Patent Publication Number: US-11046411-B2

Title: Tiller assembly for a marine outboard engine

Description:
CROSS-REFERENCE 
     The present application claims priority to U.S. Provisional Patent Application No. 62/772,429, filed Nov. 28, 2018, the entirety of which is incorporated herein by reference. 
    
    
     TECHNICAL FIELD 
     The present technology relates to tiller assemblies for marine outboard engines. 
     BACKGROUND 
     Some marine outboard engines are provided with a tiller arm with which the marine outboard engine is steerable. At least some tiller arms are pivotable about a horizontal axis with respect to the marine outboard engine so as to allow the tiller arm to be raised or lowered to a comfortable height for the driver. This tiller arm adjustment is typically independent of the marine outboard engine&#39;s steering with respect to the swivel bracket about a vertical steering axis and independent of the marine outboard engine&#39;s tilting/trimming with respect to the stern bracket about a horizontal tilt-trim axis. Various mechanisms exist for setting and keeping a tiller arm at a desired angle with respect to the marine outboard engine. 
     For example, it is common to use a bolt that extends through the tiller arm and tiller arm base as an axle about which the tiller arm pivots. Tightening a nut at the end of the bolt creates sufficient friction in the tiller assembly to lock the tiller arm at the desired angle. A downside of such a conventional bolted tiller assembly is that the clamping force provided by the bolt is effectively all-or-nothing in that it is challenging, and at least in some cases impossible, to manually tighten the bolt just enough to resist gravity and the normal shocks, loads and vibrations to which a tiller arm may be subjected to when the watercraft to which it is mounted is underway, while remaining repositionable manually. 
     Also, such bolted tiller assemblies typically require tools to tighten/untighten the bolt, making changing the locked position of the tiller arm inconvenient. 
     Other, more easily adjustable tiller assemblies exist. Some such tiller assemblies use a spring loaded positive locking mechanism with a retractable spring-loaded pin (or a similar element) on one of the tiller arm and the base to selectively engage one of a plurality of recesses on the other of the tiller arm and the base to lock the tiller arm in one of a plurality of a given number of pre-defined angular positions. Such systems are adjustable without tools but provide a limited number of possible tiller arm positions. 
     It is also known to provide an adjustable stopper on a base beneath the tiller arm that sets a lower position of the tiller arm. In such prior art tiller assemblies, the tiller arm remains loose (not locked) during operation, and rests on the stopper. The stopper can be raised or lowered to set the lower position of the tiller arm. However, in at least some cases, adjusting the position of the stopper can be awkward when the outboard marine engine is in use. 
     In summary, prior art tiller assemblies are suitable for their intended purposes. However, there remains a need for a tiller assembly that enables convenient positioning and repositioning of the tiller arm before, during and after use. 
     SUMMARY 
     It is an object of the present technology to ameliorate at least some of the inconveniences present in the prior art. 
     According to one aspect of the present technology, there is provided a tiller assembly for a marine outboard engine. The tiller assembly includes a base adapted to pivot relative to a steering axis of the marine outboard engine and defining an axis of rotation that is perpendicular to the steering axis, and a tiller arm pivotably connected to the base to pivot relative to the base about the axis of rotation for adjusting an angular position of the tiller arm relative to the base. One of the base and the tiller arm defines a recess. The recess is coaxial with the axis of rotation and is at least partially defined by a female tapered surface. 
     The tiller assembly further includes a shaft extending through the base and the tiller arm. The shaft extends through the recess, defines the axis of rotation, and has a first threaded portion. The tiller assembly yet further includes a clamping fitting and a handle. The clamping fitting is connected to the shaft and received at least in part in the recess. The clamping fitting is rotationally fixed relative to another one of the base and the tiller arm and has a male tapered surface received at least in part in the recess. At least one of the handle and the clamping fitting has a second threaded portion engaged with the first threaded portion. Rotation of the first threaded portion relative to the second threaded portion in a pre-determined direction causes the male tapered surface of the clamping fitting to press against the female tapered surface of the recess. 
     In some embodiments, the other one of the base and the tiller arm defines a plurality of first splines disposed circumferentially about the axis of rotation, and the clamping fitting has a plurality of second splines engaging the plurality of first splines. 
     In some embodiments, the tiller assembly further comprises at least one resilient member arranged in compression so as to press the male tapered surface of the clamping fitting against the female tapered surface of the recess. 
     In some embodiments, the at least one resilient member is arranged in compression between: a) one of the handle and the shaft, and b) one of the base and the tiller arm, so as to push the male tapered surface of the clamping fitting against the female tapered surface of the recess. 
     In some embodiments, the at least one resilient member is disposed between the handle and the clamping fitting. 
     In some embodiments, the at least one resilient member includes at least one spring washer defining an axial aperture therein and receiving the shaft through the axial aperture. 
     In some embodiments, the handle is coaxial with the axis of rotation of the tiller arm. 
     In some embodiments, the clamping fitting has the second threaded portion; the female tapered surface of the recess faces away from the handle; and the rotation of the first threaded portion relative to the second threaded portion in the pre-determined direction causes the shaft to rotate in the pre-determined direction about the axis of rotation and to thereby press the male tapered surface of the clamping fitting toward the handle against the female tapered surface of the recess. 
     In some embodiments, the recess has a cylindrical portion and a frusto-conical portion; the cylindrical portion and the frusto-conical portion are coaxial with the axis of rotation; and the frusto-conical portion extends and narrows from the cylindrical portion toward the handle. 
     In some embodiments, the recess is a first recess defined in a portion of the base; the clamping fitting is a first clamping fitting; the base defines a second recess in the portion of the base opposite the first recess, the second recess having a cylindrical portion and a female tapered surface that are coaxial with the axis of rotation, the female tapered surface of the second recess extending and narrowing from the cylindrical portion of the second recess toward the first recess; the tiller arm defines the plurality of first splines and a plurality of third splines disposed circumferentially about the axis of rotation; and the tiller assembly further includes a second clamping fitting, the second clamping fitting slidably engaging the shaft and comprising a male tapered surface and a plurality of fourth splines disposed circumferentially about the axis of rotation, the second clamping fitting being received at least in part in the second recess, the male tapered surface of the second clamping fitting pressing against the female tapered surface of the second recess, the plurality of fourth splines of the second clamping fitting engaging the plurality of third splines of the tiller arm. 
     In some embodiments, the tiller arm defines a first arm at a rear end of the tiller arm, the first arm defining a first aperture coaxially with the axis of rotation, the first aperture comprising the plurality of first splines therein; the tiller arm defines a second arm at the rear end of the tiller arm, the second arm defining a second aperture coaxially with the axis of rotation, the second aperture comprising the plurality of third splines therein; the first and second clamping fittings are slidable relative to the tiller arm along the axis of rotation and are rotationally fixed relative to the tiller arm; and the portion of the base defining the first and second recesses therein is received between the first arm and the second arm. 
     In some embodiments, the second clamping fitting is disposed between the first clamping fitting and the handle; the tiller assembly further includes at least one resilient member disposed between the handle and the second clamping fitting; and the handle presses the at least one resilient member against the second clamping fitting. 
     In some embodiments, the at least one resilient member includes at least one spring washer defining an axial aperture therein and receiving the shaft through the axial aperture. 
     In some embodiments, the handle has the second threaded portion; the clamping fitting is rotationally fixed relative to the shaft; and the handle is rotatable relative to the shaft in the pre-determined direction, the handle rotating relative to the shaft in the pre-determined direction causing the first threaded portion to operate against the second threaded portion to thereby press the handle against the resilient member, the resilient member thereby pressing against the second clamping fitting. 
     In some embodiments, the male tapered surface of the clamping fitting and the female tapered surface of the recess each have a smooth frusto-conical surface. 
     In some embodiments, the frusto-conical surfaces of the clamping fitting and the recess define an angle with the axis of rotation, the angle being between 7 degrees and 45 degrees. 
     In some embodiments, the angle is between 14 and 16 degrees. 
     In some embodiments, the angle is approximately 15 degrees. 
     In some embodiments, the tiller arm has a longitudinal axis and the axis of rotation is perpendicular to both the longitudinal axis and the steering axis. 
     In another aspect, the present technology provides a marine outboard engine. In some embodiments, the marine outboard engine includes: a stern bracket attachable to a watercraft; a swivel bracket pivotably connected to the stern bracket to pivot relative to the stern bracket about a tilt/trim axis; a drive unit pivotably connected to the swivel bracket for pivoting with the swivel bracket about the tilt/trim axis and for pivoting relative to the swivel bracket about the steering axis; and the tiller assembly as described herein above. In some such embodiments, the base of the tiller assembly is attached to the drive unit for pivoting the drive unit about the steering axis. 
     In yet another aspect, the present technology provides a tiller assembly kit for a marine outboard engine. In some embodiments, the tiller assembly kit includes: a base for being connected to the marine outboard engine to pivot relative to a steering axis of the marine outboard engine, the base defining an axis of rotation that is perpendicular to the steering axis when the base is connected to the marine outboard engine; and a tiller arm for being pivotably connected to the base to pivot relative to the base about an axis of rotation for adjusting an angular position of the tiller arm relative to the base, the axis of rotation being perpendicular to the steering axis when the tiller assembly kit is assembled and attached to the marine outboard engine. 
     In some embodiments, one of the base and the tiller arm defines a recess, the recess being coaxial with the axis of rotation when the tiller assembly kit is assembled and being at least partially defined by a female tapered surface. 
     In some embodiments, the tiller assembly kit further includes: a shaft for being received through the base and the tiller arm and for extending through the recess, the shaft having a first threaded portion; a clamping fitting for being connected to the shaft and for being received at least in part in the recess, the clamping fitting being adapted to be rotationally fixed relative to another one of the base and the tiller arm when the tiller assembly kit is assembled, the clamping fitting having a male tapered surface shaped to be received at least in part in the recess when the tiller assembly kit is assembled; and a handle adapted to be connected to the shaft, at least one of the handle and the clamping fitting having a second threaded portion, wherein when the tiller assembly kit is assembled, rotation of the first threaded portion relative to the second threaded portion in a pre-determined direction causes the male tapered surface of the clamping fitting to press against the female tapered surface of the recess. 
     In some embodiments, the handle, the female tapered surface, and the male tapered surface are adapted to be coaxial with the axis of rotation of the tiller arm when the tiller assembly kit is assembled. 
     In some embodiments of the tiller assembly kit: the other one of the base and the tiller arm defines a plurality of first splines disposed circumferentially about the axis of rotation; the clamping fitting has the second threaded portion and a plurality of second splines engaging the plurality of first splines; the female tapered surface of the recess is oriented to face away from the handle when the tiller assembly kit is assembled; and the handle is adapted for, when the tiller assembly kit is assembled, rotating the shaft in the pre-determined direction about the axis of rotation to thereby press the male tapered surface against the female tapered surface. 
     In some embodiments of the tiller assembly kit: the recess is a first recess defined in a portion of the base, the first recess having a cylindrical portion and a female frusto-conical portion, the cylindrical portion and the female frusto-conical portion being coaxial with the axis of rotation and the female frusto-conical portion extending and narrowing from the cylindrical portion toward the handle when the tiller assembly kit is assembled; the clamping fitting is a first clamping fitting, the first clamping fitting having a plurality of first splines disposed circumferentially about the axis of rotation when the tiller assembly kit is assembled; and the base defines a second recess in the portion of the base opposite the first recess, the second recess having a cylindrical portion and a female frusto-conical portion, the cylindrical portion and the female frusto-conical portion of the second recess being coaxial with the axis of rotation and the female frusto-conical portion of the second recess extending and narrowing from the cylindrical portion of the second recess toward the first recess when the tiller assembly kit is assembled. 
     In some such embodiments, the tiller assembly kit further includes a second clamping fitting, the second clamping fitting being for slidably engaging the shaft and comprising a male tapered surface and a plurality of second splines, the male tapered surface of the second clamping fitting being shaped to be received at least in part in the second recess when the tiller assembly kit is assembled. In some such embodiments, the tiller arm defines: a plurality of third splines for engaging the plurality of first splines of the first clamping fitting when the tiller assembly kit is assembled, and a plurality of fourth splines for engaging the plurality of second splines of the second clamping fitting when the tiller assembly kit is assembled. 
     In some embodiments, the tiller arm defines a first arm at a rear end of the tiller arm, the first arm defining a first aperture coaxial with the axis of rotation when the tiller assembly kit is assembled, the first aperture comprising the plurality of third splines therein; the tiller arm defines a second arm at the rear end of the tiller arm, the second arm defining a second aperture coaxial with the axis of rotation when the tiller assembly kit is assembled, the second aperture comprising the plurality of fourth splines therein; the first and second clamping fittings are shaped to be received at least in part in respective ones of the first and second apertures so as to be slidable relative to the tiller arm along the axis of rotation and to be rotationally fixed relative to the tiller arm; and the portion of the base defining the first and second recesses therein is shaped to be received between the first arm and the second arm when the tiller assembly kit is assembled. 
     In yet another aspect of the present technology, there is provided another tiller assembly for a marine outboard engine. In some embodiments thereof, the other tiller assembly includes: a base adapted to pivot relative to a steering axis of the marine outboard engine and defining an axis of rotation that is perpendicular to the steering axis; a tiller arm pivotably connected to the base to pivot relative to the base about the axis of rotation for adjusting an angular position of the tiller arm relative to the base, one of the base and the tiller arm defining a male tapered surface, the male tapered surface being coaxial with the axis of rotation; a shaft extending through the base and the tiller arm, the shaft being coaxial with the axis of rotation, the shaft having a first threaded portion; a clamping fitting connected to the shaft, the clamping fitting defining a female tapered surface, the female tapered surface being coaxial with the axis of rotation, the female tapered surface contacting the male tapered surface, the clamping fitting being rotationally fixed relative to another one of the base and the tiller arm; and a handle, at least one of the handle and the clamping fitting having a second threaded portion engaged with the first threaded portion. 
     In some such embodiments, rotation of the first threaded portion relative to the second threaded portion in a pre-determined direction causes the female tapered surface of the clamping fitting to press against the male tapered surface. 
     The foregoing examples are non-limiting. 
     For purposes of this application, terms related to spatial orientation such as forward, rearward, upward, downward, left, and right, should be understood in a frame of reference where the propeller position corresponds to a rear of the marine outboard engine. Terms related to spatial orientation when describing or referring to components or sub-assemblies of the engine separately from the engine should be understood as they would be understood when these components or sub-assemblies are mounted to the engine, unless specified otherwise in this application. 
     Embodiments of the present technology each have at least one of the above-mentioned object and/or aspects, but do not necessarily have all of them. It should be understood that some aspects of the present technology that have resulted from attempting to attain the above-mentioned object may not satisfy this object and/or may satisfy other objects not specifically recited herein. 
     Additional and/or alternative features, aspects and advantages of embodiments of the present technology will become apparent from the following description, the accompanying drawings and the appended claims. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       For a better understanding of the present technology, as well as other aspects and further features thereof, reference is made to the following description which is to be used in conjunction with the accompanying drawings, where: 
         FIG. 1  is a right side elevation view of a marine outboard engine; 
         FIG. 2  is a perspective view of a tiller assembly of the marine outboard engine of  FIG. 1 , taken from a front, right, top view thereof; 
         FIG. 3  is a sectional view of a part of the tiller assembly of  FIG. 2  with clamping fittings thereof being omitted, taken through section line  3 - 3  of  FIG. 2 ; 
         FIG. 4  is a sectional view of a part of the tiller assembly of  FIG. 2 , taken through section line  4 - 4  of  FIG. 3 ; 
         FIG. 5  is the sectional view of the part of the tiller assembly of  FIG. 3  with the clamping fittings thereof being shown; 
         FIG. 6  is a perspective view of a left clamping fitting of  FIG. 5 , taken from a front, left, top side thereof; 
         FIG. 7  is a perspective view of a right clamping fitting of  FIG. 5 , taken from a front, left, top side thereof; 
         FIG. 8  is a sectional view of a part of the tiller assembly of  FIG. 2 , taken through section line  8 - 8  of  FIG. 5 ; 
         FIG. 9  is a sectional view of a part of the tiller assembly of  FIG. 2 , taken through section line  9 - 9  of  FIG. 5 ; 
         FIG. 10  is a schematic sectional view of an alternative embodiment of the tiller assembly of  FIG. 2 ; 
         FIG. 11  is a schematic sectional view of another alternative embodiment of the tiller assembly of  FIG. 2 ; 
         FIG. 12  is a schematic sectional view of another alternative embodiment of the tiller assembly of  FIG. 2 ; 
         FIG. 13  is a schematic sectional view of another alternative embodiment of the tiller assembly of  FIG. 2 ; 
         FIG. 14  is a schematic sectional view of another alternative embodiment of the tiller assembly of  FIG. 2 ; and 
         FIG. 15  is a schematic sectional view of another alternative embodiment of the tiller assembly of  FIG. 2 . 
     
    
    
     DETAILED DESCRIPTION 
     Referring to  FIG. 1 , a marine outboard engine  100  includes a drive unit  101  for powering and propelling the marine outboard engine  100 . The drive unit  101  includes a motor  102 , a mid-section  104 , a gear case  106 , and a propeller  110 . The motor  102  is an internal combustion engine, but could also be any other type of motor. In some embodiments, the motor  102  could be an electric motor for example. 
     The mid-section  104  extends downward from the motor  102  to the gear case  106 . The mid-section  104  houses vertical exhaust conduits  105  at a rear portion thereof, and a vertical drive shaft  107  at a front portion thereof. The vertical exhaust conduits  105  direct exhaust from the motor  102  into a body of water  111  in which the marine outboard engine  100  is used. The vertical drive shaft  107  connects a crankshaft (not shown) of the motor  102  to a transmission  132  disposed in the gear case  106 . 
     The gear case  106  includes a skeg  108  and a propeller shaft  109  connected at a front end thereof to the transmission  132 . The rear end of the propeller shaft  109  extends rearward out of the gear case  106 . The propeller  110  is mounted onto the rear end of the propeller shaft  109  for propelling the marine outboard engine  100  through a body of water  111 . In the present embodiment, the transmission  132  is a mechanical outboard transmission that is operable by a shift lever  130 . It is contemplated that the transmission  132  could be operated by a different mechanism. It is contemplated that the marine outboard engine  100  could have any other transmission. 
     In the present embodiment, a stern bracket  112  and a swivel bracket  114  are used to mount the drive unit  101 , and the marine outboard engine  100 , to a watercraft. More particularly, the stern bracket  112  is attachable to a stern  116  of the watercraft and can take various forms, the details of which are conventionally known. The swivel bracket  114  is pivotably connected to the stem bracket  112  to pivot relative to the stern bracket  112  about a horizontal tilt-trim axis  118 , as shown with a double-ended arrow  120  in  FIG. 1 . This allows for changes in the tilt/trim of the marine outboard engine  100 . It is contemplated that any tilt-trim mechanism could be used for the tilt/trim adjustment of the marine outboard engine  100 . It is also contemplated that the marine outboard engine  100  could have no tilt-trim mechanism. 
     The drive unit  101  of the marine outboard engine  100  is pivotably connected to the swivel bracket  114  to pivot about a steering axis  122 . This allows for steering of the marine outboard engine  100  and the watercraft to which it is attached. It is contemplated that any other mechanism could be used for mounting the marine outboard engine  100  onto a watercraft. 
     Still referring to  FIG. 1 , the marine outboard engine  100  further includes a tiller assembly  124 . The tiller assembly  124  includes a base  142 , a tiller arm  126 , and a tiller hinge mechanism  151 . 
     In the present embodiment, the base  142  is connected to the drive unit  101  to pivot with the drive unit  101  about the steering axis  122 . The base  142  is made of aluminum, but other materials are contemplated. In the present embodiment, the base  142  is bolted to an upper motor mount  147  of the drive unit  101  to transfer torque applied manually to the tiller arm  126  to the drive unit  101  to pivot the drive unit  101  about the steering axis  122 . It is contemplated that the base  142  could be connected to the drive unit  101  via any other suitable means. 
     With additional reference to  FIG. 2 , the tiller hinge mechanism  151  pivotably connects the tiller arm  126  to the base  142  to pivot relative to the base  142  about a horizontal axis of rotation  158 . The tiller hinge mechanism  151  allows a user to adjust the pivoting resistance of the tiller arm  126  relative to the base  142 . To this end, the tiller hinge mechanism  151  has a handle  182  that is manually rotatable to various positions relative to the tiller arm  126 . By changing the position of the handle  182 , the user may adjust the pivoting resistance of the tiller arm  126 . 
     In the present embodiment, the handle  182  of the tiller hinge mechanism  151  can be manually rotated to at least one position in which the tiller hinge mechanism  151  provides all of the following: a) allows the tiller arm  126  to be manually pivoted relative to the base  142  about an axis of rotation  158 , to a given angular position, b) keeps the tiller arm  126  in the given angular position when no manual force is applied to the tiller arm  126 , c) allows the tiller arm  126  to be again manually pivoted about the axis of rotation  158  to another given angular position; and d) keeps the tiller arm  126  in the other given angular position when no manual force is applied to the tiller arm  126 , until the tiller arm  126  is again manually pivoted to yet another given angular position. A user of the marine outboard engine  100  can adjust the pivoting resistance according to the user&#39;s strength and the operating conditions encountered at a given time, for example depending on whether the watercraft is operating in rough or flat waters, and can carry out all of a) to d) above without having to readjust the position of the handle  182  of the tiller hinge mechanism  151 . 
     The tiller arm  126  extends forward from the base  142  along a longitudinal axis  127 . The axis of rotation  158  is perpendicular to both the longitudinal axis  127  of the tiller arm  126  and the steering axis  122  of the marine outboard engine  100 . The tiller arm  126  allows a user to manually steer the marine outboard engine  100 . The tiller arm  126  includes a throttle grip  128  in the form of a twist grip used as throttle control as in many conventional marine outboard engines. The tiller arm  126  also includes the shift lever  130  for selecting a forward, neutral or reverse gear of the transmission  132  housed in the gear case  106 . The tiller arm  126  further includes a safety lanyard  134  connected to an engine cut-off switch  136 , an engine start/stop switch  137  and a key switch  138  operable with a key  140  to wake the electrical system of the outboard engine  100 . These elements are conventional and are therefore not described in more detail herein. It is contemplated that these elements could be different and/or omitted. 
     Referring to  FIG. 2 , the tiller arm  126  connects to the base  142  via a pair of arms  220  and  222  defined at a rear end  154  of the tiller arm  126 . The portion of the tiller arm  126  that forms the arms  220  is made of aluminum, but other materials are contemplated. The base  142  defines a projection  150  at a front side thereof and a pair of recesses  152  on the lateral sides of the projection  150 . The projection  150  extends forward and upward from the front side of the base  142 . The arms  220  and  222  of the tiller arm  126  are received in respective ones of the recesses  152  on the respective lateral sides of the projection  150 . The arms  220  and  222  of the tiller arm  126  are pivotably connected to the projection  150  via a shaft  174  and a pair of clamping fittings  192 ,  194  of the tiller hinge mechanism  151 . This construction is described in more detail next. 
     Referring to  FIGS. 3 to 5 , the base  142  defines a horizontal aperture  156  therein. The horizontal aperture  156  extends laterally through the projection  150  and receives the shaft  174  and parts of the clamping fittings  192 ,  194  therein to define the axis of rotation  158  of the tiller arm  126 . This way, the base  142  defines the axis of rotation  158  of the tiller arm  126 . More particularly, the horizontal aperture  156  forms an inner surface  160  of the base  142 . The inner surface  160  defines two recesses  162  and a space  164  between the recesses  162 . The recesses  162  receive therein respective ones of the clamping fittings  192 ,  194  of the tiller hinge mechanism  151 . 
     To this end, each of the recesses  162  includes a cylindrical outer portion  166  at an outer lateral end thereof, and a female frusto-conical portion  168 . The female frusto-conical portions  168  of the recesses  162  are positioned on opposed lateral sides of the projection  150  of the base  142 . The female frusto-conical portions  168  extend from the respective cylindrical outer portions  166  into the projection  150  toward the space  164 . The female frusto-conical portions  168  define smooth female tapered surfaces  161  of the base  142 . The female frusto-conical portions  168 , and the female tapered surfaces  161 , taper/narrow toward the space  164 . The cylindrical outer portions  166 , the female frusto-conical portions  168  and the space  164  are all coaxial with the axis of rotation  158 . The shaft  174  and the clamping fittings  192 ,  194  are also coaxial with the axis of rotation  158 . 
     Now referring in particular to  FIG. 4 , the base  142  also defines a lubricant channel  170  in the projection  150 . The lubricant channel  170  extends from a front end of the projection  150  to the space  164 . The lubricant channel  170  at its front end terminates at a nipple  172 . The lubricant channel  170  fluidly connects the nipple  172  to the space  164  between the frusto-conical portions  168 . A grease-gun (not shown), or other lubricating instrument, can be connected to the nipple  172  for injecting a lubricant, such as a grease, into the space  164 . The lubricant lubricates the tiller hinge mechanism  151 . It is contemplated that this lubrication system could be omitted or that a different lubrication system could be used. 
     As shown in  FIG. 3 , the shaft  174  has a threaded left end  176  and a threaded right end  178 . In the present embodiment, the left end  176  defines a circumferentially extending slot  181  in an outer peripheral surface thereof. The slot  181  receives a fastener  183 , more precisely a circlip  183  (also known as a c-clip or snap ring), therein. It is contemplated that the slot  181  and the circlip  183  could be omitted. The shaft is made of stainless steel, but other materials are contemplated. The left end  176  of the shaft  174  is positioned on a right side of a projection  177  of the base  142  which covers the key switch  138 . The left end  176  of the shaft  174  is spaced from the right side of the projection  177  of the base  142  by a space  179 . The space  179  allows the shaft  174  to move, by rotation about the axis of rotation  158 , laterally leftward  198  from the position shown in  FIG. 3 . It is contemplated that the projection  177  could be omitted. 
     Referring to  FIGS. 3 and 5 , further in the present embodiment, the three resilient spring washers  180  are received over the right end  178  of the shaft  174 . Each of the resilient spring washers  180  defines an axial aperture therein which is slightly larger than the diameter of the shaft  174 . The shaft  174  is rotatable relative to the resilient spring washers  180 . It is contemplated that a different number of spring washers  180  could be used and that they could be stacked in series, in parallel or some combination thereof. The spring washers  180  are made of stainless steel, but other materials are contemplated. The resilient spring washers  180  are an example of resilient members. It is contemplated that one or more different resilient members could be used instead of, in combination with, or in addition to the resilient spring washers  180 . 
     Still referring to  FIGS. 3 and 5 , the handle  182  of the tiller hinge mechanism  151  defines a threaded aperture  184  in a leftward-extending projection  185  thereof. The right end  178  of the shaft  174  is threaded into the threaded aperture  184  in the leftward-extending projection  185  of the handle  182  and is locked therein with a set screw. The handle  182  is thereby rotationally fixed relative to the shaft  174 . It is contemplated that the handle  182  could be rotationally fixed relative to the shaft  174  via any other suitable means. For example, in some embodiments, the handle  182  could be integral with the shaft  174 . The handle  182  has four projections  186  that are disposed radially about the threaded aperture  184  coaxially with the axis of rotation  158 . The projections  186  extend radially outward from the leftward-extending projection  185 . It is contemplated that other configurations of the handle  182  could be used. 
     Referring to  FIGS. 5 to 7 , the clamping fittings  192  and  194  of the tiller hinge mechanism  151  are received over the shaft  174 . The clamping fittings  192  and  194  are made of stainless steel, but other materials are contemplated. Referring to  FIGS. 5 and 6 , the left clamping fitting  192  defines a threaded axial aperture  196  that extends laterally therethrough. The left end  176  of the shaft  174  is threaded into the threaded axial aperture  196 . The thread in the threaded axial aperture  196  engages the thread on the left end  176  of the shaft  174 . Referring to  FIGS. 5 and 7 , the right clamping fitting  194  defines an axial aperture  200  that extends laterally therethrough. The diameter of the axial aperture  200  is slightly larger than the diameter of the shaft  174 . The axial aperture  200  is smooth inside, and does not have a thread therein. The axial aperture  200  slidably receives the shaft  174  therein. Thus, the shaft  174  is slidable relative to the right clamping fitting  194  along the axis of rotation  158 . 
     The left clamping fitting  192  is received in the recess  162  defined in the lateral left side of the projection  150 . The right clamping fitting  194  is received in the recess  162  defined in the lateral right side of the projection  150 . As best seen in  FIGS. 6 and 7 , the clamping fittings  192 ,  194  both have an outer splined cylindrical portion  204 , a smooth cylindrical mid-portion  206 , and a smooth male frusto-conical portion  208 . The male frusto-conical portions  208  are received in respective ones of the female frusto-conical portions  168  of the recesses  162 . In the present embodiment, the female frusto-conical portions  168  of the recesses  162  and the male frusto-conical portions  208  of the clamping fittings  192 ,  194  are disposed symmetrically about a vertical plane  211  passing through the longitudinal axis  127  of the tiller arm  126 . 
     Still referring to  FIGS. 5 to 7 , the male frusto-conical portion  208  of the left clamping fitting  192  extends from the cylindrical mid-portion  206  of the left clamping fitting  192  toward the handle  182  (i.e. toward the right). The male frusto-conical portion  208  of the left clamping fitting  192  narrows from the cylindrical mid-portion  206  of the left clamping fitting  192  toward the handle  182 . The male frusto-conical portion  208  of the right clamping fitting  194  extends from the cylindrical mid-portion  206  of the right clamping fitting  194  toward the left clamping fitting  192  (i.e. toward the left). The male frusto-conical portion  208  of the right clamping fitting  194  narrows from the cylindrical mid-portion  206  of the right clamping fitting  194  toward the left clamping fitting  192 . 
     Both of the male frusto-conical portions  208  define smooth male tapered surfaces  209 . The male tapered surfaces  209  contact and mate with the respective ones of the frusto-conical portions  168  of the recesses  162 . The male tapered surface  209  of the left clamping fitting  192  faces toward the handle  182 . The male tapered surface  209  of the right clamping fitting  194  faces away from the handle  182 . Referring to  FIG. 5 , the female tapered surfaces  161  of the recesses  162  and the male tapered surfaces  209  of the clamping fittings  192 ,  194  define respective angles  216  relative to the axis of rotation  158 . In the present embodiment, the angles  216  are all equal to 15 degrees from the axis  158 . In some embodiments, the angles  216  are different, depending on the particular materials, surface finishes, and construction of the tiller assembly  124  for example. 
     The choice of taper angle  216  will have an effect on the application and adjustment of the friction between respective female and male tapered surfaces  161  and  209  when the handle  186  is turned clockwise  190  or countered-clockwise  191 , a process that will be described in further detail below. As will be appreciated by one skilled in the art, too low an angle  216  may create a locking taper, also known as a self-holding machine taper, that could make loosening the tiller hinge mechanism  151  difficult. In contrast, and as will also be appreciated by one skilled in the art, the greater the angle  216  the less mechanical advantage when adjusting the pivoting resistance of the tiller hinge mechanism  151 . It is contemplated that, in some embodiments, the angles  216  could be in a range of at least 7 degrees and up to 45 degrees, or could be in a range of 10 degrees to 20 degrees and in some cases in a range of 14 to 16 degrees. 
     In the present embodiment, the outer splined cylindrical portion  204  of the left clamping fitting  192  is larger in diameter than the cylindrical mid-portion  206  of the left clamping fitting  192 . The splines  210  of the outer splined cylindrical portion  204  of the left clamping fitting  192  are disposed circumferentially about the threaded axial aperture  196  parallel to a central axis of the threaded axial aperture  196 . The splines  210  of the outer splined cylindrical portion  204  of the left clamping fitting  192  are parallel to the axis of rotation  158  and are disposed circumferentially about the axis of rotation  158 . 
     Still referring to  FIGS. 5 and 7 , the outer splined cylindrical portion  204  of the right clamping fitting  194  is slightly larger in diameter than the cylindrical mid-portion  206  of the right clamping fitting  194 . The splines  210  of the outer splined cylindrical portion  204  of the right clamping fitting  194  are disposed circumferentially about the axial aperture  200  in parallel to a central axis of the axial aperture  200 . The splines  210  of the outer splined cylindrical portion  204  of the right clamping fitting  194  are parallel to the axis of rotation  158 . The outer splined cylindrical portions  204  of the left and right clamping fittings  192 ,  194  are slidably received in corresponding splined apertures  232 ,  224  defined in the arms  220 ,  220  of the tiller arm  126 . 
     The aperture  224  in the right arm  222  has a cylindrical portion  226 , which at least partly receives the spring washers  180 , and a splined cylindrical portion  228 , which slidably receives therein the outer splined cylindrical portion  204  of the right clamping fitting  194 . To this end, the splined cylindrical portion  228  defines a plurality of internal splines  230  therein as its name suggests. 
     The splines  230  are parallel to the axis of rotation  158  and are disposed circumferentially around the axis of rotation  158 . As best shown in  FIG. 8 , the splines  230  slidably engage the splines of the outer splined cylindrical portion  204  of the right clamping fitting  194 . Accordingly, the outer splined cylindrical portion  204  of the right clamping fitting  194  is slidable laterally relative to the right arm  222  of the tiller arm  126 , along the axis of rotation  158 . Due to the splined connection, the outer splined cylindrical portion  204  of the right clamping fitting  194 , and therefore the right clamping fitting  194 , is rotationally fixed relative to the tiller arm  126 . 
     Referring back to  FIG. 5 , the cylindrical portion  226  of the aperture  224  partly receives the three spring washers  180  therein. The diameter of the cylindrical portion  226  is slightly larger than the diameter of the resilient spring washers  180  such that the circumference of the resilient spring washers  180  do not contact the tiller arm  126 . It is contemplated that in some embodiments, the resilient spring washers  180  could contact the tiller arm  126 . In the present embodiment, the diameter of the cylindrical portion  226  is slightly larger than the diameter of the splined cylindrical portion  228 . However, it is contemplated that this need not be the case. 
     Still referring to  FIG. 5 , the aperture  232  in the left arm  220  slidably receives therein the outer splined cylindrical portion  204  of the left clamping fitting  192 . To this end, similar to the aperture  224 , the aperture  232  defines a plurality of splines  234  therein. The splines  234  are parallel to the axis of rotation  158  and are disposed circumferentially around the axis of rotation  158 . As best shown in  FIG. 9 , the splines  234  slidably engage the splines of the outer splined cylindrical portion  204  of the left clamping fitting  192 . Accordingly, the outer splined cylindrical portion  204  of the left clamping fitting  192  is slidable laterally relative to the left arm  220  of the tiller arm  126 , along the axis of rotation  158 . Due to the splined connection, the outer splined cylindrical portion  204  of the left clamping fitting  192 , and therefore the left clamping fitting  192 , is rotationally fixed relative to the tiller arm  126 . 
     It is contemplated that the splines  210 ,  230 ,  234  need not be equidistant from the axis of rotation  158 . It is also contemplated that the outer splined cylindrical portions  204  of the clamping fittings  192 ,  194 , and therefore the clamping fittings  192 ,  194 , could be both slidable along the axis of rotation  158  and be rotationally fixed relative to the tiller arm  126  using a different structure, such as a keyed joint or matching non-circular cross-sectional shapes. 
     The cylindrical mid-portions  206  of the clamping fittings  192 ,  194  closely match the diameter of the respective ones of the cylindrical outer portions  166  of the recesses  162 , while remaining slightly smaller. This close fit between the cylindrical mid-portions  206  and the cylindrical outer portions  166  allows the clamping fittings  192 ,  194  to slide laterally relative to the recesses  162  and act as bearing surfaces for smooth rotation of the clamping fittings  192 ,  194 , and hence the tiller arm  126  about the base  142 . The cylindrical mid-portions  206  of the clamping fittings  192 ,  194  have axial widths  212  that are slightly larger than the respective widths  214  ( FIG. 5 ) of the cylindrical outer portions  166  of the recesses  162 . The outer splined cylindrical portions  204  of the clamping fittings  192 ,  194  therefore do not contact the flat metal washers  218  that are received between the arms  220 ,  222  of the tiller arm  126  and the base  142 . 
     The flat metal washers  218  are received over the cylindrical mid-portions  206  of the clamping fittings  192 ,  194  between the corresponding arms  220 ,  222  of the tiller arm  126  and the lateral sides of the projection  150  of the base  142  and are provided to aid rotation therebetween. The left side washer  218  is disposed between and contacts the left arm  220  of the tiller arm  126  and the portion of the base  142  that defines the left side recess  162 . The right side washer  218  is disposed between and contacts the right arm  222  of the tiller arm  126  and the portion of the base  142  that defines the right side recess  162 . As noted above, the outer splined cylindrical portions  204  of the clamping fittings  192 ,  194  are spaced from the respective ones of the flat metal washers  218 . 
     As shown in  FIG. 5 , the handle  182  is in contact with the right side of the spring washers  180 , the left side of the spring washers  180  is in contact with the right side of the right clamping fitting  194 , the male tapered surfaces  209  of the left and right clamping fittings  194  and  192  are in contact with the female tapered surfaces  161  of the left and right recess  162 , respectively, and the left clamping fitting  192  is threaded onto the left end  176  of the shaft  174 , which is fixed to the handle  182 . When the resilient spring washers  180  are compressed between the handle  182  and the right clamping fitting  194  by a leftward  198  axial force, F 1 , the resilient spring washers  180  in turn press the right clamping fitting  194 , and the male tapered surface  209  thereof, against the female tapered surface  161  of the right side recess  162 . The axial force F 1  thereby creates friction between the male tapered surface  209  of the right clamping fitting  194  and the female tapered surface  161  of the right side recess  162 . Since the outer splined cylindrical portion  204  of the right clamping fitting  194  does not contact the right side washer  218 , the right clamping fitting  194  does not press on the right side washer  218 . 
     Still referring to  FIG. 5 , the compression of the resilient spring washers  180  results in the shaft  174  applying an axial force F 2  to the left clamping fitting  192 . The axial force F 2  is directed rightward  202 . The left clamping fitting  192 , and the male tapered surface  209  thereof, is therefore pressed against the female tapered surface  161  of the left side recess  162 . More particularly, the tapered surface  209  of the left clamping fitting  192  is pulled by the axial force F 2  against the female tapered surface  161  of the left side recess  162  as the compressed resilient spring washers  180  push rightward against the handle  182 . The axial force F 2  thereby creates friction between the male tapered surface  209  of the left clamping fitting  192  and the female tapered surface  161  of the left side recess  162 . Since the outer splined cylindrical portion  204  of the left clamping fitting  192  does not contact the left side washer  218 , the left clamping fitting  192  does not press on the left side washer  218 . 
     The friction between the female tapered surfaces  161  of the base  142  and the male tapered surfaces  209  of the clamping fittings  192 ,  194  determines the resistance to manually pivoting the tiller arm  126  about the axis of rotation  158  relative to the base  142 . This possible pivoting motion is shown with a double-ended arrow  236  in  FIG. 1 . The resistance of the tiller arm  126  to pivoting about the axis of rotation  158  relative to the base  142  may be referred to as a pivoting resistance. In turn, since the friction between the male and female tapered surfaces  161  and  209  provides the pivoting resistance of the tiller arm  126 , the friction may be referred to as a pivoting friction. In the present embodiment, due to the symmetry of the pivot connection between the base  142  and the tiller arm  126 , described above, the pivoting friction is at least approximately symmetrically distributed between the projection  150  and the arms  220 ,  222 . More particularly, the pivoting friction is at least approximately symmetrically distributed along the female tapered surfaces  161  and the male tapered surfaces  209 . 
     The construction of the tiller hinge mechanism  151  described herein above allows the pivoting friction, and therefore the pivoting resistance, to be adjusted. To this end, the handle  182  may be manually rotated clockwise  190  to increase the friction, and the pivoting resistance, and counter-clockwise  191  to decrease the friction, and the pivoting resistance. In the present embodiment, turning the handle  182  clockwise  190  rotates the shaft  174  clockwise  190  about the axis of rotation  158  relative to tiller arm  126  and the left clamping fitting  192 . This relative rotation of the thread of the left end  176  of the shaft  174  and the thread in the axial aperture  196  of the left clamping fitting  192  draws the left clamping fitting  174  and the handle  182  toward each other. Since the left clamping fitting  174  is pressed up against the left female tapered surface  161 , the clockwise rotation  190  of the handle  182  results in the shaft  174  and handle  182  moving leftward  198  relative to both the left clamping fitting  192  and the base  142 , as well as the right clamping fitting  194 , which is pressed up against the right female tapered surface  161 . This further compresses the resilient spring washers  180 . 
     The more the handle  182  is rotated clockwise  190 , the harder it pushes  198  against the resilient spring washers  180 . The more the resilient spring washers  180  are compressed between the handle  182  and the right clamping fitting  194  the more the male tapered surfaces  209  the clamping fittings  192 ,  194  press against the female tapered surfaces  161  of the side recesses  162 . This increases the pivoting friction between the clamping fittings  192 ,  194  and the base  142 . 
     In the present embodiment, the handle  182  may be manually rotated counter-clockwise  191  to decrease the pivoting friction, and the pivoting resistance. Doing so moves the shaft  174  rightward  202  relative to both the left clamping fitting  192  and the right clamping fitting  194 . This reduces the compression of the resilient spring washers  180  and hence the pivoting friction described above, between the male tapered surfaces  209  of the clamping fittings  192 ,  194  and the corresponding female tapered surfaces  161  of the recesses  162 . It is possible to rotate the handle  182  counter-clockwise  191  to a point where the resilient spring washers  180  are no longer compressed. If counter-clockwise rotation of the handle  182  is continued beyond that point, then a gap will form between at least one of the following pairs: the handle  182  and the springs washers  180 , the spring washers  180  and the right clamping fitting  194 , the right clamping fitting  194  and the right recess  162 , and the left recess  162  and the left clamping fitting  192 . It is contemplated that the threaded connections between the left clamping fitting  192  and the shaft  174  could be reversed such that counter-clockwise  191  rotation of the handle  182  would increase the pivoting friction and clockwise  190  rotation of the handle  182  would decrease the pivoting friction. When the handle  182  is manually rotated to a given position, the handle  182  stays in the given position at least for some time until the handle  182  is again manually rotated to a different position. 
     In the present embodiment, the handle  182  can be manually rotated to at least one equilibrium position  250  in which the tiller hinge mechanism  151 , and more particularly the interaction between the resilient washers  180  and the handle  182  and the clamping fittings  192  and  194 , holds the tiller arm  126  in an equilibrium state. In the equilibrium state, the tiller arm  126  can be manually pivoted about the axis of rotation  158  against the pivoting friction provided by the tiller hinge mechanism  151  to any desired position relative to the base  142  and will stay in the selected position. While the handle  182  remains in the at least one equilibrium position  250 , the tiller hinge mechanism  151  will keep the tiller arm  126  in the selected position against both gravity and at least some of the shocks that may be experienced by the tiller arm  126  and/or the tiller hinge mechanism  151  during normal operation of a watercraft to which the marine outboard engine  100  may be mounted. 
     In summary, in the at least one equilibrium position  250  of the handle  182 , the tiller arm  126  can be manually pivoted by a user about the axis of rotation  158  to a given angular position relative to the base  142 . The tiller arm  126  will stay in the given angular position, while the handle  182  is in the equilibrium position  250 , until the user decides to again change the given angular position of the tiller arm  126 . At that point, and while keeping the handle  182  in the position  250 , the user will be able to manually pivot the tiller arm  126  to a different angular position without having to first rotate the handle  182  away from the equilibrium position  250 . The tiller arm  126  will stay in the different angular position until the user decides to again change reposition the tiller arm  126  relative to the base  142  about the axis of rotation  158 . 
     Since the male tapered surfaces  209  of the clamping fittings  192 ,  194  and the female tapered surfaces  161  of the recesses  162  are smooth, the tiller assembly  124  is not limited to a particular pre-determined number of angular positions to which it can be pivoted relative to the base  142  about the axis of rotation  158 . The tiller hinge mechanism  151  therefore may be said to provide an infinite number of angular positions to which the tiller arm  126  may be pivoted relative to the base  142 . It is contemplated that in some embodiments, the clamping fittings  192 ,  194  could have female tapered surfaces and the recesses  162  could have male tapered surfaces receivable in and mateable with the female tapered surfaces of the clamping fittings  192 ,  194 . 
     Reference is now made to  FIG. 10 , which schematically shows a part of a tiller assembly  1000 . The tiller assembly  1000  is a different embodiment of the tiller assembly  124 . The tiller assembly  1000  includes a base  1002  and a tiller arm  1004 . As shown in  FIG. 10 , the base  1002  and the tiller arm  1004  define complementary L-shapes  1003 ,  1005 , respectively. The tiller arm  1004  is pivotably connected at a rear portion  1027  of the L-shape  1005  to a front portion of the L-shape  1003  of the base  1002  to pivot relative to the base  1002  about an axis of rotation  1008 . A flat washer  1007  is received between the rear portion  1027  of the L-shape  1005  of the tiller arm  1004  and the front portion of the L-shape  1003  of the base  1002 . Similar to the base  142 , the base  1002  can be bolted, or otherwise fixed, to the drive unit  101  of the marine outboard engine  100 , to pivot with the drive unit  101  about the steering axis  122  of the marine outboard engine  100 . 
     In this alternative embodiment, instead of the recesses  162  of the base  142 , the base  1002  defines a horizontal aperture  1006  therethrough. The horizontal aperture  1006  is similar to the aperture  232  in the tiller arm  126  of the tiller assembly  124 . More particularly, the horizontal aperture  1006  is coaxial with, and defines, the axis of rotation  1008  of the tiller arm  1004 . The horizontal aperture  1006  defines a plurality of splines therein, which are parallel to and distributed circumferentially about the axis of rotation  1008  of the tiller arm  1004 . The splines  1009  of the horizontal aperture  1006  are similar to the splines  234  of the aperture  232  of the tiller assembly  124  and are therefore not described in detail herein. 
     The horizontal aperture  1006  slidably receives therein an outer splined cylindrical portion  1010  of a single clamping fitting  1012  of the tiller assembly  1000 . The splines of the outer splined cylindrical portion  1010  of the single clamping fitting  1012  engage the splines in the horizontal aperture  1006 . Accordingly, the single clamping fitting  1012  is slidable relative to the base  1002  along the axis of rotation  1008  and is rotationally fixed relative to the base  1002 . 
     As shown, in the present embodiment, similar to the clamping fittings  192 ,  194 , the single clamping fitting  1012  has an outer splined cylindrical portion  1010 , a smooth mid-portion  1011 , and a male frusto-conical portion  1014 . The male frusto-conical portion  1014  extends from the right end of the smooth mid-portion  1011  toward the handle  1024 . Similar to the left clamping fitting  192 , the clamping fitting  1012  defines an axial threaded aperture (not separately labeled) therethrough. A shaft  1016  having a threaded mid-portion  1017  is threaded into the axial aperture of the single clamping fitting  1012 . 
     The male frusto-conical portion  1014  is matingly received in a matching female frusto-conical recess  1018  defined through the rear end  1027  of the tiller arm  1004 . Both the male frusto-conical portion  1014  of the clamping fitting  1012  and the female frusto-conical recess  1018  are coaxial with the axis of rotation  1008 . The smooth surface of the clamping fitting  1012  that defines its male frusto-conical portion  1014  and the smooth surface of the tiller arm  1004  that defines the female frusto-conical recess  1018  together define a 12 degree angle  1020  relative to the axis of rotation  1008 . 
     In this embodiment, the shaft  1016  at one end thereof terminates at a head  1022  and at the other end thereof terminates at the handle  1024 . Both the head  1022  and the handle  1024  are rotationally and longitudinally fixed relative to the shaft  1016 . A flat washer  1026  is received over the one end of the shaft  1016  between the head  1022  of the shaft  1016  and a left side surface of the base  1002 . Two resilient washers  1028  are received over the other end of the shaft  1016  and are compressed between the handle  1024  and a right side surface of the tiller arm  1004 . It is contemplated that the resilient washers  1028  could be received in a recess in the right side surface of the tiller arm  1004 , i.e. a counterbore. The shaft  1016  together with the clamping fitting  1012  and the base  1002  define the axis of rotation  1008  of the tiller arm  1004 . 
     Rotation of the handle  1024  about the axis of rotation  1008  causes the shaft  1016  to rotate about the axis of rotation  1008  relative to the clamping fitting  1012 . In this embodiment, when the handle  1024  is rotated clockwise  190  about the axis of rotation  1008  toward a given position, the thread of the shaft  1016  engages and rotates relative to the thread in the axial aperture of the clamping fitting  1012 , which draws the handle  1024  towards the tiller arm  1004  and further compresses the resilient washers  1028 . As this happens, the shaft  1016  pushes the male tapered surface of the frusto-conical portion  1014  of the clamping fitting  1012  against the female tapered surface of the female frusto-conical recess  1018 . Since the clamping fitting  1012  is rotationally fixed relative to the base  1002 , the increased friction between the clamping fitting  1012  and the tiller arm  1004  increases the pivoting friction between the base  1002  and the tiller arm  1004 . 
     Similar to the tiller assembly  124 , the handle  1024  can be rotated about the axis of rotation  1008  to at least one position in which the tiller arm  1004  both: a) resists gravity and normal shocks and remains in a given angular position relative to the base  1002 , and b) allows a user of the marine outboard engine  100  to manually change the given angular position of the tiller arm  1004  without having to readjust the position of the handle  1024 . 
     It is contemplated that in some embodiments the threading of the shaft  1006  and the clamping fitting  1012  could be selected such that counter-clockwise  191  rotation of the handle  1024  would increase friction between the clamping fitting  1012  and the tiller arm  1004 , and therefore the pivoting friction of the tiller arm  1004  relative to the base  1002 . In such embodiments, the pre-determined direction for decreasing friction between the clamping fitting  1012  and the tiller arm  1004 , and therefore the pivoting friction of the tiller arm  1004  relative to the base  1002 , would be clockwise  190 . 
     Reference is now made to  FIG. 11 , which schematically shows a part of a tiller assembly  1100 . The tiller assembly  1100  is a different embodiment of the tiller assembly  1000 . The tiller assembly  1100  is similar to the tiller assembly  1000  and is therefore not described in detail herein. 
     One difference between the tiller assembly  1100  and the tiller assembly  1000  is that in the tiller assembly  1100 , the handle  1102  is positioned on the opposite lateral side of the base  1104  as the resilient member  1106 . Another difference between the tiller assembly  1100  and the tiller assembly  1000  is that the resilient member  1106  is a coil spring  1106 . The spring  1106  replaces and is equivalent to the resilient washes. The spring  1106  is compressed by a head  1112  of the shaft  1110  against the lateral right side  1114  of the tiller arm  1116 . Similar to the clamping fitting  1012 , the clamping fitting  1118  and the base  1104  comprise corresponding splined surfaces such that the clamping fitting  1118  is rotationally fixed with respect to the base  1104 , and the clamping fitting  1118  and the tiller arm  1116  comprise a male frusto-conical portion and corresponding female frusto-conical recess, respectively. Also similar to the clamping fitting  1012 , the clamping fitting  1118  defines an axial threaded aperture (not separately labeled) therethrough. The thread in the axial threaded aperture of the clamping fitting  1118  engages a correspondingly threaded portion of the shaft  1110 . Accordingly, when the coil spring  1106  is compressed, rotation of the handle  1102  will change the friction between the clamping fitting  1118  and the tiller arm  1116 . 
     As in the tiller assembly  1000 , the handle  1102  of the tiller assembly  1100  is rotatable about the axis of rotation  1122  to at least one equilibrium position in which the tiller arm  1116  is in an equilibrium state and both: a) remains in a given angular position relative to the base  1104 , and b) allows a user of the marine outboard engine  100  to manually change the given angular position of the tiller arm  1116  without having to readjust the position of the handle  1102 . 
     Reference is now made to  FIG. 12 , which schematically shows a part of a tiller assembly  1200 . The tiller assembly  1200  is a yet another different embodiment of the tiller assembly  124 . The tiller assembly  1200  is similar to the tiller assembly  124 , and therefore the tiller assembly  1200  is not described herein in detail. 
     One difference between the tiller assembly  1200  and the tiller assembly  124  is that in the tiller assembly  1200 , it is the base  1202  and not the tiller arm  1208  that defines a pair of arms  1204 ,  1206 . The pair of arms  1204 ,  1206  receive therebetween the rear end of the tiller arm  1208 . Another difference between the tiller assembly  1200  and the tiller assembly  124  is that in the tiller assembly  1200 , the resilient metal washers  1207  are not all of the same size. 
     Another difference between the tiller assembly  1200  and the tiller assembly  124  is that in the tiller assembly  1200 , it is the tiller arm  1208  and not the base  1202  that defines the female frusto-conical recesses  1210  therein. Also, in the tiller assembly  1200 , it is the base  1202  that defines the splined apertures  1212  therein, the splined apertures  1212  slidably receiving the splined portions of the respective ones of the clamping fittings  1214  therein. Accordingly, in the tiller assembly  1200 , the clamping fittings  1214  are rotationally fixed relative to the base  1202 . 
     Similar to the tiller assembly  124 , in the tiller assembly  1200 , it is the left clamping fitting  1214  that is threaded onto and operatively engages with the shaft  1216 . Operation of the tiller assembly  1200  is similar to the operation described above with respect to the tiller assembly  124 , and is therefore not described in more detail herein. 
     Reference is now made to  FIG. 13 , which schematically shows a part of a tiller assembly  1300 . The tiller assembly  1300  is a different embodiment of the tiller assembly  1200 . The tiller assembly  1300  is similar to the tiller assembly  1200 , and therefore the tiller assembly  1300  is not described herein in detail. 
     One difference between the tiller assembly  1300  and the tiller assembly  1200  is that in the tiller assembly  1300 , the left clamping fitting  1302  is both laterally and rotationally fixed to the shaft  1304 . More particularly, the shaft  1304  is received in a central axial aperture defined in the left clamping fitting  1302  and is fixed laterally and rotationally to the left clamping fitting  1302  with a set screw. It is contemplated that any suitable means for laterally and rotationally fixing the left clamping fitting  1302  to the shaft  1304  could be used instead of or in addition to the set crew. Another difference between the tiller assembly  1300  and the tiller assembly  1200  is that in the tiller assembly  1300 , the handle  1306  is threaded onto the right end of the shaft  1304  such that the handle  1306  can be manually rotated by a user of the marine outboard engine  100  about the axis of rotation  1308  relative to the shaft  1304 . 
     Rotating the handle  1306  clockwise  190  relative to the shaft  1304  threads the shaft  1304  further into the handle  1306 . This reduces the distance between the handle  1306  and the left clamping fitting  1302  and thereby pushes the handle  1306  harder against the resilient washers  1310  and the left clamping fitting  1302  harder against the female tapered surface  1312  in the left side recess  1314 . The right clamping fitting  1316  in turn pushes harder against the female tapered surface  1318  of the right side recess  1320 . The pivoting friction thereby increases at least approximately symmetrically on the left and right sides of the tiller arm  1322 . 
     Rotating the handle  1306  counter-clockwise  191  relative to the shaft  1304  unthreads the shaft  1304  out of the handle  1306 . This increases the distance between the handle  1306  and both the left clamping fitting  1302  and the right clamping fitting  1316 . This reduces the magnitude of the force with which the handle  1306  and the resilient washers  1310  push the right clamping fitting  1316  against the tapered surface  1318  of the right side recess  1320 . The increased distance between the handle  1306  and the left clamping fitting  1302  also reduces the force with which the left clamping fitting  1302  pushes against the tapered surface  1312  in the left side recess  1314 . The pivoting friction thereby decreases at least approximately symmetrically on the left and right sides of the tiller arm  1322 . 
     Reference is now made to  FIG. 14 , which schematically shows a part of a tiller assembly  1400 . The tiller assembly  1400  is a another different embodiment of the tiller assembly  1200 . The tiller assembly  1400  is similar to the tiller assembly  1200 , and therefore the tiller assembly  1400  is not described herein in detail. 
     One difference between the tiller assembly  1400  and the tiller assembly  1200  is that in the tiller assembly  1400 , the recesses  1402  defined in the tiller arm  1404  are defined in part by male tapered surfaces  1406  instead of female tapered surfaces. More particularly, as shown in  FIG. 14 , each of the recesses  1402  has a smooth outer cylindrical portion  1408  and a smooth male frusto-conical portion  1412 . The outer cylindrical portions  1408  and the male frusto-conical portions  1412  are all coaxial with the axis of rotation  1410 . The male frusto-conical portions  1412  define the respective ones of the male tapered surfaces  1406 . 
     Another difference between the tiller assembly  1400  and the tiller assembly  1200  is that in the tiller assembly  1400 , the clamping fittings  1414  define female frusto-conical portions  1416  instead of male frusto-conical portions. Each of the female frusto-conical portions  1416  defines a female tapered surface  1418  at an inward lateral side thereof and a smooth cylindrical mid-section  1420  that is disposed circumferentially about the female tapered surface  1418 . The female frusto-conical portions  1416 , the female tapered surfaces  1418 , and the smooth cylindrical mid-sections  1420  are all coaxial with the axis of rotation  1410 . 
     The female frusto-conical portions  1416  of the clamping fittings  1414  are received in the respective ones of the recesses  1402  such that the female tapered surfaces  1418  of the clamping fittings  1414  contact and mate with respective ones of the male tapered surfaces  1406  of the tiller arm  1404  in the recesses  1402 . The smooth cylindrical mid-sections  1420  of the clamping fittings  1414  are received in part in respective ones of the recesses  1402 . 
     Similar to the tiller assembly  1200 , in the tiller assembly  1400 , the left clamping fitting  1414  is threaded onto and operatively engages the thread on the left end of the shaft  1422 . In the tiller assembly  1400 , the threaded axial aperture  1424  of the left clamping fitting  1414  extends the entire width of the left clamping fitting  1414 , from the lateral right side of the female frusto-conical portion  1416  to the lateral left side of the splined outer portion  1426 . 
     As in the tiller assembly  1200 , the shaft  1422  of the tiller assembly  1400  is received through and slidably engages a smooth inner surface of the non-threaded axial aperture  1428  of the right clamping fitting  1414 . However, in the tiller assembly  1400 , two resilient washers  1430  are used instead of the three resilient washers  1207  of the tiller assembly  1200 . The two resilient washers  1430  are compressed by the handle  1432  against the right clamping fitting  1414 . As in the tiller assembly  1200 , the handle  1432  is rotationally and laterally fixed to the shaft  1422 , and is coaxial therewith. 
     Operation of the tiller assembly  1400  is similar to the operation described above with respect to the tiller assembly  1200 , and is therefore not described in more detail herein. 
     Reference is now made to  FIG. 15 , which schematically shows a part of a tiller assembly  1500 . The tiller assembly  1500  is a another different embodiment of the tiller assembly  1400 . The tiller assembly  1500  is similar to the tiller assembly  1400 , and therefore the tiller assembly  1500  is not described herein in detail. 
     One difference between the tiller assembly  1500  and the tiller assembly  1400  is that in the tiller assembly  1500 , the base  1502  defines smooth frusto-conical male tapered surfaces  1504  on lateral sides thereof. More particularly, as shown in  FIG. 15 , each of the frusto-conical male tapered surfaces  1504  is coaxial with the axis of rotation  1506  and extends laterally outward away from respective ones of the lateral sides of a central portion  1508  of the base  1502 . 
     Accordingly, in the tiller assembly  1500 , each of the clamping fittings  1510  defines a smooth frusto-conical female tapered surface  1512  on an inward lateral side thereof, and a splined cylindrical outer surfaces  1514  disposed circumferentially about the frusto-conical female tapered surface  1512 . The frusto-conical female tapered surfaces  1512  and the splined cylindrical outer surfaces  1514  of the clamping fittings  1510  are all coaxial with the axis of rotation  1506 . 
     Similar to the tiller assembly  124 , the tiller arm  1516  of the tiller assembly  1500  has two arms  1518  at a rear end thereof. The arms  1518  are disposed on respective ones of the lateral sides of the central portion  1508  of the base  1502 . To help with assembly of the tiller assembly  1500 , the left arm  1518  of the tiller arm  1516  is removably attached, via bolts  1530 , to the right tiller arm  1518 . It is contemplated that the left arm  1518  of the tiller arm  1516  could be removably attached to the right tiller arm  1518  via any other suitable removable attachment means. 
     It is also contemplated that another part of the tiller assembly  1500  could be made removable to facilitate assembly of the tiller assembly  1500 . It is also contemplated that the arm(s)  1518  need not be detachable and instead the base  1502  could define recesses coaxially with the axis of rotation  1506 . In such embodiments, the frusto-conical male tapered surfaces  1504  of the base  1502  could be defined inside such recesses. Such recesses could be shaped similar to the recesses  1402  of the tiller assembly  1400 , which in that embodiment are defined in the tiller arm  1404  of the tiller assembly  1400 . 
     In the tiller assembly  1500 , the arms  1518  of the tiller arm  1516  are pivotably connected to the base  1502  to pivot about the axis of rotation  1506 . More particularly, similar to the tiller assembly  124 , the splined cylindrical outer surfaces  1514  of the clamping fittings  1510  of the tiller assembly  1500  are splined to corresponding splined apertures  1520  defined in respective ones of the arms  1518 . Thus, the clamping fittings  1510  are slidable relative to the tiller arm  1516  along the axis of rotation  1506  and are rotationally fixed relative to the tiller arm  1516  and the axis of rotation  1506 . Also similar to the tiller assembly  124 , the clamping fittings  1510  are received over a shaft  1522 . The shaft  1522  is received through a smooth axial aperture  1524  defined through the base  1502 . The axial aperture  1524  in the base  1502  is coaxial with the axis of rotation  1506 . Therefore, the shaft  1522  is slidable relative to the base  1502  along the axis of rotation  1506 . 
     Similar to the tiller assembly  124 , in the tiller assembly  1500  the left end of the shaft  1522  is threaded into a matching threaded axial aperture (not separately labeled) defined in the left clamping fitting  1510 . The right end of the shaft  1522  is received in and fixed to a handle  1526 . Also similar to the tiller assembly  124 , the shaft  1522  passes through a smooth axial aperture (not separately labeled) defined through the right clamping fitting  1510  and receives thereon a pair of resilient washers  1528 . The shaft  1522  is slidable relative to the right clamping fitting  1510 . 
     The pair of resilient washers  1528  is disposed between the handle  1526  and the right clamping fitting  1510 , and is compressed by the handle  1526  against the lateral right side of the right clamping fitting  1510 . The pair of resilient washers  1528  thereby press the female tapered surface  1512  of the right clamping fitting  1510  against the male tapered surface  1504  of the base  1502 . 
     Operation of the tiller assembly  1500  is similar to the operation described above with respect to the tiller assemblies  124  and  1400  and is therefore not described in more detail herein. 
     It is contemplated that the tiller assemblies described herein above could be provided as tiller assembly kits. It is contemplated that the tiller assembly kits could be used in the assembly of new marine outboard engines or to replace existing tiller assemblies of at least some existing marine outboard engines. For example, a tiller assembly kit for assembling the tiller assembly  124  described above could contain the base  142 , the tiller arm  126 , the shaft  174 , the washers  180 ,  218 , the handle  182 , and the clamping fittings  192 ,  194 . The tiller assembly kit could also contain the circlip  183  for the left end  176  of the shaft  174  and instructions on how to assemble the tiller assembly  124  and mount the tiller assembly to a marine outboard engine. It is also contemplated that the tiller assembly kit for assembling the tiller assembly  124  could include adapter hardware permitting mounting of the tiller assembly  124  onto different models and brands of marine outboard engines. 
     It is contemplated that any suitable material(s) and manufacturing methods could be used, so long as the functionality described in this document is provided. Modifications and improvements to the above-described embodiments of the present technology may become apparent to those skilled in the art. The foregoing description is intended to be exemplary rather than limiting.