bias mechanism116to the yoke66. The front pivot pin120extends generally horizontally between the side walls60of the main arm46and couples the bias mechanism116to the main arm46. In one embodiment, the ends of the front pivot pin120may be treaded to securely receive fasteners122, which extend through the side walls60.

H. Overview of the Exploded Motor Coupling Assembly32

InFIG. 2, the upper cover124extends over and interfaces with the upper bushing126, and extends around and over a portion of the upper sleeve128. The upper sleeve128rotatably interfaces with the upper bushing126and the spring130. The spring130interfaces with the lower sleeve132. The lower sleeve132rotatably interfaces with the spring130and the lower bushing134and extends through the lower cover136. The lower cover136interconnects with the upper cover124. In one embodiment, the fastener138removably secures the motor coupling assembly32to the linkage assembly50. The sleeves128,132may be adapted to rotatably interface with and couple to the shaft22of the trolling motor16, which is inserted into the interior of the motor coupling assembly32through an orifice140in the upper cover124. In another embodiment of the motor coupling assembly32, the upper cover124may include the recesses142and/or the tracks144, which are adapted to interface with and secure the motor coupling assembly32to the front side links82.

3. The Base Assembly28

FIG. 3shows an exploded front perspective view of an embodiment the base assembly28, which includes the base extrusion34, the motor ramp36, the side plate supports38, and the side plates40. Additionally, the base assembly28includes motor ramp fasteners146, side plate support fasteners148, and side plate fasteners150.

InFIG. 3, the base extrusion34is a U-shaped channel adapted to be secured to surface(s) such as the gunnels. The motor ramp fasteners146secure the motor ramp36to the lower front portion of the base extrusion34. The side walls44run along the length of the base extrusion34. The side walls44are adapted to receive the side plate support fasteners148, which mount the side plate supports38to the side walls44. The side plate supports38are adapted to receive the side plate fasteners150, which mount the side plates40to the side plate supports38. The side plates40cover the side surfaces of the base extrusion34for cosmetic purposes.

FIGS. 4A to 4Cshow different views of an embodiment of the base extrusion34. In addition to the side walls44and the base plate42, the base extrusion34includes side plate support apertures152, pivot mechanism apertures154, slots156, front edges157, locking notches158, thru holes160, and motor ramp apertures162.

FIGS. 4A to 4Cshow the two spaced apart side walls44that extend generally vertically upward from the base plate42and extend generally parallel to one another along the edge of the base plate42. The side walls44define a recess capable of receiving the main arm46in the deployed position. In a one embodiment, the side walls44are configured with side plate support apertures152to receive the side plate support fasteners148, which mount the side plate supports38to the side walls44.

The countersunk pivot mechanism apertures154in the rear portion of the side walls44receive the fasteners74, which secure the rear pivot brackets68to the base extrusion34. Likewise, the slots156are configured to receive a projecting portion of the rear pivot brackets68. The slots156retain the rear pivot brackets68from pivotally rotating.

The diagonal front edges157of the side walls44interconnect the top edges of the side walls44with the locking notches158. In one embodiment, each locking notch158is disposed at a 7.5 degree angle to the base plate42. The lower edge of each locking notch158extends forward past the forward termination point of the front edges157. The lower edges of the locking notches158are configured to catch the latch bar114. The angle of the locking notches158draws the latch bar114into releasable engagement with the locking notches158when the main arm46is in the deployed position. In other embodiments, means including apertures, recesses, tabs, or slots may be used to engage the main arm46with the base assembly28.

InFIGS. 4A to 4C, the base plate42is generally flat for ease of mounting, and rectangular in shape. The base plate42extends from a rear end generally near the rear pivot mechanism48to a front end, which interconnects with the motor ramp36. The base plate42is configured with thru holes160, which receive fasteners that secure the trolling motor assembly10to the surface of the watercraft12. The motor ramp apertures162extend through the base plate42and receive the motor ramp fasteners146, which secure the motor ramp36to the base plate42.

FIGS. 5A and 5Bshow an embodiment of the motor ramp36, which includes a base interconnection portion164, apertures166and a motor engaging portion168.

The base interconnection portion164of the motor ramp36is adapted to be inserted on the front portion of the base plate42between the side walls44. The base interconnection portion164has apertures166, which align with the motor ramp apertures162when the motor ramp36is disposed on the base plate42. The motor ramp apertures162and the apertures166receive the motor ramp fasteners146, which secure the motor ramp36to the base plate42. In one embodiment, when the motor ramp36is disposed on the base plate42, the motor engaging portion168cantilevers off the front end of the base plate42and over the edge of the watercraft12. InFIGS. 5A and 5B, the motor engaging portion168is spade shaped with two angled surfaces connecting at one forward end point. The motor engaging portion168is adapted to rotate the propulsion unit24of the trolling motor16as the unit24comes into contact with the motor ramp36at a position between stow and deploy. The motor ramp36reduces the likelihood of contact between the propulsion unit24and the watercraft12.

4. The Main Arm Assembly30

FIG. 6is an exploded front perspective view of an embodiment of the main arm assembly30, which includes the main arm46, the rear pivot mechanism48, the linkage assembly50, the latch system52and the motion control device54.

A. The Main Arm46

FIGS. 7A to 7Dshow different views of an embodiment of the main arm46. In addition to the bottom wall56, the top wall58, the side walls60, the rear pivot mechanism apertures62, and the lower front apertures64, the main arm46includes a lower cutaway170, spring apertures172, a stop aperture174, a safety latch slot176, stop portions178, front latch slots180, latch thru holes182, motion control device thru holes184, and cutouts186.

InFIGS. 7A to 7D, the main arm46is a single piece extrusion with a rigid open frame comprised of four interconnected walls. In one embodiment, the main arm46is formed of a metallic such as aluminum. The main arm46is capable of housing most of the other components of the main arm assembly36. The bottom wall56is disposed below the top wall58when the main arm46is in the deployed position. The bottom wall56is generally rectangular and extends from a rear end adjacent the rear pivot mechanism48to a front end adjacent the motor coupling assembly32. The bottom wall56has a number of apertures.

The generally square shaped lower cutaway170extends through the rear portion of the bottom wall56and receives the yoke66. The rear portion of the bottom wall56extends to either side of the lower cutaway170and has spring apertures172, which receive the extension springs110. The extension springs110connect the rear latch assembly100to the main arm46. The threaded stop aperture174extends through the center middle portion of the bottom wall56. The stop aperture174receives a fastener, which secures the leaf spring stop78to the interior surface of the bottom wall56. The safety latch slot176extends into the front portion of the bottom wall56. The safety latch slot176is adapted to receive a portion of the safety latch96when the motor coupling assembly32is removed from the linkage assembly50.

The bottom wall56interconnects with a pair of generally rectangular shaped side walls60. The side walls60extend generally perpendicularly from the bottom wall56. The side walls60extend from the rear of the main arm46to the front. The rear portion of the side walls60are cantilevered off the end of the bottom wall56and the top wall58. The cantilevered portion has the rear pivot mechanism apertures62, which receive the rear pivot bushings70and rear pivot brackets68. In a one embodiment, the rear pivot mechanism apertures62are between about 1 inch and about 4 inches (about 25.4 mm and about 101.6 mm) in diameter. The pivot mechanism apertures62allow the main arm46to pivotally rotate about the stationary rear pivot brackets68.

The side walls60include features which allow the main arm46to couple with the linkage assembly50, the front latch assembly102, and the motion control device54. More specifically, in one embodiment the stop portion178of the upper top front edge of the side walls60is adapted to abuttably interface with the upper pin80when the main arm46is in the deployed position. The front latch slot180in the lower front portion of the sidewalls60is adapted to receive the latch bar114, which extends through the front latch slot180from the interior of the main arm46. The front latch slot180allows the latch bar114to releasably slide into and out of engagement with the locking notch158when the main arm46is in the deployed position. InFIGS. 7A to 7D, the side walls60are configured with latch thru holes182and motion control device thru holes184, which receive pins106and120to pivotally couple the rear latch assembly100and the motion control device54to the main arm46, respectively. In one embodiment, the latch thru holes182or motion control device thru holes184may be counter bored to receive the head of a fastener (such as fastener122), which allows the fastener head to be generally flush with the exterior surface of the side walls60. The lower front portion of the side walls60are configured with the lower front apertures64to receive the lower pin92, which pivotally couples the linkage assembly50to the main arm.46. In one embodiment, the side walls60have cutouts186separated by struts. The cutouts186allow the operator to view the interior components of the mount18, increase the cosmetic appeal of the mount18, and decrease the weight of the main arm46.

The side-walls60interconnect with the top wall58. As shown inFIG. 2, the top wall58is generally rectangular, and extends longitudinally from an end adjacent the rear pivot mechanism48to an end adjacent the motor coupling assembly32. The walls50,52,54surround and protect the interior components from damage during operation. The components that extend into or are located in the interior compartment56may include the leaf spring76, the rear latch assembly100, the front latch assembly102, and the motion control device54. In other embodiments of the invention, all or some of these components may be disposed outside the main arm46.

B. The Rear Pivot Mechanism48

FIG. 6shows an exploded front perspective view of the rear pivot mechanism48, which includes the yoke66, the rear pivot brackets68, the rear pivot bushings70, the rear pivot pin72, and the fasteners74. The rear pivot mechanism48is secured between the side walls44at the rear portion of the base extrusion46and pivotally couples the main arm46to the base extrusion46. The rear pivot mechanism48also pivotally couples the leaf spring76to the base extrusion46. In one embodiment, the rear pivot mechanism48allows the main arm46to be rotated approximately 177 degrees between the stowed position and the deployed position.

FIGS. 8A to 8Dshow an embodiment of the yoke66, which includes hub receiving portions186, yoke pivot apertures188, channels190, a base portion192, shaft receiving arms194and apertures196.

In one embodiment, the yoke66is symmetrically disposed between the side walls60toward the rear portion of the main arm46. The yoke66is configured with two symmetric hub receiving portions186having yoke pivot apertures188. The yoke pivot apertures188extend through the hub receiving portions186, and are adapted to rotatably receive a portion of the rear pivot brackets68. The yoke66is configured to allow the yoke pivot apertures188to align with the rear pivot apertures62when the main arm46is in the deployed position. The outer surfaces of two hub receiving portions186are adapted with channels190, which are capable of receiving the rear pivot bushings70. The base portion192of the yoke66contacts the base plate42when the main arm46is in the deployed position. The base portion192is adapted with two symmetric shaft receiving arms194, which contact the base plate42when the main arm46is in the deployed position. When the main arm46is in the stowed position, the shaft receiving arms194project generally vertically and are adapted to receive and retain the shaft22of the trolling motor16. The apertures196extend through the base portion192and receive the rear knurled pin118, which interconnects the yoke66with the motion control device54. In one embodiment, the motion control device54actuates pivotal rotation of the yoke66about an axis defined by the rear pivot brackets68during a portion of the rotation of the main arm46between the stowed position and the deployed position. In one embodiment, this rotation occurs when the main arm46is between the stowed position and about 90 degrees.

FIGS. 9A to 9Cshow an embodiment of the rear pivot brackets68, which include fins198, cylindrical hubs200, apertures202, keys204, rear apertures206, and retention apertures208.

In one embodiment, each rear pivot bracket68is disposed generally parallel to the other between hub receiving portions186of the yoke66, and each extends outward over the rear end of the base extrusion34. The fins198form the base of the rear pivot brackets68. The fins198interconnect with the cylindrical hubs200and taper rearward. The cylindrical hubs200allow the rear pivot brackets68to extend through the yoke pivot apertures188and the rear pivot mechanism apertures62such that the exterior surface of the cylindrical hubs200are roughly flush with the interior surface of the side walls44. In one embodiment, the circular projections138on the rear pivot brackets68(and the pivot apertures62,188) 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 arm46and the base assembly28increases the durability of the pivot coupling. The increased durability of the pivot coupling reduces the likelihood that the coupling may loosen and cause the mount18to rattle or make other unpleasant noises during operation of the watercraft12.

The cylindrical hubs200are adapted with threaded apertures202to receive the fasteners74, which fix the rear pivot brackets68to the base extrusion34. The keys204extend outward from the cylindrical hubs200. The keys204are adapted to fit into and engage with the slots156on the rear side walls44. The rear apertures206extend through the rearward tapered portion of the fins198. The rear apertures206receive the rear pivot pin72, which allows the leaf spring76to pivotally couple to the rear pivot mechanism48.

The fins198may be configured to retain the rear pivot pin72non-pivotally or pivotally. In the embodiment shown inFIG. 9C, the rear outward edge of the fin198is adapted with a threaded retention aperture208, which receives a fastener that engages the rear pivot pin72. The fastener retains the rear pivot pin72from pivotally rotating with the leaf spring76. The bushings77allow the leaf spring76to pivot on the stationary rear pivot pin72as the main arm46pivots on the rear pivot brackets68.

FIGS. 10A and 10Bshow an embodiment of the rear pivot bushing70, which includes a lip210and an interior projection212.

The split ring rear pivot bushings70are disposed in the rear pivot mechanism apertures62on the main arm46between the edge of the rear pivot mechanism apertures62and the cylindrical hubs200. More specifically, the annular lip210engages the outer surface of the side walls60. The interior projection212interfaces with the edge of the rear pivot mechanism apertures62and the annular cylindrical hubs200. The rear pivot bushing70allows the main arm46to be pivotally rotated relative to the stationary rear pivot bracket68.

FIG. 6shows an exploded front perspective view of the linkage assembly50, which includes the leaf spring76, the bushings77, the leaf spring stop78, the upper pin80, the front side links82, the linkage projections84, the bushings86, the rope guide88, the rope hole90, the lower pin92, the torsion spring94, the safety latch96, and the washer98. The linkage assembly50is disposed adjacent to (and pivotally couples with) the front portion of the main arm46, and extends through the main arm46to pivotally couple to the rear pivot mechanism48. The linkage assembly50and the motor coupling assembly32are adapted to removably interconnect.

FIGS. 11A and 11Bshow the leaf spring76, which includes a rear portion214, a rear aperture216, a member218, a front portion220, and a front aperture222.

The rear portion214is adapted with the rear aperture216to receive the rear pivot pin72and the bushings77, which pivotally couple the leaf spring76to the rear pivot mechanism48. The member218interconnects with the rear portion214and extends through the open frame of the main arm46. In one embodiment, the member218may flexibly bow to contact the leaf spring stop78when the main arm46is in the stowed position. The front portion220interconnects with the member218and is adapted with the front aperture222to receive the upper pin80and the bushings77, which pivotally couple the leaf spring76to the remainder of the linkage assembly50. The leaf spring76actuates pivotal rotation of the remainder of the linkage assembly50(and the motor coupling assembly32) about the pivot coupling between the main arm46and the linkage assembly50. The leaf spring76rotates the remainder of linkage assembly50(and the motor coupling assembly32) from the generally vertical position when in the stowed position, to the generally horizontal position in the deployed position.

FIG. 6shows the front side links82, which include the linkage projections84. The two front side links82receive the ends of the upper pin80and extend downward and forward generally parallel to each other to receive the lower pin92. More specifically, the longitudinally and vertically offset trapezoidal linkage projections84are adapted to receive the lower and upper pins80,92. The linkage projections84extend outwards from the exterior side surface of the front side links82. In one embodiment, the linkage projections84are selectively sized and geometrically disposed to interlock with the recesses142on the motor coupling assembly32.

FIGS. 12A and 12Bshow an embodiment of the rope guide88, which in addition to the rope hole90, includes an upper portion224, upper apertures226, lower members228, a motor coupling aperture230, and lower apertures232.

The upper portion224of the rope guide88is separated from the front side links82along the length of the upper pin80by the bushings86. The upper apertures226pivotally receive the upper pin80. The upper portion224is disposed symmetrically over the front portion220and extends down to receive the upper pin80to either side of the front portion220of the leaf spring76. The rope hole90extends downward through the upper portion224. The rope hole90is adapted to receive the rope14. The upper portion224extends forward and interconnects with the lower members228. The two lower members228extend downward generally parallel to each other to receive the lower pin92. In one embodiment, the threaded motor coupling aperture230receives the fastener138, which secures the motor coupling assembly32to the linkage assembly50. The lower apertures232receive the lower pin92, which allows the rope guide88to pivotally couple with the main arm46.

FIGS. 13A and 13Bshow front and side views of an embodiment of the safety latch96, which includes a main body234, an aperture236, a rearward nose238, and a forward nose240.

In one embodiment, the safety latch96is disposed on the lower pin92adjacent one of the lower members228. The cylindrical main body234surrounds the lower pin92. The aperture236pivotally receives the lower pin92. The rearward nose238extends from the main body234and engages the torsion spring94. The forward nose240extends from the main body234and engages the motor coupling assembly32when the motor coupling assembly32is mounted on the linkage assembly50. The torsion spring94engages the adjacent lower member228to bias the rearward nose238into the safety latch slot176when the motor coupling assembly32is not interconnected with the linkage assembly50.

FIG. 6shows an exploded front perspective view of the latch system52, which includes the rear latch assembly100, the latch straps101, and the front latch assembly102. The rear latch assembly100includes the rear latch bracket104, the pivot pin106, the e-clips108, and the extension springs110. The front latch assembly102is comprised of the latch strap bracket112and the latch bar114. The latch system52is configured to releasably engage with the base extrusion34to lock the main arm46in the deployed position, and to releasably engage with the rear pivot mechanism48to lock the main arm46in the stowed position. In one embodiment, the operator must actuate the latch system by pulling on the rope14before rotating the main arm46from either the stowed position or the deployed position. The latch system100protects against unintended and potentially harmful rotation of the main arm46.

FIGS. 14A and 14Bshow an embodiment of the rear latch bracket104, which includes side surfaces242, a member244, a cutout246, spring apertures248, pivot apertures250, notches252, and upper apertures254.

The rear latch bracket104has two symmetrical side surfaces242disposed generally parallel to each other. In one embodiment, the side surfaces242are disposed adjacent the interior surface of the side walls60. The side surfaces242are interconnected by the member244. The half circular cutout246extends symmetrically through the lower portion of the member244. The cutout246accommodates the barrel of the bias mechanism116when the main arm46is in the deployed position.

The spring apertures248on the lower rear portion of each side surface242receive the extension springs110, which connect the rear latch bracket104to the main arm46via the apertures172. The extension springs110bias the rear latch assembly100and the front latch assembly102into releasable engagement. To unlatch the rear latch assembly100and the front latch assembly102this bias must be overcome by the force of the operator's pull on the rope14. In one embodiment, the extension springs110have 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 apertures250are disposed through the lower rear of the side surfaces242and receive the pivot pin106, which pivotally couples the rear latch bracket104to the main arm46. In one embodiment, the side surfaces242are contacted by the e-clips108, which retain the rear latch bracket104symmetrically on the pivot pin106.

The notches252extend through rear edge side surfaces242and are configured to engage with the rear pivot pin72of the rear pivot mechanism48when the main arm46is in the stowed position. The notches252remain in engagement (biased by the extension springs110) with the rear pivot pin72in the stowed position until the rear latch assembly100is pivotally actuated out of engagement by the operator.

The upper apertures254receive fasteners, which pivotally couple the rear latch bracket104to the latch straps101. The latch straps101interconnect the rear latch bracket104with the latch strap bracket112(and the rear latch assembly100with the front latch assembly102). The latch straps101are adapted to pivotally couple to both the rear latch bracket104and latch strap bracket112. Thus, both the rear latch assembly100and the front latch assembly102may be actuated simultaneously by the pull of the rope14.

FIGS. 15A to 15Cshow an embodiment of the latch strap bracket112, which includes side walls256, a base platform258, thru holes260, square apertures262, slots264, an front wall266, a rope aperture270, and a groove projection272.

The latch strap bracket112is disposed in the interior of the main arm46adjacent the front end of the main arm46. The symmetrical side walls256of latch strap bracket112interconnect generally vertically with the base platform258. Thru holes260receive the fasteners, which pivotally couple the latch straps101to the latch strap bracket112. The square apertures262are adapted to receive the latch bar114, which extends outward to either side of the side walls256. The slots264receive the lower pin92, which allows the latch system52to be slidably linearly actuated into and out of engagement with the base extrusion34or the rear pivot mechanism48.

The front wall266interconnects to the side walls256. The rope aperture270extends through the front wall266and is adapted to receive the rope14, allowing the rope14to interconnect with the latch strap bracket112. This interconnection may occur, for example, by looping the rope14around the aperture270and then tying a knot, or by extending the rope14through the aperture270and then tying a knot that is larger than the rear side of the aperture270.

The groove projection272extends generally vertically from the central portion of the base platform258generally parallel with the side walls256. The groove projection272generally aligns horizontally with the square apertures262. The groove projection272engages the latch bar114and retains the latch bar114from side-to-side movement.

FIGS. 16A and 16Bshow an embodiment of the latch bar114, which includes a groove274and end portions276.

The latch bar114is 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 bar114extends through the latch strap bracket112from one side wall256to the other. The groove274extends across the center of the bottom surface of the latch bar114and engages the groove projection272. The end portions276of the latch bar114are rounded and extend from the side walls256through the slots132in the main arm46to engage the locking notches158in the base extrusion34when the main arm46is in the deployed position. The latch bar114remains in engagement (biased by the extension springs110) with the locking notches158in the deployed position until the front latch assembly102is actuated by the operator. By applying a pulling force to the rope14the operator causes the latch strap bracket112to slide forward moving the latch bar114out of engagement with the locking notches158.

E. The Motion Control Device54

FIG. 6shows an exploded front perspective view of the motion control device54, which includes the bias mechanism116, the rear knurled pin118, the front pivot pin120, and fasteners122. The motion control device54pivotally couples with the main arm46and extends within the main arm46to pivotally couple with the rear pivot mechanism48. The motion control device54may be configured to assist, impede, or otherwise bias the movement of the main arm46from the stowed position to the deployed position. In one embodiment, the motion control device54is configured to assist the operator when the main arm46rotates 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 device54from the deployed position to about 90 degrees. In another one embodiment, the motion control device54is configured to impede the rotate of the main arm46through 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 device54from about 90 degrees to the deployed position. The motion control device54may be configured to exert biasing forces (whether assisting or impeding) on the main arm46during other portions of the rotation path of the main arm46between the stowed position and the deployed position in other embodiments of the invention.

FIGS. 17A and 17Bshow an embodiment of the bias mechanism116, which includes a rear portion278, a rear aperture280, a main body282, a front portion284, and a front aperture286.

The rear portion178has the rear aperture280, which extends through it. The rear aperture280receives the rear knurled pin118, which allows the bias mechanism116to the pivotally couple with the rear pivot mechanism48. The main body282interconnects with the rear portion278, and in the embodiment shown is extendable and retractable from the rear portion278. In one embodiment, the main body282is extendable and retractable only during a portion of the rotation of the main arm46between the stowed position and the deployed position. In one embodiment, the bias mechanism116exerts its biasing force on the main arm46only during the extendable or retractable movement of the main body282. The main body282interconnects with the front portion284. The front aperture286extends through the front portion284. The front aperture284receives the front pivot pin120, which allows the bias mechanism116to pivotally couple with the main arm46. In one embodiment, the front pivot pin120is fixed to the main arm46by the fasteners122.

In one embodiment, the bias mechanism116is a gas spring that provides assistance or resistance to the main arm46. According to an exemplary embodiment, the device40is 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 Assembly32

FIG. 18shows an embodiment of the motor coupling assembly32, which includes the upper cover124, the upper bushing126, the upper sleeve128, the spring130, the lower sleeve132, the lower bushing134, the lower cover136and the fastener138. Additionally, the lower cover132includes a second orifice287, and the upper cover128includes an aperture288. The motor coupling assembly32is removable from the linkage assembly50and the remainder of the mount18and is configured to couple with, retain, and guide the shaft22of the trolling motor16.

InFIG. 18, the upper cover124extends over and interfaces with the upper bushing126, and extends around and over the lower portion of the upper sleeve128. The upper sleeve128rotatably interfaces against and aligns with the upper bushing126and the spring130. The upper sleeve128rotatably couples with the shaft22of the trolling motor16when the shaft22is inserted in the assembly32. In one embodiment, the upper sleeve128may be configured to selectively tighten and loosen on the: shaft22.

The spring130aligns with and interfaces against both the upper sleeve128and the lower sleeve132. The spring130protects and absorbs some of the shock incurred during operation of the trolling motor16. The lower sleeve132aligns with and rotatably interfaces against the spring130and the lower bushing134. The lower sleeve132rotatably couples with the shaft22of the trolling motor16. In one embodiment, the lower sleeve132may be configured to selectively tighten and loosen on the shaft22.

The lower cover136interconnects with and is fastened to the upper cover124to surround the interior components. The orifices140,287in the upper and lower covers124,136vertically align. The other components including the upper bushing126, the upper sleeve128, the spring130, the lower sleeve132, the lower bushing134also vertically align with the orifices140,287. The aligned components allow the second orifice287to receive the shaft22of the trolling motor16.

In one embodiment, the fastener138may be received by the aperture288, which aligns with the motor coupling aperture230. In one embodiment, the fastener138threads into the motor coupling aperture230to removably secure the motor coupling assembly32to the linkage assembly50. Alternatively, (or in addition to the fastener138) the upper cover124may include the recesses142and/or the tracks144adapted to interface with and mount the motor coupling assembly32to the front side links82.

6. The Mounting of the Motor Coupling Assembly32

FIG. 19shows the mount18and the features that allow the motor coupling assembly32to be removable from the linkage assembly50and the mount18. These features and components include the front side links82, the linkage projections84, the fastener138, the recesses.142and the tracks144. These features and components allow the motor coupling assembly32to be quickly disconnected from or connected to the linkage assembly50and the mount18.

InFIG. 19, the motor coupling assembly32is adapted with the single aperture288which receives the single fastener138. The fastener138passes through the aperture288and engages the motor coupling aperture230in the rope guide88to connect the motor coupling assembly32to the linkage assembly50and the mount18. Because conventional linkages between the trolling motor and the mount utilize multiple fasteners, the single fastener138allows the operator to more quickly and easily remove or connect the motor coupling assembly32to or from the mount18. In one embodiment, the fastener138is the only means used to interconnect the motor coupling assembly32with the linkage assembly50.

By locating the rope hole90in the rope guide88, the motor coupling assembly32and trolling motor16can be quickly and easily disconnected from or connected to the mount18when 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's main arms before the motor coupling assembly and the trolling motor can be removed from the remainder of the mount.

InFIG. 19, the fastener138is not the only means of interconnecting the motor coupling assembly32to the linkage assembly50. InFIG. 19, the fastener138is supplemented by the upper cover124and the front side links82, which are configured to interlock using male and female surface profiles. In the embodiment shown inFIG. 19, the interior surface of the upper cover124has longitudinally and vertically offset recesses142. The symmetry of the recesses142is mirrored by longitudinally and vertically offset trapezoidal linkage projections84, which extend outwards from the side surfaces of the front side links82.

The linkage projections84are selectively sized to interlock with the recesses142. The linkage projections84and the recesses142interlock to retain the motor coupling assembly32from side-to-side or vertical motion when the motor coupling assembly32is interconnected to the linkage assembly50. In other embodiments of the invention, the male and female interlocking surface profiles may be the only means of retaining the motor coupling assembly32and connecting the assembly58to the mount18. In other embodiments, the male profile may be on the motor coupling assembly32and the female profile may be on the front side links82. The male/female interlocking profiles allow the operator to quickly remove or connect the motor coupling assembly32to or from the mount18.

InFIG. 19, the interior side surfaces of the upper cover124may have generally vertical depressed surfaces that form the tracks144. The tracks144may be used to guide the upper rear linkage projections84into interlocking contact with the recesses142. Thus, to connect the motor coupling assembly32to the front side links82, the motor coupling assembly32must initially be disposed above the front side links82. The upper rear linkage projections84are aligned with the tracks144. The motor coupling assembly32is moved vertically downwards toward the front side links82until the upper rear linkage projections84contact the tracks144. The tracks144guide the linkage projections84into interlocking contact with the recesses142as the motor coupling assembly32is moved downwards onto the front side links82. The process is reversed to remove the motor coupling assembly32from the front side links82.

7. The Assembled Rear Pivot Mechanism48

FIG. 19shows the assembled rear pivot mechanism48disposed at the rear of the base assembly28and main arm assembly30. InFIG. 19, the main arm assembly30is shown in the deployed position.

In the deployed position, the base portion192of the yoke66contacts the base plate42. The yoke66is disposed symmetrically between the side walls44. The yoke66receives the cylindrical hubs200of the rear pivot bracket68. The yoke66is configured to pivotally rotate on the cylindrical hubs200of the rear pivot brackets68. The rear pivot bushings70interface the outer annular surface of the cylindrical hubs200and the circular edge of the rear pivot apertures62. The rear pivot bushings70allow the main arm46to pivot relative to the fixed rear pivot brackets68between the stowed position and the deployed position.

The fasteners74(received by the pivot mechanism apertures154and threaded into the apertures202in rear pivot bracket68) and slot projection204secure the rear pivot brackets68in a stationary position to the side walls44of the base extrusion34. The two rear pivot brackets68cantilever rearward off the rear end of the side walls44generally parallel to one another, and receive the rear pivot pin72. The rear portion214of the leaf spring76pivotally couples to the rear pivot pin72between the rear pivot brackets68.

8. The Operation of the Latching System52

FIG. 19shows the latch bar114extending from the side surfaces60of the main arm46to releasably engage the locking notches158. While the first arm46is in the deployed position the latch bar114remains in locked releasable engagement with the locking notches158until the operator actuates the latching system52forward by pulling on the rope14. As will be discussed in greater detail subsequently, while the motor coupling assembly32is removed from the linkage assembly50(as shown inFIG. 19) the latching system52cannot be actuated by the operator's pulling on the rope14. InFIG. 19, the rope14enters the interior of the linkage assembly50via the rope hole90.

InFIG. 20, the rope14is shown entering the interior of the linkage assembly50, which is engaged with the motor coupling assembly32. The rope14extends generally vertically downward between the lower members228of the rope guide88. The rope14wraps over the front facing portion of the lower pin92before entering the interior compartment of the main arm46to connect generally horizontally to the latch strap bracket112.

FIG. 20shows the “latch system lockout,” which includes the torsion spring94and safety latch96. InFIG. 20, the motor coupling assembly32is mounted on the linkage assembly50, and the safety latch96is disposed on the lower pin92adjacent one of the lower members228. Because the motor coupling assembly32is mounted on the linkage assembly50, the rearward nose238of the safety latch96engages the torsion spring94and points generally rearward in a raised position. InFIG. 20, the forward nose240engages the motor coupling assembly.32and points generally forward. The torsion spring94engages the adjacent lower member228and the rearward nose238to bias the safety latch96. If the motor coupling assembly32was not mounted to the linkage assembly50and engaging the forward nose240, the safety latch96would rotate downward to dispose the rearward nose238in the safety latch slot176. While received in the safety latch slot176, the rearward nose238interferes with the sliding movement of the latch strap bracket112so that the main arm46cannot be unlatched from either the stowed position or the deployed position.

FIG. 21Ashows the components of the latching system52in the deployed position with the base assembly28and main arm46suppressed (i.e. not shown). InFIG. 21A, the rope14generally horizontally interconnects with the latch strap bracket112. The slots264engage the lower pin92to transfer the pulling motion that the operator exerts on the rope14to a generally horizontal linear motion. When the main arm46is in the deployed position and the operator has not actuated the rope14, the extension springs110bias the latch bar114into engagement with the locking notches158. When actuated, the horizontal (relative to the deck of the watercraft12) linear motion of the rope14overcomes the bias of the extension springs110to unlock the front latch assembly102by disengaging the latch bar114from the locking notches158on the base extrusion34.

FIG. 21Bshows the components of the latching system52in the stowed position. In this position, the rear latch bracket104notches252engage the rear pivot pin72. The locking notches98remain in engagement (biased by the extension springs110) with the rear pivot pin72in the stowed position until the rear latch assembly100is pivotally actuated out of engagement by the operator. The rear latch assembly100may be actuated out of engagement by a pull of the rope14; which slides the front latch assembly102forward. The sliding motion of the front latch assembly102pulls the latch straps101forward. The latch straps101pivotally couple to the rear latch bracket104. The rear latch assembly100is pulled pivotally forward out of engagement with the rear pivot pin72by the latch straps101.

9. The Operation of the Linkage Assembly50

FIGS. 21A and 21Bshow the linkage assembly50with the main arm46and base assembly28suppressed (i.e. not shown). InFIG. 21A, the linkage assembly50is shown in the deployed position. In this position, the upper pin80couples the leaf spring76to the remainder of the linkage assembly50. 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 assembly50excluding the leaf spring76and the bushings77. The front portion of the linkage assembly50is configured to pivotally couple with the main arm46via the lower pin92. The leaf spring76and the main arm46are configured to place the upper pin80into interference with the stop portions178of the main arm46when the main arm46is in the deployed position. In the deployed position, the main arm46and the rear pivot mechanism48are configured to place the leaf spring76in tension. This tension force causes the leaf spring76to exert a resistive force moment on the linkage assembly50. The force moment actuates the interference engagement between the linkage assembly50and the main arm46, and impedes the rotation of the front portion of the linkage assembly50out of the interference engagement (and the motor coupling assembly32out of the generally horizontal position). The force moment generated by the leaf spring76reduces play at the coupling joint between the linkage assembly50and the main arm46. The reduction in joint play reduces the likelihood of vibratory noise when the mount18is in the deployed position.

In another embodiment, the leaf spring76and/or the main arm46may be selectively configured to position the linkage assembly52(and the motor coupling assembly32) in a position other than the one shown inFIG. 21A. The leaf spring76actuates pivotal rotation of the linkage assembly50about an axis defined by the lower pin92as the main arm46rotates between the stowed position and the deployed position.

InFIG. 21B, the linkage assembly50is shown in the stowed position. In addition to the main arm46and base assembly28, the guide member68has also been suppressed to better show the leaf spring76. In the stowed position, the front portion of the linkage assembly50(and the motor coupling assembly32) is rotated to the generally vertical position shown. The leaf spring76actuates the pivotal rotation of the front portion of the linkage assembly50from the interference engagement when the mount18is in the deployed position, to the generally vertical position when the mount18is in the stowed position. In the stowed position, the upper pin80which couples the front portion of the linkage assembly50to the front portion214of the leaf spring76is now disposed near the lower rear portion of the mount18. In the stowed position, the main arm46and the rear pivot mechanism48are configured to place the leaf spring76in compression. This compressive force causes the leaf spring76to exert a resistive force moment on the remainder of the linkage assembly50. This force moment holds the motor coupling assembly32in the generally vertical position shown while the mount18remains in the stowed position. The force moment impedes rotation of the front portion of the linkage assembly50(and the motor coupling assembly32) out of the generally vertical position. The force moment generated by the leaf spring76reduces play at the coupling joint between the linkage assembly50and the main arm46. The reduction in joint play reduces vibratory noise when the mount18is in the stowed position.

In other embodiments, the leaf spring76and/or the main arm46may be selectively configured to position the front portion of the linkage assembly50(and the motor coupling assembly32) in a position other than the generally vertical position. In one embodiment, the position of the linkage assembly50in the stowed position may be determined by the leaf spring stop78, which acts as a spacer to halt the rotation of the leaf spring76inside the main arm46. In another embodiment, the leaf spring stop78may retain the leaf spring76from flexibly bowing when the main arm46is in the stowed position. In another embodiment of the invention, the leaf spring76and/or the leaf spring stop78may be disposed outside the interior compartment56of the main arm46.

10. The Operation of the Motion Control Device54

FIGS. 21A and 21Bshow the motion control device54, which extends forward from the rear pivot mechanism48toward the motor coupling assembly32. InFIG. 21A, the bias mechanism116pivotally couples to the yoke66via the rear knurled pin118. The bias mechanism116extends forward from the yoke66to pivotally couple with the front pivot pin120. InFIG. 21Athe bias mechanism116is retracted.

In one embodiment, the bias mechanism116rotates with the movement of the main arm46from the deployed position shown inFIG. 21Ato the stowed position shown inFIG. 21B. In one embodiment, the bias mechanism116extends for a portion of the movement of the main arm46from the deployed position to the stowed position. In one embodiment, the extension of the bias mechanism116aids the operator in lifting and rotating the main arm46. As the main arm46reaches about 90 degrees, the bias mechanism116becomes fully extended and no longer exerts a biasing force on the main arm46. After the bias mechanism116becomes fully extended the bias mechanism116actuates rotation of the yoke66, which is configured to pivotally rotate on a portion of the rear pivot brackets68. In one embodiment, when the yoke66is not contacting the base plate42, the bias mechanism116exerts no biasing force on the main arm46.

In the stowed position shown inFIG. 21B, the yoke66is not in contact with the base plate42, and the receiving members194of the yoke66extend generally vertically. As the main arm46begins to rotate from the stowed position to the deployed position, the bias mechanism116actuates rotation of the yoke66downward toward the base plate42. In one embodiment, the bias mechanism116begins to retract and exert a biasing force on the main arm46when the base of the yoke66with the receiving members194contacts the base plate42. In another embodiment, the retraction of the bias mechanism116exerts a resistive force on the main arm46. The bias mechanism116continues to exert the biasing force while retracting. In one embodiment, the yoke66remains in contact with the base plate42and the bias mechanism116continues to exert the biasing force from about 90 degrees to the deployed position.

11. The Operation of the Rear Pivot Mechanism48

FIGS. 21A and 21Bshow the rear pivot mechanism48in the stowed position and the deployed position, viewed from the same perspective. InFIG. 21Athe receiving members194of the yoke66are in horizontal contact with the base plate42, and the yoke66is configured to pivotally rotate about and axis defined by the rear pivot brackets68. As main arm46rotates from the deployed position inFIG. 21A, to the stowed position inFIG. 21B, the receiving members194pivotally rotate upward off the base plate42. The pivotal rotation of the yoke66is actuated by the motion control device54. InFIG. 21B, the receiving members194of the yoke66extend generally vertically to receive the shaft22of the trolling motor16. InFIGS. 21A and 21B, the rear pivot brackets68remain in a stationary position fixed to the base extrusion34. The annular portion of the rear pivot brackets68interface with the rear pivot bushings70, which allows the main arm46to pivotally rotate from the deployed position to the stowed position. The rear pivot brackets68retain the rear pivot pin72, which pivotally couples the leaf spring76to the rear pivot brackets68.

12. The Overall Assembly18

FIG. 22further illustrates the disposition of some of the components of the motor coupling assembly32, the rear pivot mechanism48, the linkage assembly50, the latching system52, and the motion control device54, when the main arm46is in the deployed position. InFIG. 22, the side plates40, main arm46, and leaf spring76are suppressed (i.e. not shown).

InFIG. 22, the motor coupling assembly32is mounted to the front portion of the linkage assembly50. The front latch assembly102is slightly disengaged from the locking notches158. More specifically, the latch strap bracket112has been slidably actuated forward on the slots264around the lower pin92such that the latch bar114is not in full engaging contact with the locking notches158.

FIG. 22also shows some of the improvements to the mount18. One of these improvements is the large diameter of the rear pivot mechanism48, which increases the durability of the pivot coupling between the main arm46and the base assembly28. More specifically, in one embodiment of the invention, the hub receiving portions186of the yoke66, the cylindrical hubs200of the rear pivot bracket68, the rear pivot bushings70, and the rear pivot mechanism apertures62of the main arm46may 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 arm46and the base assembly28. 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 arm46and the base assembly28increases the durability of the pivot coupling. The increased durability of the pivot coupling reduces the likelihood that the coupling may loosen and cause the mount18to rattle or make other unpleasant noises during operation of the watercraft12.

FIG. 22also shows the improved interconnection between the motor coupling assembly32and the linkage assembly50. By locating the rope hole90in the rope guide88, the motor coupling assembly32and trolling motor16can be quickly and easily disconnected from or connected to the linkage assembly50via the single fastener138and/or the recesses142and/or the tracks144. 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'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. 23shows the rotation of the of the main arm assembly30, the motor coupling assembly32and the yoke66as the main arm46rotates between the stowed position and the deployed position.FIG. 23shows some of the improvements to the mount18. The rigid open frame main arm46provides durable light weight protection for the other components of the main arm assembly30.

The leaf spring76is one component of the main arm assembly30which extends within the open frame of the main arm46. The leaf spring76provides smooth constant rotational actuation force to the remainder of the linkage assembly50as the main arm46rotates between the stowed position and the deployed position. The remainder of the linkage assembly50interconnects with motor coupling assembly32to provide the motor coupling assembly32with smooth constant pivotal rotation between the stowed position and the deployed position. In the deployed position and the stowed position, the leaf spring76exerts “down pressure” (from the force moment it exerts) on the remainder of the linkage assembly50(and motor coupling assembly32). This “down pressure” reduces play at the coupling joint between the linkage assembly50and the main arm46. The reduction in joint play reduces the likelihood of vibratory noise when the mount18is 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.