Note: Descriptions are shown in the official language in which they were submitted.
CA 02555039 2006-08-23
1
TRACK FOR A SNOW VEHICLE
FIELD OF THE INVENTION
The invention relates generally to a cycle type snow vehicle designed for
banked turning, and, more particularly, to an improved track for a cycle type
snow
vehicle.
BACKGROUND OF THE INVENTION
A variety of vehicles have been designed for travel over snow, with the well
known snowmobile type being by far the most prevalent and commercially
successful.
Snowmobiles have evolved into highly refined and capable vehicles for travel
over
snow and are used predominantly for recreation. Yet, these commercially
available
snowmobiles exhibit a number of undesirable features and characteristics that
limit
their agility and versatility. They are generally quite heavy, weighing
typically from
400 to 600 pounds, and require powerful motors to provide power-to-weight
ratios
sufficient for high performance in highly variable power-sapping snow
conditions and
for the wide furrows they plow through the snow. A snowmobile typically has
two
outboard steering skis and a relatively wide, flat track. The outrigger
positioning of
the skis and the wide flat track constrain the snowmobile to travel flat upon
the snow
and inhibit banked or leaned turning. These features also tend to limit the
steepness
of slope that the snowmobile can traverse, since the snowmobile can easily
slide
sideways when traveling across a steep slope. When cornering on hard packed
snow, a snowmobile cannot be easily banked to achieve tight-radius cornering,
and
the operator must move his or her body far to the inside of the turn to avoid
tipping or
side slipping the snowmobile.
A second much less common type of snow vehicle is the snow bike or snow
cycle. These vehicles are generally smaller and lighter than snowmobiles. Snow
cycle designs are usually based upon off-road motorcycles or scooters with the
front
wheel replaced by a ski and the rear wheel replaced by an endless loop
traction belt,
commonly called a track. Snow cycles are vehicles designed for banked turning
like
a motorcycle or bicycle, and are operated "in balance". Snow cycles typically
have a
single steering ski and a relatively narrow track located behind and in line
with the
single ski. In turns, a snow cycle is leaned sideways in the direction of the
turn
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
2
such that the sum of gravitational and centrifugal forces acting on the
vehicle and
operator bears centrally on the contact areas between the snow and the ski and
between the snow and the track. In this way, the snow cycle and rider remain
in
balance through the turn. When traversing slopes, a snow cycle maintains a
vertical
position such that the gravitational forces acting on the snow cycle and
operator
intersect the approximate center of the contact areas between the snow cycle
ski
and the snow and between the track and the snow.
Motor-driven snow cycles are described in U.S. patent numbers 5,474,146,
4,613,006 and 4,442,913. None of these snow cycles have achieved notable
commercial success. The snow cycles described in the '006 and '913 patents
have
minimal suspension travel between the ski and the vehicle main frame and
between
the track support and the main frame. The ability of their tracks to incline
and
decline relative to their front skis is also limited, reducing the compliance
of their
tracks to varying terrain and limiting traction. While the snow cycle
described in the
'146 patent exhibits improved suspension travel and traction over the earlier
snow
cycles, it does so by using a track carriage that extends rearward from the
snow
cycle, making the snow cycle longer than the snow cycles referenced in the
'006
and '913 patents. Positioning the track so far rearward from the snow cycle
center
of gravity limits the braking effectiveness of the track for slowing and
stopping the
snow cycle.
Human powered snow cycles or "snow bicycles" are also banking snow
vehicles. In snow bicycles, a single ski in front and an endless-loop track in
back
replace the bicycle wheels. Drive power from the operator's legs is
transferred from
a pedal crank through a chain and sprocket drive train to the track. Snow
bicycles
are described in U.S. patent numbers 5,423,559 and 5,102,153. The vehicles
described in these patents exhibit all of the same limitations as conventional
motor
driven snow cycles. In addition, the absence of shock absorbers or some other
type
of suspension between the tracks and the frames of these snow bicycles limits
traction and results in an uncomfortable ride over rough terrain.
SUMMARY OF THE INVENTION
The present invention is directed to a cycle type snow vehicle that offers
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/tlS99/03868
3
improved agility and maneuverability in snow conditions ranging from powder
snow
to hard packed snow and ice and over varying terrain topography. The snow
cycle
is designed to emulate the steering and balancing characteristics of
motorcycles and
bicycles to make it easier and more natural for the operator to ride and
control.
Unlike conventional snow cycles that deliver power to the front of the track,
the
snow cycle of the present invention delivers power to the back of the track.
The
track extends forward from the drive wheel to position the track substantially
under
the snow cycle for improved propulsion and braking traction. The scissors-type
configuration of the swingarm and track also helps reduce the overall length
of the
snow cycle. A novel track carriage suspension improves tractional compliance
of
the track to the snow surface over varying terrain topography. A gyroscopic
stabilizer and steering aid coupled to the front steering fork helps the snow
cycle
handle and balance more like a motorcycle or bicycle. The track design
utilizes a flat
belt to enhance edging and support in soft snow. Traction paddles that are
quite
stiff with paddle tips having laterally convex curvature are deployed to allow
the
snow cycle to be easily leaned or banked on hard packed snow or ice. The
traction
paddles are formed with block-shaped features having side surfaces that help
reduce
side slipping of the track when the snow cycle is banked in turning or is
traversing
steep slopes. Ice runners with ice piercing edges are deployed adjacent to the
track
edges to dig into ice or hard-pack snow to further inhibit side-slipping when
the
snow cycle is steeply banked on ice and hard-pack snow.
The snow vehicle of the present invention includes a frame, a ski, an arm, a
track carriage, a drive wheel, and an endless loop track. The ski is rotatably
coupled
to the frame through, for example, a steering member that has an upper portion
connected to the frame and a lower portion mounting the ski. The steering
member,
such as the front fork of a motorcycle or bicycle, would be connected to the
frame
so that it rotates about a steering axis like the front fork and wheel of a
motorcycle
or bicycle. The forward portion of the arm is mounted to the frame. The
rearward
portion of the track carriage is mounted to the rearward end of the arm. A
rotatable
drive wheel is mounted to the rearward portion of the track carriage. The
track is
coupled to and extends forward from the drive wheel and circulates in a fixed
path
around the track carriage. In one embodiment, the snow vehicle includes a
motor
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
4
operatively coupled to the drive wheel to drive the track and propel the
vehicle over
the snow. In another embodiment, the vehicle includes a pedal crank
operatively
coupled to the drive wheel for human-powered propulsion over the snow.
In one embodiment of both the motor-powered and the human-powered snow
cycles, the arm is a swing arm that is hinged at its forward end to the snow
cycle
main frame. The back of the track carriage is hinge mounted to the rear of the
swing arm. This hinged mounting is implemented, for example, by an axle that
extends between the prongs of a forked swing arm. The rear of the track
carriage
and the drive wheel are supported on the axle. This hinge mounting and
positioning
of the track carriage beneath the swing arm in a scissors-type configuration
enables
the track carriage to move vertically under the snow cycle, and allows the
track
carriage to incline and decline to follow the snow surface to maintain
traction upon
the snow. In one version of this embodiment, the combined mass of the vehicle
and
operator is cushioned upon both the front and back of the track carriage by a
single
shock absorber combined with a force-distributing bell crank. The force-
distributing
bell crank distributes the vehicle suspension force from the shock absorber to
the
back of the track carriage through the swing arm and to the front of the track
carriage through a connecting rod. Additionally, the bell crank can pivot to
allow the
track carriage to incline and decline without a change in the force exerted
upon the
bell crank pivot by the shock absorber.
In another embodiment of the snow vehicle, a snow compacting ramp is
attached to the front of the track carriage. The ramp is positioned forward of
the
track and it is inclined upward away from the track to progressively compress
the
snow ahead of the track for improved traction and to prevent snow from packing
in
front of the track.
In another embodiment, the snow vehicle includes a gyroscopic stabilizer and
steering aid. The stabilizer consists of a gyroscope mounted or coupled to the
steering member and, preferably, an electric drive motor to spin the
gyroscope. The
spinning gyroscope tends to stabilize the ski in its steered direction by
generating
forces in response and opposition to forces that tend to deflect the ski from
its
steered direction. The gyroscope also automatically initiates the re-balancing
of the
snow vehicle when it becomes deflected and tipped out of balance by generating
an
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
instantaneous steering torque in response to the deflection. This response
torque
steers the ski in the direction toward which the vehicle is being tipped and
the
forward motion of the snow cycle brings the ski back under the center of the
vehicle, helping to bring the vehicle back upright and in balance.
5 Relating to the following descriptions of structure and operation for the
snow
cycle and snow bicycle embodiments, and also relating to the claims, unless
expressly stated clearly and unambiauouslv otherwise in this Specification or
in the
Claims, "a" something means one or more of that something. For example, "a
ski"
in Claim 1 means one or more skis, and "a drive wheel" in Claim 1 means one or
more drive wheels.
DESCRIPTION OF THE DRAWINGS
Fig. 1 is a side view of one embodiment of the snow cycle of the present
invention.
Fig. 2 is a front view of the snow cycle of Fig. 1.
Fig. 3 is a rear view of the snow cycle of Fig. 1.
Fig. 4 is an exploded assembly side view of the snow cycle of Fig. 1
Fig. 5 is an enlarged side view of the rear portion of the snow cycle of Fig.
1.
Fig. 6 is a detail side view of the track carriage of the snow cycles of Fig.
1
and Fig. 34. This view shows the track carriage removed from the snow cycle
swing arm frame. The track shield, track carriage suspension frame and snow
compacting ramp are removed, and are not shown in this view.
Fig. 7 is an isometric view of the track carriage of Fig. 6.
Fig. 8 is an exploded view of the track carriage of Fig. 7.
Fig. 9 is a sectional view of the track carriage of Fig. 6 along the section
line
9-9 in Fig. 6.
Fig. 10 is a sectional view of the track carriage of Fig. 6 along the section
line 10-10 in Fig. 6.
Fig. 11 is a sectional view of the track carriage of Fig. 6 along the section
line 11-11 in Fig, 6.
Fig. 12 is an isometric view of a sectioned portion of the track of the snow
cycles of Fig. 1 and Fig. 34 illustrating the track belt, traction paddles and
slide
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
6
bearing clips.
Fig. 13 is an enlarged side view of the snow compacting ramp assembly of
the snow cycle of Fig. 1.
Fig. 14 is an enlarged side view of the intermediate hub, disc brake, and
drive
chains of the snow cycle of Fig. 1
Fig. 15 is a top rear view of the intermediate hub and the swing arm pivot
connection to the main frame of the snow cycle of Fig. 1., as viewed from the
view
line 15-15 indicated in Fig. 14.
Fig. 16 is a side view of the rear portion of the snow cycle of Fig. 1
illustrating an alternate embodiment the track suspension having a single
shock
absorber, a bell crank, and a connecting rod.
Fig. 17 is a side view of the rear portion of the snow cycle of Fig. 1
illustrating a second alternate track suspension embodiment having a single
shock
absorber, a bell crank, and a connecting rod.
Fig. 18 is a side view of the rear portion of the snow cycle of Fig. 1
illustrating a third alternate track suspension embodiment using two shock
absorbers.
Fig. 19 is a side view of the rear portion of the snow cycle of Fig. 1
illustrating a fourth alternate track suspension embodiment using a single
shock
absorber.
Fig. 20 is a side view of the front portion of the snow cycle of Fig. 1,
illustrating the telescoping steering fork, extension frame, ski and ski pivot
bracket,
and the enclosed gyroscopic stabilizer and steering aid.
Fig. 21 is a side view of an electric motor-driven embodiment of the
gyroscopic stabilizer and steering aid, steering extension frame, and ski. For
clarity
of illustration, this view is shown with the gyroscope covers removed and
without
the telescoping steering fork attached.
Fig. 22 is a front view of the gyroscopic stabilizer and steering aid,
steering
extension frame, and ski of Fig. 21.
Fig. 23 is a side view of an alternate electric motor drive embodiment of the
gyroscopic stabilizer and steering aid with steering extension frame and ski.
For
clarity of illustration, this view is shown with the gyroscope covers removed
and
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
7
without the telescoping steering fork attached.
Fig. 24 is a front view of the gyroscopic stabilizer and steering aid,
steering
extension frame, and ski of Fig. 23.
Fig. 25 is a top view of the gyroscope motor controller and control box with
operator controls, all mounted to the upper triple clamp forward of the
handlebar.
Fig. 26 is a circuit diagram of a servo input circuit for the gyroscope motor
controller of Fig. 25. Electrical voltage waveforms are shown for
clarification of the
electronic signal processing.
Fig. 27 is a top rear view of the intermediate hub and disc brake showing the
electronic tachometer.
Fig. 28 is a side view of a mechanical drive embodiment of the gyroscopic
stabilizer and steering aid, steering extension frame, and ski. This view
illustrates
the driven end of a flexible shaft and driven-end bevel gears of a mechanical
transmission coupling the intermediate hub to the gyroscope. For clarity of
illustration, this view is shown with the gyroscope covers removed and the
telescoping steering fork removed.
Fig. 29 is a front view of the gyroscopic stabilizer and steering aid,
steering
extension frame, and ski of Fig. 28.
Fig. 30 is a top rear view of the intermediate hub and driving end of the
mechanical gyroscope drive embodiment of Figs. 28 and 29, illustrating the
driving
end bevel gears.
Fig. 31 is an exploded view of the gyroscope, viscous coupler and driven-end
bevel gear of the mechanical drive embodiment of the gyroscopic stabilizer and
steering aid of Figs. 28 and 29.
Fig. 32 is a side view of a portion of the snow cycle of Fig. 1 with an
alternate embodiment of the gyroscopic stabilizer and steering aid. This view
illustrates an electric motor driven gyroscope mounted in a rotatable
gyroscope
carriage suspended rearward in the snow cycle frame. For clarity of
illustration, this
view is shown with the gyroscope covers removed and portions of the snow cycle
body, saddle, and gas tank cut away.
Fig. 33 is an enlarged side partial view of the gyroscopic stabilizer and
steering aid of Fig. 32.
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 9s/43540 Pcr/1JS99/03868
8
Fig. 34 is a side view of a human-powered snow bicycle according to the
present invention.
Fig. 35 is a front view of the snow bicycle of Fig. 34.
Fig. 36 is a rear view of the snow bicycle of Fig. 34.
Fig. 37 is an exploded assembly side view of the snow bicycle of Fig. 34.
Fig. 38 is an enlarged side view of the rear portion of the snow bicycle of
Fig.
34.
Fig. 39 is an enlarged rear view of the swing arm frame and intermediate hub
of the snow bicycle of Fig. 34 along the view line 39-39 of Fig. 38.
Fig. 40 is an enlarged front view of the gyroscope and driven-end bevel gears
of the snow bicycle of Fig. 35. For clarity of illustration, this view is
shown with
the gyroscope covers removed and without the telescoping steering fork
attached.
Fig. 41 is an exploded view of the intermediate hub, brake disc, gyroscope
driving-end bevel gears and chain sprockets of the snow bicycle of Fig. 34.
Fig. 42 is an exploded view of the gyroscope, viscous coupler, freewheel,
and driven-end bevel gear of the gyroscopic stabilizer and steering aid of the
snow
bicycle of Fig. 34.
Fig. 43 is a sectional view of the track carriage and track of the snow cycle
of Fig. 1, illustrating a banked turn on ice.
Fig. 44 is a sectional view of the track carriage and track of the snow cycle
of Fig. 1, illustrating a banked turn in soft or powder snow.
Fig. 45 is a sectional view of the track carriage and track of the snow cycle
of Fig. 1, illustrating a banked turn on a hard-pack snow surface.
Fig. 46 is a sectional view of the track carriage and track of the snow cycle
of Fig. 1, illustrating a banked turn on moderately packed snow.
Fig. 47 is a side view of the snow cycle of Fig. 1 with the shock absorber
and telescoping steering fork maximally loaded and compressed as would occur
in
high G-force loading of the snow cycle track suspension and telescoping
steering
fork. The unloaded, uncompressed positions of the track carriage, snow
compacting
ramp assembly, ski, extension frame and other associated components are
illustrated using phantom lines.
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT1US99/03868
9
DETAILED DESCRIPTION OF THE INVENTION
SNOW CYCLE STRUCTURE
Figs. 1-3 illustrate from the side, front and rear, respectively, a motor
driven
cycle type snow vehicle designated generally by reference number 10. Fig. 4 is
an
exploded assembly side view of snow cycle 10. Snow cycle 10 may include many
parts typical of a conventional off-road motorcycle. For example, and
referring to
Figs. 1-4, snow cycle 10 includes a telescoping steering fork 12, a main frame
14, a
saddle 16, a gasoline motor 18, a transmission 20, a fuel tank 22, a body 24,
and a
head tube 26. Steering fork 12 is an elongated steering member that is
supported
by and rotates in head tube 26. Each prong of steering fork 12 is typically
constructed as a combination of telescoping upper and lower members, referred
to
herein as fork tubes 34 and fork sliders 36. Fork tubes 34 and a head pipe 32
(visible only in Fig. 2) are clamped in position by upper and lower triple
clamps 30.
Head pipe 32 rotates in head tube 26. Fork tubes 34 slide in and out of fork
sliders
36. Springs and hydraulic damping mechanisms inside the fork tubes and fork
sliders provide spring support and shock absorption to cushion the front end
of snow
cycle 10 upon a ski 204. A handlebar 38 is attached to the top of upper triple
clamp 30. As best viewed in Figs. 2 and 3, a clutch control lever 40 is
attached to
the left hand side of handlebar 38 and a throttle control 42 is mounted on the
right
hand side of handlebar 38. A headlight 44 is mounted to steering fork 12 to
point in
the steered direction of the snow cycle. A gearshift control lever 46
connecting to
transmission 20 is positioned forward of left footrest 28a. A brake lever
pedal 48
(visible in Figs. 2 and 3) is positioned forward of right footrest 28b. An
exhaust pipe
50 exits the front of gasoline motor 18, routes alongside the gasoline motor,
and
attaches to the front of a muffler 52. A pair of motor cooling radiators 54
(visible in
Fig. 2) mount to the forward portion of main frame 14, and are enclosed on the
sides by a pair of radiator shrouds 56.
Track Susaension,`Snow Ramp and Drive Train
Referring now also to Figs. 5, 14 and 15, a swing arm pivot axle 60 is
attached to main frame 14 at left and right swing arm pivot mounts 58. Swing
arm
pivot axle 60 extends through and is supported by two swing arm support bosses
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99143540 PCT/US99/03868
62 (visible in Fig. 15). Swing arm support bosses 62 are attached to and part
of
main frame 14. Swing arm pivot axle 60 serves as a stationary non-rotating
axle on
which a swing arm 64 pivots. An intermediate hub 66 that rotates on ball
bearings
is also mounted on swing arm pivot axle 60.
5 Referring to Figs. 4 and 5, a left track carriage pivot bracket 82a and a
right
track carriage pivot bracket 82b bolt to the left and right sides,
respectively, of the
lower rear portion of swing arm 64. Brackets 82 mount a pair of track carriage
pivot
bearings 84 ( shown in Figs. 4 and 8). A cogwheel axle 88 extends through
track
carriage pivot bearings 84. A track carriage 86 pivots relative to swing arm
64 on
10 cogwheel axle 88. Swing arm 64 also includes left and right swing arm
braces 106.
Left swing arm brace 106 attaches to the left side of the forward upper end of
swing arm 64 and extends back and downward to attach to left track carriage
pivot
bracket 82a. Right swing arm brace 106 (not visible) attaches below the
forward
upper end of the right side of swing arm 64 and mounts to right track carriage
pivot
bracket 82b. Swing arm braces 106 strengthen the combined structure comprising
swing arm 64, left and right swing arm braces 106, and left and right track
carriage
pivot brackets 82. The combined swing arm structure comprising swing arm 64,
left and right swing arm braces 106, and left and right track carriage pivot
brackets
82 forms a stiff cantilever suspension arm that pivots vertically around swing
arm
pivot axle 60. A grab handle 110 attaches to the rear of swing arm 64 and
facilitates lifting and dragging the snow cycle.
Referring now to Figs. 6-8, track carriage 86 attaches pivotably at cogwheel
axle 88 to the rear of the combined swing arm structure and pivots vertically
under
swing arm 64. An endless-loop track 138 is carried by track carriage 86 and
circulates around the periphery of the track carriage. The swing arm structure
and
pivot connections to track carriage 86 allow the track carriage to move
scissors-
fashion vertically under swing arm 64 while maintaining a level orientation,
inclining,
or declining to enable track 138 to maintain traction with the terrain below
the snow
cycle.
The construction of track carriage 86 is illustrated in Figs. 6-11. Track
carriage 86 includes a track carriage frame 112, a left track slide rail 1 14a
attached
to the left side of track carriage frame 112, a right track slide rail 1 14b
attached to
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
11
the right side of track carriage frame 112, and a pair slide runners 116
mounted
along the bottoms of track slide rails 114. Slide runners 116 are, preferably,
manufactured from a durable high-density plastic having good friction and wear
properties. A left ice runner support 1 58a is mounted to left slide rail
114a, and a
right ice runner support 1 58b is mounted to right slide rail 114b. Ice
runners 160
are attached to the lower edges of ice runner supports 158. Ice runners 160
should
be made of tungsten carbide alloy or another suitably hard material to provide
sharp,
durable, ice-piercing edges.
Cogwheel axle bearings 118 (visible in Figs. 8, 9, and 11) mount in slide
rails
114. Cogwheel axle 88 is supported by and rotates in cogwheel axle bearings
118
and also mounts and rotates in track carriage pivot bearings 84. This
structure
allows cogwheel axle 88 to function as a hinge pivot between track carriage 86
and
the combined swing arm structure comprising swing arm 64, braces 106, and
brackets 82. A cogwheel axle sprocket 120 is mounted to the left end of
cogwheel
axle 88. Two drive wheels, called cogwheeis 122, are mounted to the central
portion of cogwheel axle 88. A swing arm pivot brace rod 124 (visible in Figs.
7-9)
is mounted between track carriage pivot brackets 82 to help maintain the
correct
spacing and alignment of track carriage pivot bearings 84.
Two guide wheels 126 are mounted to and rotate on a fixed guide wheel axle
130. Guide wheel axle 130 is mounted into left and right track tension
adjusters
132 that are attached to each side of the forward portion of track carriage
frame
112. The position and alignment of guide wheel axle 130 in track carriage
frame
112 may be adjusted by, for example, the externally threaded rods and
adjusting
nuts illustrated in Figs. 6-9 as track tension adjusters 132. Idler wheels 134
are
mounted to and rotate on fixed idler wheel axles 136. The ends of Idler wheel
axles
136 are mounted to the middle portions of track slide rails 114. Rotation of
guide
wheels 126 and idler wheels 134 on their respective axles is facilitated by
bearings
128.
As illustrated in Figs. 6 and 9-11, track 138 circulates around track carriage
frame 112, and is moveably guided and supported by drive cogwheels 122, guide
wheels 126, idler wheels 134, and slide runners 116. Driving and braking
forces are
delivered to track 138 by the engagement of cogwhQels 122 with cogwheel lugs
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
12
150. Tensioning and alignment of track 138 upon track carriage 86 is
accomplished
by the positioning of guide wheels 126 using track tension adjusters 132.
The components of track 138 are illustrated in Fig. 12, and are also visible
in
Figs. 9-11. Referring to Fig. 12, track 138 includes a track belt 140, design
A
traction paddles 142a, design B traction paddles 142b, cogwheel lugs 150,
reinforcing rods 152, and slide bearing clips 154. Track belt 140 is formed in
an
endless loop, and may be made of any flexible reinforced rubber compound or
similarly strong flexible material such as that used for conventional
snowmobile
tracks. Traction paddles 142 and track cogwheel lugs 150 are, preferably, also
lo made of a strong flexible rubber compound molded to track belt 140.
Traction
paddles 142 include a multitude of traction paddle blocks 146. Blocks 146 have
a
generally rectangular cross section and are tapered in both cross-sectional
dimensions from base to tip. Traction paddle blocks 146 provide a multitude of
broad side surfaces 145 that serve as lateral snow traction surfaces. Traction
paddle webs 148 extend between selected traction paddle blocks 146 to form
snow
traction surfaces for vehicle propulsion and braking. Reinforcing rods 152
extend
laterally across track belt 140 at the bases of traction paddles 142, and are
encased
by the same material from which traction paddles 142 are formed. Traction
paddles
142 and reinforcing rods 152 extend laterally beyond the sides of track belt
140,
leaving track belt openings 155 between the ends of adjacent traction paddles.
Reinforcing rods 152 are made of fiberglass, carbon fiber, or other suitable
rigid,
strong, lightweight material. Slide bearing clips 154 are clamped around the
rubber-
encased ends of reinforcing rods 152 to provide durable bearing and guide
surfaces
to bear upon slide runners 116. Slide bearing clips 154 should be made of
steel or
some other suitably wear resistant material.
A track suspension is desirable to support and cushion snow cycle 10 and
the operator upon track carriage 86. In one embodiment of a track suspension
for
snow cycle 10 illustrated in Figs. 1, 4 and 5, a shock absorber 68 is mounted
pivotably to a frame suspension mount 70 of main frame 14, and to a bell crank
first
arm pivot 78 of a bell crank 72. As shown in Figs. 4 and 5, a bell crank
fulcrum
pivot 74 attaches to a swing arm suspension mount 76 on swing arm 64 such that
bell crank 72 can pivot upon swing arm 64. Shock absorber 68 is operatively
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PC.'T/US99/03868
13
coupled to swing arm 64 through bell crank 72. Shock absorber 68 is also
operatively coupled to the forward end track carriage 86 through bell crank
72, a
connecting rod 98, and a track carriage suspension frame 90. Suspension frame
90
comprises left and right side brackets 92 and a top bracket 94 and serves as a
suspension mount for the front of track carriage 86. Side brackets 92 attach
to the
sides of track carriage frame 112, and top bracket 94 spans across the top of
track
138 and a track shield 156, and attaches to left and right side brackets 92.
Track
shield 156 attaches to top bracket 94 and a track shield support 157 (visible
in Fig.
4 only) and covers the upper run of track 138. Connecting rod 98 includes a
shaft
100, an upper rod end 102 which can be adjustably screwed in to or out of
shaft
100, and a lower rod end 104 which can likewise be adjustably screwed in to or
out
of shaft 100. Lower rod end 104 of connecting rod 98 mounts selectively into
one
of pivot connections 96 in top bracket 94. Upper rod end 102 of connecting rod
98
mounts selectively into one of bell crank second arm pivot connections 80. The
length of connecting rod 98 can be adjusted, for example, by screwing the
threaded
sections of upper rod end 102 and lower rod end 104 into or out of shaft 100.
The
track loading distribution and track suspension characteristics can be
modified by
adjusting the length of connecting rod 98 and/or by selectively changing pivot
connection 80 and/or pivot connection 96 to which connecting rod 98 attaches.
Bell crank 72 apportions the suspension force from shock absorber 68 to swing
arm
64 and to the forward end of track carriage 86 through connecting rod 98 and
suspension frame 90. The suspension force apportioned to the swing arm urges
it
pivotally downward around swing arm pivot axle 60. The suspension force
apportioned to the forward end of track carriage 86 urges the track carriage
pivotally
downward around cogwheel axle 88 that functions as the pivot connection
between
track carriage 86 and swing arm 64. The suspension forces of shock absorber 68
are thus distributed to both the rearward and forward ends of track carriage
86 in a
predetermined proportion to affect a pre-determined longitudinal loading
distribution
along the length of the ground-contacting run of track 138. Snow cycle 10 and
the
operator are thus cushionably supported upon the ground-contacting run of
track
138.
An alternate embodiment of a track carriage suspension using a single shock
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
14
absorber, a bell crank, and a connecting rod is illustrated in Fig. 16. As
shown in
Fig. 16, shock absorber 68 is pivotally connected between a swing arm
suspension
mount 76' of a swing arm 64 and a bell crank first arm pivot 78' of a bell
crank 72'.
A fulcrum pivot 74' of bell crank 72' mounts rotatably to a frame suspension
mount
70' of main frame 14. Two connecting rods 98' are used, with the upper ends of
connecting rods 98' connecting on opposite sides of bell crank 72' to one of a
set of
bell crank second arm pivot connections 80'. Connecting rods 98' extend
downward on opposite sides of swing arm suspension mount 76' and shock
absorber 68 and the lower ends of connecting rods 98' connect selectively into
one
of the pivot connections 96 of a track carriage suspension frame 90. Only one
of
connecting rods 98' is visible in Fig. 16, the right side connecting rod 98'
being
behind and obscured by the left side connecting rod 98' in this view. Bell
crank 72'
apportions suspension force from shock absorber 68 through swing arm 64 to the
rearward end of track carriage 86 and through connecting rods 98' and
suspension
frame 90 to the forward end of track carriage 86. The suspension force is
apportioned to establish a predetermined loading distribution along the length
of the
ground-contacting run of track 138. Bell crank 72' of this embodiment
additionally
has a suspension stop bumper 73 that contacts the top of suspension mount 76'
to
prevent the forward end of track carriage 86 from pivoting below and away from
swing arm 64 further than is desirable.
A third configuration of a track carriage suspension comprising a single shock
absorber, bell crank and connecting rod is shown in Fig. 17. A fulcrum pivot
74" of
a bell crank 72" mounts to a swing arm suspension mount 76" on the lower
rearward portion of a swing arm 64. Shock absorber 68 connects pivotably
between a pivot connection 96' on top bracket 94' of suspension frame 90 and a
first arm pivot 78" of bell crank 72". A connecting rod 98" connects pivotably
between a frame suspension mount 70" of main frame 14 and one of a set of
second arm pivot connections 80" of bell crank 72". Shock absorber 68 applies
suspension cushioning force between track carriage suspension frame 90 and
first
arm pivot 78" of bell crank 72". This force urges track carriage 86 downward
around its hinge connection with track carriage pivot brackets 82 at cogwheel
axle
88, and simultaneously urges bell crank 72" around bell crank fulcrum pivot
74" in
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
a counter-clockwise direction as viewed in Fig. 17. Bell crank 72" transmits
this
force to second arm pivot connection 80" with connecting rod 98", creating a
compression force through connecting rod 98" to frame suspension mount 70".
The force couple established in bell crank pivot connection 80" and fulcrum
pivot
5 74" urges swing arm 64 downward around swing arm pivot axle 60. Bell crank
72"
apportions the cushioning force from shock absorber 68 between swing arm 64
and
the forward end of track carriage 86, and between main frame 14 and swing arm
64. Suspension forces from shock absorber 68 are thus distributed in pre-
determined proportion to the rearward and forward ends of track carriage 86,
10 thereby cushioning the weight of snow cycle 10 and the operator upon track
carriage 86 while establishing a pre-determined longitudinal loading
distribution
between track 138 and the snow.
Three different ways have been described and illustrated in Figs. 5, 16 and
17 for a single shock absorber, a force-distributing bell crank and a
connecting rod
15 to be used in combination as a track carriage suspension for snow cycle 10.
Considering the shock absorber, bell crank, and connecting rod in pivotally-
connected combination, but separated from snow cycle 10, there remain three
open
pivots. These three pivots comprise the bell crank fulcrum pivot, a shock
absorber
end pivot, and a connecting rod end pivot. There are six different ways or
combinations in which these three open pivot connections can be individually
and
exclusively connected into suspension pivot mounts on main frame 14, swing arm
64, and track carriage suspension frame 90. Three of these six possible
connection
combinations have been described and illustrated in Figs. 5, 16, and 17. There
exist
three other pivot connection combinations of the six possible combinations
that
enable the forces from a single shock absorber to be distributed by the bell
crank in
pre-determined proportion to the rearward and forward ends of the track
carriage. It
is believed the three remaining connection combinations are less practical
than those
that have been described and illustrated, and so they are not shown or
described in
detail, but are summarized as follows:
1. The shock absorber connected pivotably between the track
carriage and the bell crank first arm; the bell crank fulcrum connected
pivotably to the snow cycle main frame; and the connecting rod
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
16
connected pivotably between the bell crank second arm and the swing
arm.
2. The shock absorber connected pivotably between the swing arm
and the bell crank first arm; the bell crank fulcrum connected pivotably to
the track carriage; and the connecting rod connected pivotably between
the bell crank second arm and the snow cycle main frame.
3. The shock absorber connected pivotably between the main frame
and the bell crank first arm; the bell crank fulcrum connected pivotably to
the track carriage; and the connecting rod connected pivotably between
the bell crank second arm pivot and the swing arm.
One embodiment of a track suspension for snow cycle 10 that uses two
shock absorbers is illustrated in Fig.18. Shock absorber 68 and a second shock
absorber 69 each provides both spring and damping cushioning forces using, for
example, a coil spring and a hydraulic damper. Shock absorber 68 is connected
between frame suspension mount 70 and a swing arm suspension mount 76"', and
urges a swing arm 64 pivotally downward around swing arm pivot axle 60. Second
shock absorber 69 is connected pivotably between a lower swing arm suspension
mount 77 of swing arm 64 and one of pivot connections 96 in top bracket 94.
The
force of second shock absorber 69 is applied between swing arm 64 and
suspension
frame 90 to urge track carriage 86 pivotally downward around the pivot
connection
on cogwheel axle 88 between track carriage 86 and track carriage pivot
brackets
82. The cushioning forces of shock absorbers 68 and 69 are distributed to the
rearward and forward ends of track carriage 86 to establish a predetermined
loading
distribution along the length of the ground-contacting run of track 138. Snow
cycle
10 and the operator are thus cushionably supported upon the ground-contacting
run
of track 138.
A track suspension embodiment using a single shock absorber is shown in
Fig. 19. A frame suspension mount 70"' is located on a portion of main frame
14'
that extends rearward under saddle 16. Track carriage suspension frame 90 is
attached to a track carriage frame 112' at a location further rearward
compared to
the location of suspension frame 90 on track carriage frame 1 12 of the
previously-
described embodiments. Suspension frame 90 is also mounted in a reversed
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
17
orientation in this embodiment. A shock absorber 68' connects pivotally
between
frame suspension mount 70"' and one of pivot connections 96 of top bracket 94
to
cushionably support snow cycle 10 and the operator upon track carriage 86.
Referring now to Figs. 2, 4, and 13, a snow compacting ramp assembly 162
is pivotally attached to the front of track carriage 86 and to the bottom of
main
frame 14. As shown in Fig. 13, ramp assembly 162 includes a ramp frame 164, a
ramp 166 secured to the bottom of ramp frame 164, a snow cover 168 enclosing
the top of the ramp assembly, and a pair of ramp pivot links 170. Preferably,
ramp
166 is made from ultra-high molecular weight plastic to provide a(ow friction
ramp
surface that is durable, fracture resistant, and abrasion resistant. Ramp
frame 164
is slightly wider than track carriage 86 and extends around the forward sides
of
track carriage 86 and attaches pivotally to the ends of guide wheel axle 130
to form
a hinge between ramp assembly 162 and track carriage 86. The rearward end of
ramp 166 is located at approximately the same height as the front of the lower
run
of track belt 140 of track 138. The front of ramp frame 164 pivots on the
lower
ends of pivot links 170. The upper ends of pivot links 170 hinge to a pair of
ramp
bosses 172 mounted on the sides of the lower portion of main frame 14. The
front
of ramp frame 164 is supported by pivot links 170 and is constrained in
movement
to an arc around ramp bosses 172 in close proximity to the bottom of main
frame
14. Ramp assembly 162 can incline and decline and move forward and rearward as
necessitated by the suspension motion of track carriage 86 relative to main
frame
14.
The power transmission system of snow cycle 10 will now be described with
reference to Figs. 4, 5, 14 and 15. Drive power for track 138 is provided by
gasoline motor 18, and is delivered through transmission 20 to a transmission
output
shaft 174 that mounts a transmission output shaft sprocket 176. As best viewed
in
Fig. 15, intermediate hub 66 is supported by and rotates on swing arm pivot
axle
60. A primary intermediate sprocket 178 is attached to the inside end of
intermediate hub 66. A secondary intermediate sprocket 180 is attached to the
outside end of intermediate hub 66. A hydraulic disc brake 181 includes a
brake
disc 182 attached to the middle of intermediate hub 66 and a hydraulic brake
caliper
184 that is mounted to main frame 14. Brake caliper 184 straddles brake disc
182
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
18
and forces brake pads against the sides of brake disc 182 during braking of
snow
cycle 10. A primary drive chain 186 wraps transmission output shaft sprocket
176
and primary intermediate sprocket 178 in an endless loop and delivers drive
power
to intermediate hub 66. A secondary drive chain 188 wraps secondary
intermediate
sprocket 180 and cogwheel axle sprocket 120 in an endless loop and delivers
drive
power and braking torque from intermediate hub 66 to cogwheel axle 88. A
secondary chain guide/cover 190 (shown in Figs. 1-5, but removed in Figs. 14
and
for illustration clarity) encloses the upper and lower runs of secondary drive
chain
188, and is attached to left swing arm brace 106a.
10 Steerina Ski, Suspension, and Gyroscopic Stabilizer and Steering Aid
The front suspension, steering ski, and gyroscopic stabilizer and steering aid
will be described. Referring first to Figs. 2, 4, and 20, ski 204 is connected
to
steering fork 12 through a steering extension frame 192. A gyroscopic
stabilizer
and steering aid 250 is mounted to extension frame 192. For convenience,
15 gyroscopic stabilizer and steering aid 250 is sometimes referred to simply
as
stabilizer 250. Extension frame 192 is clamped or otherwise attached to the
lower
portion of steering fork 12. Extension frame 192 allows the use of a
conventional
motorcycle steering fork. A longer steering fork may be used, if desired,
instead of
the combined steering fork 12 and extension frame 192 shown in the drawings.
Also, a monolithic elongated steering member could be substituted for steering
fork
12, in which case stabilizer 250 could mount to the side of the monolithic
steering
member.
Refer now also to Figs. 21 and 22 that show from the side and the front
extension frame 192, ski 204, and stabilizer 250 removed from telescoping
steering
fork 12 for illustration clarity. As illustrated in Fig. 20, fork slider
clamps 194 wrap
around the outsides of the upper middle portions of fork sliders 36 and bolt
to the
top of extension frame 192, clamping the extension frame firmly to the fork
sliders.
A gyro axle 196 is mounted to and extends between the end of each prong of
steering fork 12. Preferably, gyro axle 196 is threaded on one end to
facilitate
clamping the bottom of fork sliders 36 using a threaded axle nut 197 just like
the
front wheel axles of some motorcycles are clamped to the motorcycle fork
sliders.
Gyro axle 196 extends between fork sliders 36 through holes in left and a
right
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
19
mounting brackets 200 welded to the mid portions of the left and right members
of
extension frame 192, serving to rigidly attach extension frame 192 to
telescoping
steering fork 12. As visible in Fig. 4 and Fig. 20, motorcycle brake mounts
202
fabricated on the back of the lower end of ieft fork slider 36 are bolted to
left
mounting bracket 200 to provide additional strength and rigidity to the
attachment
of extension frame 192 to telescoping steering fork 12.
Ski 204 is mounted to a ski pivot bracket 206. A ski pivot axle 208 mounts
in ski pivot bracket 206 and extends through and rotates in the bottom of
extension
frame 192. The resulting pivot allows ski 204 to incline and decline to follow
the
terrain topography while constraining the ski to be steered. A ski biasing
shock
absorber 210 is pivot mounted between extension frame 192 and the rear portion
of
ski pivot bracket 206. A ski wear runner 212 is attached to the bottom center
of
ski 204.
One embodiment of stabilizer 250 is illustrated in Figs. 4, 20-22,and 25-27.
Stabilizer 250 is positioned between the prongs of steering fork 12 mounted
within
extension frame 192. Stabilizer 250 includes a gyroscope 252, an electric
motor
258, an electronic motor controller 262 and a control box 266. Gyroscope 252
is
mounted to a gyro hub 254 (visible in Fig. 22) that rotates on gyro axle 196
and
spins in a rotational direction indicated by the curved arrow shown on the
side of
gyroscope 252 in Figs. 4 and 21. Motor 258 is operatively mounted to gyroscope
252 and to extension frame 192, and applies torque between extension frame 192
and gyroscope 252 to spin the gyroscope in the direction indicated. As viewed
in
Figs. 20 and 25, controller 262 and control box 266 are attached to upper
triple
clamp 30 forward of handlebar 38. A motor wiring cable 260 exits motor 258 and
attaches along the front of extension frame 192 and left fork slider 36 to
guide a
reinforced and stiffened section of motor wiring cable 260 to controller 262.
Stabilizer 250 should be enclosed and protected by, for example and visible in
Figs.
4 and 20, a pair of covers 256 that attaches to extension frame 192.
Mechanical power to spin gyroscope 252 is generated by motor 258
substantially in proportion to the electric power delivered to motor 258.
Controller
262 controls the supply of electric power to motor 258. Controller 262 is
powered
from an electrical generator system that is driven from and integral with
gasoline
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
motor 18. Referring now to Fig. 25, controller 262 represents generally any
commercially available d-c motor controller that is compatible with motor 258
and
with the electrical generator system of snow cycle 10. For example and
illustrated
in Fig. 25, a pulse-width modulation d-c motor controller may be used as
controller
5 262, such as the Eagle Series 12 volt, 40 amp PWM motor controller
manufactured
by 4QD, 30 Reach Road, Burwell, Cambridge shire, CB5, OAH, Great Britain. The
speed control input of controller 262 can be supplied from external speed
control
circuits or devices in different ways. Control box 266 is also available from
4QD for
the Eagle Series PWM controller. Control box 266 connects to controller 262
10 through a control cable 268, and includes a speed set knob 270, an on/off
pushbutton switch 272, and a 3-L.E.D. speed indicator meter 274. As show in
Fig.
25, control box 266 is mounted to upper triple clamp 30 forward of handlebar
38 to
allow the controls to be easily reached by the snow cycle operator.
Fig. 26 is a circuit diagram of an electronic servo input circuit 284 of an
15 optional servo control system for servoing the rotational velocity of
electric motor
258 to the speed of snow cycle 10. This servo control system includes an
electronic tachometer 282 attached to the side of brake caliper 184 (visible
in Fig.
27), servo input circuit 284, and controller 262. Tachometer 282 senses the
rotational velocity of intermediate hub 66 by sensing the rotational velocity
of brake
20 disc 182, and delivers a tachometer signal 288 through a tachometer cable
283 to
servo input circuit 284 enclosed in control box 266. Servo input circuit 284
includes a one-shot 290 and a low pass filter 296. Servo input circuit 284
converts
tachometer signal 288 to a low frequency voltage signal 294 that is
transmitted to
controller 262 through control cable 268. Controller 262 drives motor 258 to a
rotational velocity that is in approximate proportion to the rotational
velocity of
intermediate hub 66. In this embodiment, speed set knob 270 attaches to a gain
potentiometer 286 (shown in Fig. 26) that controls the gain of servo input
circuit
284.
An alternate embodiment of an electric motor driven gyroscopic stabilizer and
steering aid 250 is shown in Figs. 23 and 24. In this embodiment, an electric
motor
258' appears differently than motor 258 as presented in Figs. 4, 21, and 22.
Motor
258 is specially designed to attach integrally to the side of gyroscope 252 in
the
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
21
limited space between the gyroscope and extension frame 192. Alternately,
motor
258' represents a commercially available electric motor that is more prevalent
and
economical than motor 258. Motor 258' is mounted to a motor mounting frame
300 that is attached to the upper rearward portion of extension frame 192.
Motor
258' has electrical supply requirements very similar to those of motor 258,
and can
be supplied by the same controller options described for motor 258 and
illustrated in
Figs. 25-27. The electrical power for motor 258' is supplied by controller 262
through wiring cable 260. Motor 258' is operatively coupled to gyroscope 252
using, for instance, a 1 to 2 drive-ratio pulley and belt system. A driving
pulley 304
having twice the diameter of a driven pulley 306 is mounted to a motor shaft
302 of
electric motor 258'. Driven pulley 306 is attached concentrically to gyro hub
254.
An endless-loop belt 308 wraps driving pulley 304 and driven pulley 306.
Torque
generated by electric motor 258' is coupled to gyroscope 252 through driving
pulley
304, belt 308, and driven pulley 306 to propel the gyroscope to twice the
R.P.M.,
for example, of electric motor 258'.
As an alternative to motor 258, power delivered from the drive train of snow
cycle 10 could be used to spin gyroscope 252. One example of a mechanical
drive
for powering gyroscope 252 from the snow cycle drive train is shown in Figs.
28-
31. As shown in Fig. 30, a primary driving-end bevel gear 310 is
concentrically
attached to intermediate hub 66, and meshes with a secondary driving-end bevel
gear 312 that is attached to and drives a flexible shaft 316. Flexible shaft
316 is
similar in construction to the flexible shaft drives commonly used for
grinding and
shaping power tools that have handheld tool chucks driven through their
flexible
shafts by remote stationary electric motors. A bevel gear bearing and bracket
314
holds bevel gear 312 enmeshed with bevel gear 310. As shown in Fig. 30, for
example, a 1 to 4 step-up drive ratio from bevel gear 310 to bevel gear 312 is
employed to reduce the torque that must be transmitted by flexible shaft 316.
The driven end of the mechanical drive for gyroscope 252 is illustrated in
Figs. 28, 29 and 31. Flexible shaft 316 attaches to and drives a primary
driven-end
bevel gear 318. As shown in Figs. 28 and 29, a bevel gear bearing and bracket
322
holds bevel gear 318 properly meshed with a secondary driven-end bevel gear
320.
A 2 to 1 step-down drive ratio is employed, for example, such that gyroscope
252 is
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
22
driven to rotate substantially at one-half the R.P.M. of flexible shaft 316.
The 1 to 4
step-up drive ratio at the driving end and the 2 to 1 step-down drive ratio at
the
driven end of this mechanical drive results in a 1 to 2 step-up drive ratio
between
intermediate hub 66 and gyroscope 252. Other drive ratios may be deployed as
dictated by component design limits and design optimization of stabilizer 250.
Referring to Figs. 29 and 31, a viscous coupler 324 is concentrically attached
to the left side of gyroscope 252. Viscous coupler 324 is similar in
construction and
operation to the viscous couplers used as automobile radiator fan clutches in
many
late 1970's and early 1980's General Motors Corporation automobiles. Viscous
coupler 324 includes a viscous coupier disc 328, a viscous coupler cover 326,
a
viscous coupler seal 327 and a suitable viscous fluid (not shown). Viscous
coupler
cover 326 attaches to the side of gyroscope 252, compressing viscous coupler
seal
327 and sandwiching viscous coupler disc 328 with the suitable viscous fluid
between the left side of gyroscope 252 and the interior side of the viscous
coupler
cover. Secondary driven-end bevel gear 320 is attached to and drives viscous
coupler disc 328. Gyro hub 254 and viscous coupler disc 328 rotate upon gyro
axle
196. Torque to spin gyroscope 252 is coupled from viscous coupler disc 328
through the suitable viscous fiuid to the left side of gyroscope 252 and the
interior
side of viscous coupler cover 326.
Other mechanical power transmission options exist which could be adapted
for transferring motive power from the snow cycle drive train to gyroscope 252
to
spin the gyroscope, including hydraulic pumps and motors, pneumatic power
transmission systems, belt drives, and other mechanical power transmission
means
too numerous to mention here. Gyroscope 252 could also be powered from a wheel
or track that contacts the snow in proximity to ski 204, and imparts
rotational
power derived from the motion of snow cycle 10 over the snow to the gyroscope,
causing it to spin at a rotational velocity substantially proportional to the
speed of
the snow cycle.
Figs. 32 and 33 illustrate an alternate embodiment for stabilizer 250 that
mounts a gyroscope 252' separate from steering fork 12 and extension frame
192.
In this embodiment, gyroscope 252' spins on a gyro axle 196' that is mounted
within a gyroscope carriage 340. Gyroscope 252' spins in a rotational
direction
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO Ma3Sao PcrnrS99/03869
23
indicated by the curved arrow shown on the side of gyroscope 252' in Fig. 33.
Gyroscope carriage 340 is suspended in a pair of bearings 342 that attach to
main
frame 14. Bearings 342 allow gyroscope carriage 340 to pivot on the axis of
rotation of bearings 342. A connecting rod 344 is made up of a shaft 346 and a
rod
end 348 at each end. The rearward end of connecting rod 344 is attached at one
end to the side of gyroscope carriage 340 off-axis from the axis of rotation
of the
gyroscope carriage. The forward end of connecting rod 344 is attached to lower
triple clamp 30 off-axis from the steering axis of rotation of steering fork
12.
Connecting rod 344 couples steering and stabilization torques between steering
fork
12 and gyroscope carriage 340. Electric motor 258 spins gyroscope 252' and is
powered by electrical current delivered through wiring cable 260' from
controller
262.
SNOW CYCLE OPERATION
In operation and referring to Fig. 1, snow cycle 10 is suspended and
cushioned on ski 204 by telescoping steering fork 12, and on track carriage 86
by
the combination of swing arm 64, shock absorber 68, bell crank 72, connecting
rod
98 and suspension frame 90. The pivot connections of swing arm 64 to main
frame
14 and to the back of track carriage 86 allow track carriage 86 to move up and
down as the swing arm rotates in an arc around swing arm pivot axle 60. The
pivot
connection of track carriage 86 to swing arm 64 allows track carriage 86 to
pivot
vertically relative to the rearward end of swing arm 64. The combined motion
of the
swing arm and the track carriage allows the track carriage to remain level
throughout the full range of track suspension travel and to incline or decline
to
maintain tractional contact with the terrain that snow cycle 10 is traversing
over.
Within practical limits, track carriage 86 is designed to minimize the size
and mass
of track 138 while maximizing the area of tractional contact between track 138
and
the snow. This is accomplished by implementing a substantially fixed path for
track
138 around drive cogwheels 122, guide wheels 126, idler wheels 134, and slide
runners 116 as illustrated in Fig. 6. The diameters of drive cogwheels 122 and
guide wheels 126 are selected to be substantially minimized, but not so small
as to
cause large power losses due to the flexing of track 138 as it moves around
drive
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
24
cogwheels 122 and guide wheels 126. As shown in Figs. 7-10, the central
structural member of track carriage frame 112 is, preferably, fabricated from
thin-
walled aluminum tubing having an elliptical cross-section, or some other
similarly
strong shaped light weight material that provides adequate torsional rigidity
for track
carriage 86 with a high torsional stiffness to weight ratio. This torsional
rigidity
minimizes the twisting of track carriage 86 when one side of track 138 is more
heavily loaded than the other as occurs when the snow cycle is banked in turns
or is
traversing sloped terrain. Minimizing the twisting of track carriage 86 is
desirable to
minimize side-slippage of snow cycle 10, to improve directional stability of
the snow
cycle, and to maintain proper tension in track 138.
It is desirable to have the axis of the pivot connection between track
carriage
86 and swing arm 64 congruent with the axis of rotation of cogwheel axle 88,
and
to have the axis of rotation of intermediate hub 66 congruent with the axis of
the
pivot between swing arm 64 and main frame 14. These congruent axes allow track
carriage 86 and swing arm 64 to move through the full range of suspension
travel
while keeping the length of secondary drive chain 188 relatively constant.
This
eliminates the need for a dynamic chain tensioner for secondary drive chain
188,
and reduces the transient stresses that could load chain 188 due to suspension
movement of the track carriage and swing arm. The congruency of the axes of
rotation with the suspension pivot axes could be approximate, or substantially
congruent, where the center of rotation of cogwheel axle 88 is within, for
example,
100mm of the axis of the pivot connection between track carriage 86 and swing
arm 64. Intermediate hub 66 could be mounted with an axis of rotation
substantially congruent, within 100mm for example, with the pivot axis of the
attachment of swing arm 64 to mainframe 14.
Referring to Fig. 5, shock absorber 68 provides damped spring force between
vehicle main frame 14 and first arm pivot 78 of bell crank 72. This suspension
and
cushioning force is geometrically distributed in predetermined proportion by
bell
crank 72 to the back of track carriage 86 through swing arm 64 and to the
front of
track carriage 86 through connecting rod 98 and suspension frame 90. The force
from shock absorber 68 urges swing arm 64 rotatingly downward around swing arm
pivot 60, thereby urging the back of track carriage 86 downward. The force
from
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/U599/03868
shock absorber 68 simultaneously urges bell crank 72 rotatingly downward
around
bell crank fulcrum pivot 74 on swing arm suspension mount 76, thereby urging
the
front of track carriage 86 downward through connecting rod 98 and suspension
frame 90. The relative proportion of shock absorber cushioning force
distributed to
5 the back and to the front of track carriage 86 is determined by the
dimensions,
geometries and geometrical relationships of the components of the track
carriage
suspension. These dimensions, geometries and geometrical relationships include
the
relative spacing and positioning of swing arm pivot axle 60 and frame
suspension
mount 70 on main frame 14, the location of swing arm suspension mount 76 on
10 swing arm 64, the lengths of and separation angle between the arms of bell
crank
72, the length of connecting rod 98, and the location of pivot connections 96
on
track carriage suspension frame 90. These same geometries and dimensions also
determine the rates at which the suspension forces distributed to the back and
the
front of track carriage 86 increase as gravitational and inertial forces from
the snow
15 cycle and operator increasingly load track carriage 86, compressing shock
absorber
68. To optimize the snow cycte's suspension performance and/or operator
comfort,
different proportions and rates of suspension force distribution to the back
and front
of track carriage 86 can be achieved by altering the geometrical and
dimensional
designs of the components of the track carriage suspension. To a more limited
20 degree, the track carriage suspension characteristics can be modified by
adjusting
the length of connecting rod 98, repositioning connecting rod 98 in bell crank
second arm pivot connections 80 and pivot connections 96 of suspension frame
90,
and/or by adjusting the preload spring compression of shock absorber 68. For
example, a suspension force distribution causing surface pressures between
track
25 138 and the snow at the back of track carriage 86 that are fifty percent
higher than
surface pressures at the front of track carriage 86 could be set up. This
would be
desirable to enable track 138 to progressively compact the snow as track
carriage
86 moves over it, thereby enhancing the traction of track 138 upon the snow.
It is
betieved that such lighter loading of the front of track 138 and snow
compacting
ramp 166 allows the snow compacting ramp and the track to more easily and
quickly plane up onto the surface of soft snow. Other track loading
distributions
and track suspension characteristics may be desired for other operational
suspension
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
26
and traction characteristics, and can be accomplished through modifications to
the
component adjustments and geometrical designs.
It is desirable to minimize the mass of the snow cycle components that are
not cushioned upon the track carriage by the track suspension. Uncushioned
mass
borne by the track carriage is subject to much higher acceleration forces due
to
impacts between track 138 and the terrain obstacles and undulations that the
track
encounters. The higher acceleration forces resulting from additional
uncushioned
mass must be borne by the idler wheels, idler wheel bearings, and slide
runners.
The life and reliability of these components are thus adversely affected. The
track
suspension embodiments of Figs. 1-5 and 16 are desirable since only one shock
absorber is required and the majority of the mass of the shock absorber and
the bell
crank are borne by the snow cycle main frame and the upper portion of the
swing
arm. The mass of these components is cushioned upon the track carriage by the
track suspension.
For the single shock absorber and force-distributing bell crank embodiments
of Fig. 16 and 17, the operation, performance, and adjustability of the
suspension
characteristics are practically identical to those described for the
embodiment of the
single shock absorber and force-distributing bell crank embodiment illustrated
in Figs.
1-5. The embodiment illustrated in Fig. 17 is less desirable since the mass of
shock
absorber 68 and bellcrank 72" is carried by track carriage 86 and the rear of
swing
arm 64, and is practically uncushioned mass.
The two shock absorber track carriage suspension illustrated in Fig. 18
differs
somewhat in operation and performance from the single shock absorber/force-
distributing bell crank/connecting rod embodiments of Figs. 1-5, Fig.16, and
Fig. 17
in that the track carriage does not incline and decline as freely to follow
terrain
undulations. While the track carriage can incline and decline relative to the
longitudinal axis of the snow cycle to maintain tractional contact with the
snow, this
is resisted by the spring and damper of second shock absorber 69. This
embodiment places second shock absorber 69 between track carriage 86 and the
lower-rear portion of swing arm 64, and so the mass of second shock absorber
69 is
practically uncushioned.
The single shock absorber track suspension embodiment shown in Fig. 19 is
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
27
perhaps the simplest of the embodiments herein described. This embodiment
tacks
some of the desirable suspension adjustment features of the track suspension
embodiments shown in Figs. 1-5, Fig. 16, and Fig. 17. To provide a comparable
range of track suspension travel, shock absorber 68' must be substantially
longer
and have a substantially longer stroke than shock absorber 68 of the
embodiments
of Figs. 1-5, Fig. 16, and Fig.17.
Referring to Figs. 2 and 13, as snow cycle 10 moves forward, ramp 166
slides over and compresses the snow ahead of track 138 to a height about equal
to
the front of the lower run of track 138. This prevents the snow from packing
up in
front of track 138, and begins the snow compacting process that is continued
beneath the track. It is expected that this progressive compacting of the snow
will
pack the snowflakes and granules into a more cohesive mass beneath the track,
thereby allowing the traction forces from the track to be more efficiently
distributed
to a greater mass of snow. As facilitated by ramp pivot links 170, ramp
assembly
162 can incline or decline and translate back and forth relative to main frame
14.
The pivot connection of ramp frame 164 to guide wheel axle 130 allows ramp
assembly 162 to incline and decline relative to track carriage 86. This snow
compacting ramp configuration allows track carriage 86 to move through the
entire
range of travel of the track suspension while holding the lower rear of ramp
166 in
desired proximity to the forward end of the lower run of track 138. In this
way, a
snow compacting ramp having an adequately large ramp can be deployed in the
limited space between the tower extremity of main frame 14 and the snow while
allowing the full range of suspension motion of track carriage 86.
Fig. 47 illustrates the full ranges of vertical motion of the track carriage
suspension and the front ski suspension of snow cycle 10. Fig. 47 is a side
view of
the snow cycle of Fig. 1 with shock absorber 68 and telescoping steering fork
12
maximally loaded and compressed as would occur in high G-force loading of the
snow cycle track suspension and telescoping steering fork. The unloaded
suspension positions of track carriage 86, swing arm 64, snow compacting ramp
assembly 162, ski 204, extension frame 192 and other associated components are
illustrated using phantom lines.
Referring now to Fig. 12, track 138 is fabricated with traction paddles 142
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT1US99/03868
28
that have blunt paddle tips 144 with laterally-convex profiles and stiff
traction
paddle blocks 146 with side surfaces 145. Paddle webs 148 extend between
selected traction paddle blocks to form propulsion and braking snow traction
surfaces. Blocks 146 strengthen the paddles and help prevent them from flexing
excessively during extreme snow cycle acceleration and braking, thereby
helping to
maintain traction. Side surfaces 145 of blocks 146 dig in and press laterally
against
the snow to minimize side-slippage when the snow cycle is leaned in cornering
or is
traversing steep slopes. Reduced-height web sections 149 are deployed between
selected blocks of traction paddles 142a and 142b. The openings created by
these
reduced height web sections increase the exposed area of side surfaces 145 of
blocks 146 adjacent to reduced height web sections 149. This is intended to
improve the track's resistance to side-slippage.
Blunt paddle tips 144 of traction paddles 142 cannot penetrate the surface of
ice or very hard packed snow, and blunt paddle tips 144 bear the weight of the
snow cycle on such hard surfaces. Fig. 43 illustrates this in a vertical
sectional view
of track carriage 86 and track 138 with snow cycle 10 banked on an ice surface
650. Various portions of the blunt paddle tips 144 contact the ice as the
operator
leans snow cycle 10 to differing angles. The convex curvature of blunt paddle
tips
144 allows the operator to lean snow cycle 10 smoothly from side to side on
hard
surfaces such as ice or hard packed snow to keep snow cycle 10 in balance
during
turning of the snow cycle. The curved lateral profile of a motorcycle tire
allows the
motorcycle to be smoothly leaned from side to side in turning in much the same
way. When snow cycle 10 is leaned more than about 14 degrees, for example and
illustrated in Fig. 43, ice runners 160 cut and dig into the ice or hardpack
snow
surface. This helps inhibit side slipping of the snow cycle upon such a
slippery
surface.
Fig. 44 is a vertical sectional view of track carriage 86 and track 138 with
snow cycle 10 banked on a soft powder snowbase 652. In soft or powder snow,
the entire width and length of track 138 penetrate the snow surface and
compress
the soft snow. In soft snow, the majority of the weight borne by track 138 is
distributed across the flat portions of track belt 140 between traction
paddles 142.
Even though track belt 140 is flat, it is expected the compressibility of soft
snow
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/[JS99/03868
29
will allow snow cycle 10 to be easily leaned and banked.
Fig. 45 shows a vertical sectional view of track carriage 86 and track 138
with snow cycle 10 banked on a densely-packed snowbase 654. Traction paddles
142 penetrate the surface of densely-packed snow and compress the snow under
blunt paddle tips 144 only to the depth where the compressed snow beneath the
blunt paddle tips supports the weight of snow cycle 10 and the operator. As
shown
in Fig. 12, traction paddles 142 have more of blocks 146 near the center of
track
138 than at the edges of track 138. Additionally, the paddle blocks near the
center
of track 138 have larger tip areas than those near the edges of track 138.
Because
of this, the paddle blocks near the center of track 138 penetrate and compress
densely-packed snow to a lesser depth than do the sparser and smaller blocks
nearer
the edges of track 138. These features enable the operator to more easily lean
and
balance snow cycle 10 in moderately dense snow conditions.
Refer now to Fig. 46 that illustrates a vertical sectional view of track
carriage
86 and track 138 with snow cycle 10 banked upon a moderately packed snowbase
656. A multitude of track belt openings 155 (visible in Fig. 12) between slide
bearing clips 154 allow the end portions of traction paddles 142 adjacent
track belt
openings 155 and slide bearing clips 154 to penetrate the snow to the extent
that
slide bearing clips 154 on the low side of track 138 are below the surface of
the
snow. The rearward and forward sides of slide bearing clips 154 function as
additional snow traction surfaces in moderately packed and soft snow
conditions.
Track belt openings 155 also allow snow flakes and ice granules to be
introduced
between slide bearing clips 154 and slide runners 116 as a lubricant between
the
bearing surfaces of the slide bearing clips and the slide runners.
As illustrated in Figs. 43, 45 and 46, ice runners 160 cut into ice, hard
packed snow and moderately dense snow to help minimize side slippage of the
snow
cycle during extreme banking.
Referring generally to Figs. 20-33, gyroscopic stabilizer and steering aid 250
is mounted so as to orient gyroscope 252 to spin in a nominally upright plane
aligned substantially with the vertical axis of snow cycie 10 and with the
steered
direction of ski 204. Gyro axle 196 is mounted or coupled to steering fork 12.
The
Gyroscope can also be mounted in a rotatable gyroscope carriage as
illustrated, for
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
example, in Figs. 32-33. This separate mounting of the gyroscope requires that
steering torque be coupled between the gyroscope carriage and the steering
fork
using, for example, connecting rod 344. The gyroscopic stabilizing effect
produced
by stabilizer 250 occurs when snow cycle 10 is moving forward and becomes
tipped
5 sideways out of balance. This sideways tipping of snow cycle 10 also tips
gyroscope 252 sideways, and causes the gyroscope to generate a gyroscopic
response torque that is perpendicular to the lengthwise axis of snow cycle 10
around which the snow cycle is tipping. This response torque is transferred
through
gyro axle 196 and is coupled to steering fork 12 and to ski 204. The gyroscope
10 response torque is substantially proportional to the rotational moment of
inertia of
gyroscope 252, the rotational velocity (RPM) of gyroscope 252, and the angular
velocity with which snow cycle 10 is tipping out of balance. The gyroscope
response torque coupled to steering fork 12 and ski 240 urges the steering
fork and
ski to turn on the steering axis of steering fork 12 toward the direction that
snow
15 cycle 10 is tipping. The forward motion of snow cycle 10 then causes the
ski to
steer back under the center of gravity of snow cycle 10, tending to bring snow
cycle
10 again upright and in balance. This re-balancing response generated by
gyroscope
252 and coupled to ski 204 is instantaneous and independent of operator
response,
making snow cycle 10 easier to balance.
20 The steering aid benefit of stabilizer 250 results from this same
gyroscopic
response force by enabling the snow cycle operator to steer snow cycle 10 by
intentionally tipping or leaning snow cycle 10 out of balance. This is
accomplished
by the operator placing more of his or her weight on footrest 28a or 28b that
is on
the side of the desired direction of the turn, or by pressing the operators
lower torso
25 sideways against snow cycle 10 in the direction of the desired turn. The
resulting
gyroscopic force from gyroscope 252 forces ski 204 to turn in the intended
direction
without the operator applying steering force to handlebar 38. These steering
dynamics are an inherent aspect of motorcycle and bicycle operation. It is
desirable
to emulate these balance and steering dynamics in snow cycle 10 to make its
30 operation seem natural and intuitive to an experienced motorcycle or
bicycle rider.
Gyroscope 252 is propelled to a rotational velocity in approximate
predetermined proportion to the speed of snow cycle 10 or to another
predetermined
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
31
rotational velocity to provide desired gyroscopic vehicle steering control and
balancing characteristics.
One gyroscope constant-speed option using an electric motor and controller
to spin the gyroscope is shown in Fig. 25. The rotational speed of motor 258
is
controlled to a set speed that is proportional to the setting position of
speed set
knob 270. Speed set knob 270 turns a potentiometer (not visible) enclosed in
control box 266. The potentiometer supplies a d-c signal voltage that is
proportional
to the setting of speed set knob 270 through control cable 268 to controller
262.
Controller 262 generates a pulse width modulated voltage having an on/off duty
cycle that is in substantial proportion to the setting of speed set knob 270,
and
transmits the pulse-width modulated voltage through wiring cable 260 to
electric
motor 258. Motor 258 is thereby powered to spin at a rotational velocity that
is
substantially proportional to the setting of speed set knob 270.
An electric motor speed control option that controls the gyroscope's
rotational speed to be substantially proportional to the speed of snow cycle
10 is
additionally illustrated in Figs. 26 and 27. The control system includes
electronic
tachometer 282, servo input circuit 284 enclosed in control box 266, and
controller
262. Electronic tachometer 282 is mounted to brake caliper 184 adjacent to
brake
disk 182 and senses the rotational speed of intermediate hub 66 by detecting
the
slotted holes dispersed radially on brake disc 182, thereby sensing the speed
of the
drive train of snow cycle 10. Electronic tachometer 282 supplies tachometer
signal
288 to servo input circuit 284. Tachometer signal 288 has a pulse frequency
proportional to the rotational speed of intermediate hub 66. Servo input
circuit 284,
represented by the circuit block diagram of Fig. 26, is housed in control box
266,
and converts tachometer signal 288 to low frequency voltage signal 294. A one-
shot 290 in servo input circuit 284 converts tachometer signal 288 into a
pulse train
292. Pulse train 292 consists of electrical pulses of the same frequency as
tachometer signal 288, but having pulse-widths that are determined by the
adjustment of gain potentiometer 286. A low-pass filter 296 converts pulse
train
292 to low frequency voltage signal 294. Voltage signal 294 has a varying
voltage
that is in substantial proportion to the rotational speed of intermediate hub
66, and
ranges from approximately 0.5 volts when intermediate hub 66 is not spinning
to
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43340 PCT/US99/03868
32
about 4 volts when intermediate hub 66 is rotating at the maximum desired
speed.
Voltage signal 294 is transmitted through control cable 268 to controller 262.
Controller 262 supplies motor 258 with a pulse-width modulated voltage having
an
on/off duty cycle substantially proportional to the voltage of voltage signal
294.
Motor 258 causes gyroscope 252 to accelerate and spin at a rotational speed
that is
substantially in proportion to the on/off duty cycle of the pulse width
modulation
voltage supplied to electric motor 258. Gyroscope 252 is thereby driven by
motor
258 to a rotational velocity that is substantially proportional to the speed
of snow
cycle 10.
Programmable servo control circuits could be used to more optimally control
the rotational velocity of gyroscope 252. Such a control circuit might include
tachometer sensors that sense both the snow cycle drive train speed and the
rotational velocity of gyroscope 252. A microprocessor controller could be
implemented and programmed to monitor both the speed of the gyroscope and the
speed of the drive train, and use the present and historical values of these
speeds to
generate optimal pulse width modulated control voltages and currents for
electric
motor 258.
An alternate mounting for stabilizer 250 is illustrated in Figs. 32 and 33
where gyroscope 252' is suspended within main frame 14 in a protected
location.
Mounting the gyroscope to main frame 14 rather than to extension frame 192
isolates the gyroscope from the impacts and abuse that a gyroscope mounted to
extension frame 192 would receive. Gyroscope 252', shown in Figs. 32-33, can
be
smaller and spin at a higher speed than the embodiment of gyroscope 252 shown
in
Figs. 21-24, 28, and 29 because of the protection from impact and the
isolation
from physical shock and vibration that the main frame mounting location
affords.
The mechanical drive option for gyroscope 252 shown in Figs. 28-31 spins
gyroscope 252 at a rotational velocity that is substantially proportional to
the speed
of snow cycle 10. Nominally, the ratio of the gyroscope rotational velocity to
the
speed of intermediate hub 66 is fixed, being determined by the gear ratio of
bevel
gears 310 and 312 and the gear ratio of bevel gears 318 and 320. Intermediate
hub
66 can be accelerated very quickly by gasoline motor 18 and can be decelerated
and
stopped almost instantaneously by disc brake 181. Because of this, it is
desirable
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
33
that some sort of torque-limiting device be inserted in the flexible shaft
drive train
between intermediate hub 66 and gyroscope 252 to limit the torque which
flexible
shaft 316 is required to transmit. Absent such a torque-limiting device,
flexible
shaft 316 could be subject to torque levels well beyond the practical design
limits of
the flexible shaft. Such a torque-limiting device could be, for example,
viscous
coupler 324 illustrated in Figs. 28, 29 and 31. The viscous fluid that couples
torque
between viscous coupler disc 328 and gyroscope 252 allows the viscous coupler
disc to slip relative to gyroscope 252 with the amount of slippage somewhat
proportional to the torque being coupled. Viscous coupler 324 limits the
torque that
flexible shaft 316 transmits, but may also limit the acceleration and
deceleration of
gyroscope 252 as snow cycle 10 is accelerated and braked. It is anticipated
that
such slower acceleration and deceleration of gyroscope 252 would be almost
imperceptible to the snow cycle operator, and would be functionally
acceptable.
Referring again to Fig. 20, the rear of ski 204 is urged downward around ski
pivot axle 208 by ski biasing shock absorber 210, thereby forcing the forward
tip of
the ski upward, allowing it to more easily plane up onto the surface of the
snow.
The force from shock absorber 210 also causes ski 204 to incline upward when
snow cycle 10 becomes airborne to prevent the tip of ski 204 from burrowing
into
the snow upon landing. The damping provided by shock absorber 210 helps
prevent
ski 204 from oscillating around ski pivot axle 208 when the ski is airborne
and helps
reduce undesirable vibrations and oscillations of ski 204 when it is
traversing choppy
or uneven snow surfaces. Ski wear runner 212 attached to the bottom center of
ski
204 enhances the directional stability of ski 204 and protects it from
abrasion.
SNOW BICYCLE STRUCTURE
Figs. 34-36 illustrate from the side, front, and rear, respectively, a human-
powered bicycle-type snow vehicle designated generally by the reference number
410. Snow vehicle 410 is referred to as snow bicycle 410 to differentiate it
from
motor-powered snow cycle 10. While snow bicycle 410 appears quite different
from snow cycle 10, most of the components of snow bicycle 410 that are
germane
to the present invention are similar in appearance and have the same purpose
and
function as the corresponding components of snow cycle 10. To avoid redundancy
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
34
of definition, and to enhance the comparisons of snow bicycle 410 to snow
cycle
10, the same reference numbers are used for like components of the snow cycle
and
snow bicycle embodiments. Where component structure and appearance are
significantly different, different reference numbers are used. If the function
of a
differently-appearing component of snow bicycle 410 is the same as the
function of
the corresponding component of snow cycle 10, the reference number is exactly
400 greater for the component in the snow bicycle embodiment.
Snow bicycle 410 may include many of the parts and much of the structure
of a typical full-suspension mountain bicycle. Referring also now to Fig. 37,
snow
bicycle 410 includes a main frame 414 with a steering head tube 415, a saddle
416,
a seatpost 417, a pedal crank 418 mounted upon a crank axle 419, a handlebar
438, and a handlebar stem 437. Crank axle 419 rotates within a bottom bracket
465 of a swing arm frame 464. Also included is a bicycle drive train 423 that
comprises a primary drive chain 424, a set of chainring sprockets 420 mounted
to
pedal crank 418, a front chain derailleur 425, a front derailleur shifter 446,
a cogset
426, a rear derailleur 427, and a rear derailleur shifter 447. Derailleur
shifters 446
and 447 are mounted to handlebar 438 and are visible in Figs. 35 and 36. All
of
these components are of the general type and construction used in many
mountain
bicycles of current manufacture, and perform the same functions as they do in
mountain bicycles. Because of this, the structure and operation of these
components will not be further described.
In comparing the structure of snow bicycle 410 to that of snow cycle 10, the
snow bicycle illustrations of Figs. 34-38 are comparable with the snow cycle
illustrations of Figs. 1-5, respectively.
Swing arm frame 464 of snow bicycle 410 is different in structure but very
similar in function to swing arm 64 of snow cycle 10. Swing arm frame 464 is
attached to snow bicycle main frame 414 at a swing arm pivot 460. Track
carriage
86 is basically the same in structure and function as track carriage 86 of
snow cycle
10 illustrated in Figs. 6-11, differing only in size and in some instances,
width to
height aspect ratio. Left and right track carriage pivot brackets 482 are
slightly
different in shape than track carriage pivot brackets 82 of snow cycle10, but
are
identical in function. Figs. 6-1 1 and the accompanying description of track
carriage
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCTIUS99/03868
86 already presented for snow cycle 10 apply also to the snow bicycle
embodiment
of track carriage 86. Referring now also to Fig. 38, track carriage pivot
brackets
482 attach to swing arm frame 464 and to left and right swing arm braces 506.
Cogwheel axle 88 rotates in bearings 84 mounted in pivot brackets 482 and
serves
5 as a hinge joint between track carriage 86 and swing arm frame 464. Swing
arm
frame 464 pivots vertically around swing arm pivot 460 on main frame 414, and
track carriage 86 pivots vertically around the connection of cogwheel axle 88
to
pivot brackets 482. The resulting scissors-type swing arm structure and pivot
connections allow track carriage 86 to move vertically under swing arm frame
464
10 white maintaining a level orientation, inclining, or declining as needed to
keep track
138 in tractional contact with the terrain below snow bicycle 410.
The track carriage suspension for snow bicycle 410 illustrated in Fig. 38 has
the same in basic structure and function as the track carriage suspension of
snow
cycle 10 illustrated in Fig. 5. The descriptions of structure and operation
presented
15 for that track carriage suspension also apply conceptually to the track
carriage
suspension of snow bicycle 410. A shock absorber 468 is pivotally mounted
between a frame suspension mount 470 on main frame 414 and a bell crank first
arm pivot 478 of a bell crank 472. Bell crank 472 transmits and apportions
suspension force from shock absorber 468 through a bell crank fulcrum pivot
474 to
20 a swing arm frame suspension mount 476. The apportioned force urges swing
arm
frame 464 downward around swingarm pivot 460, forcing the rear portion of
track
carriage 86 downward. The suspension force from shock absorber 468 also urges
bell crank 472 in a clockwise direction (as viewed in Fig. 38) around bell
crank
fulcrum pivot 474, thereby apportioning and transmitting suspension force
through
25 connecting rod 98 to a top bracket 94 mounted to a ramp frame 564 of a snow
ramp assembly 562. Ramp frame 564 is attached to track carriage frame 112, and
transmits the apportioned suspension force to the front of track carriage 86,
urging
it downward around the pivot connection on cogwheel axle 88 between pivot
brackets 482 and track carriage 86. The suspension force of shock absorber 468
is
30 thus apportioned and distributed to both the rearward and forward ends of
track
carriage 86 in a predetermined proportion to affect a predetermined ioading
distribution along the ground-contacting run of track 138. Like snow cycle 10,
the
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
36
length adjustment of connecting rod 98 and alternate pivot mounting locations
for
connecting rod 98 in a set of bell crank pivot connections 480 and in pivot
connections 96 of top bracket 94 allow for limited adjustment of the front-to-
rear
loading distribution of track 138. Alternate track suspension embodiments
already
described and illustrated for snow cycle 10, including the four track
suspension
embodiments illustrated in Figs. 16-19, are also, with appropriate
modification,
alternate embodiments of a track suspension for snow bicycle 410.
Referring to Figs. 37-39, an intermediate hub 466 of snow cycle 410 appears
somewhat different from intermediate hub 66 of snow cycle 10 in Figs. 14 and
15,
even though the basic structure and function are very similar. Intermediate
hub 466
mounts and rotates on an intermediate hub axle 467 that attaches to the top
center
portion of swing arm frame 464. Bicycle drive train 423 couples pedal crank
418 to
intermediate hub 466 just like a drive train of a common multi-speed bicycle
couples
the bicycle pedal crank to the rear wheel hub. Primary drive chain 424 of
bicycle
drive train 423 is routed through a chain hanger 429 that is attached to the
underside of swing arm frame 464. A bearing-suspended chain idler wheel 429'
is
mounted within chain hanger 429, and allows primary drive chain 424 to
circulate
through the chain hanger with minimal friction.
A disc brake 581 includes brake disc 182 and brake caliper 584, and is best
viewed in Figs. 37 and 39. Brake caliper 584 straddles brake disc 182 and
mounts
to swing arm frame 464. Brake caliper 584 forces brake pads against the sides
of
brake disc 182 when the operator actuates a brake lever 448 that is mounted to
handlebar 438 (visible in Figs. 35 and 36). Referring also now to Fig. 41,
brake disc
182 attaches concentrically to the mid-portion of intermediate hub 466 and a
secondary intermediate sprocket 580 attaches concentrically to the left side
of
intermediate hub 466. A secondary drive chain 588 wraps secondary intermediate
sprocket 580 and cogwheel axle sprocket 120 in an endless loop and transmits
drive
power and braking torque from intermediate hub 466 to cogwheel axle 88.
Primary
driving-end bevel gear 310 is concentrically attached to intermediate hub 466
adjacent to brake disc 182.
Snow compacting ramp assembly 562, best viewed in Figs. 37 and 38,
comprises ramp frame 564, a snow compacting ramp 566 secured to the bottom of
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
37
ramp frame 564, and a snow cover 568 enclosing the top of ramp frame 564. The
side members of ramp frame 564 extend around the forward end of track 138 and
attach to the forward sides of track carriage frame 112. Ramp frame 564 holds
ramp 566 in a fixed attitude relative to track carriage 86 with the lower
rearward
end of ramp 566 at approximately the same height as the front of the lower run
of
track 138. Top bracket 94 bridges over the top of track 138 and track shield
156,
attaching to the tops of the rearward side members of ramp frame 564.
Referring now to Figs. 35-37, the front steering and suspension components
of snow bicycle 410 are practically identical in structure and function to
those of
snow cycle 10. A telescoping steering fork 412 comprising upper and lower
triple
clamps 430, a head pipe 432 (visible in Fig. 35 only), a pair of fork tubes
434, and a
pair of fork sliders 436 has substantially the same external structure and
function as
telescoping steering fork 12 of snow cycle 10. The internal mechanism
construction
of snow bicycle telescoping steering fork 412 may differ from the internal
mechanism construction of snow cycle telescoping steering fork 12. The
illustrations of Figs. 34-37 show steering fork 412 with a pair of optional
accordian-
stye protector boots 435 enclosing the midsections of fork tubes 434. The
combined structure of steering extension frame 192, ski 204 and ski pivot
bracket
206 has basically the same structure and function for snow bicycle 410 as the
combined structure comprising these components for snow cycle 10 illustrated
in
Figs. 1-4. In snow bicycle 410, an elastomeric spring 610 connects between
extension frame 192 and the forward portion of ski pivot bracket 206.
Elastomeric
spring 610 lifts the front of ski 204, just as shock absorber 210 does in snow
cycle
10. Elastromeric spring 610 is formed using rubber or other durable elastomer
compound.
Gyroscopic stabilizer and steering aid 250 of snow bicycle 410 includes a
mechanical drive transmission that is illustrated in Figs. 39-42, and is very
similar to
the mechanical-drive gyroscope embodiment of snow cycle 10 shown in Figs. 28-
31. The description given for the structure and operation of the mechanical
drive for
gyroscope 252 of snow cycle 10 and illustrated in Figs. 28-31 applies
generally to
the mechanical drive for gyroscope 252 of snow bicycle 410. Motive power for
gyroscope 252 is delivered from intermediate hub 466 through a rotary power
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PC'f/US99/03868
38
transmission that includes primary driving-end bevel gear 310, secondary
driving-end
bevel gear 312, flexible shaft 316, primary driven-end bevel gear 318,
secondary
driven-end bevel gear 320, a ratcheting freewheel 330, and a viscous coupler
324'.
Referring to Fig. 41, bevel gear 310 attaches concentrically to intermediate
hub
466. Bevel gear 312 is held enmeshed with bevel gear 310 by bearing and
bracket
314 that attaches to swing arm frame 464. Referring also now to Figs. 34, 37
and
40, flexible shaft 316 attaches at one end to bevel gear 312, and attaches at
the
other end to bevel gear 318. As shown in Fig. 40, bevel gear 318 meshes with
bevel gear 320. Referring also to the exploded view of Fig. 42, Gyroscope 252
mounts to gyro hub 254 that rotates upon a gyro axle 196' using gyroscope
bearings 253. Bevel gear 320 attaches concentrically to a freewheel pawl
assembly
330a of ratcheting freewheel 330. Viscous coupler 324' includes a viscous
coupler
disc 328', a viscous coupler cover 326, a viscous coupler seal 327 and a
suitable
viscous fluid (not shown). A toothed freewheel hub 330b of ratcheting
freewheel
330 is concentrically attached to viscous coupler disc 328'. Viscous coupler
cover
326 attaches to the side of gyroscope 252, compressing viscous coupler seal
327
and sandwiching viscous coupler disc 328' with the suitable viscous fluid
between
the side of gyroscope 252 and the interior side of the viscous coupler cover.
Freewheel pawl assembly 330a rotates upon gyro axle 196' and fits
concentrically
within toothed freewheel hub 330b so that the ratchet pawls of freewheel pawl
assembly 330a engage the ratchet teeth of toothed freewheel hub 330b. Pawl
assembly 330a transmits torque from bevel gear 320 to toothed freewheel hub
330b only in the rotational direction indicated by the curved arrow shown
adjacent
to hub 330b in Fig. 42.
Just as for snow cycle 10, other mechanical power transmission options for
transmitting motive power from the drive train of snow bicycle 410 to
gyroscope
252 exist and could be used for spinning gyroscope 252 of snow bicycle 410.
Gyroscope drive mechanisms that extract motive power from the forward
momentum of snow bicycle 410 could also be used to spin gyroscope 252.
SNOW BICYCLE OPERATION
In operation, referring to Figs.34-38 and comparing to the corresponding Figs.
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
39
1-5 for snow cycle 10, snow bicycle 410 is very similar in operation to snow
cycle
10. The obvious major difference is that snow bicycle 410 is human-powered,
and
snow cycle 10 is powered by a gasoline motor. Otherwise, the operationai
description for snow cycle 10 generally applies to snow bicycle 410.
Snow bicycle 410 includes a track suspension that is very similar to the track
suspension of snow cycle 10 illustrated in Figs. 1-5, and features similar
structure,
functionality, performance characteristics, and adjustability - albeit scaled
to the
size, weight, and performance requirements of a snow bicycle. Track carriage
86
and track 138 in the embodiment of snow bicycle 410 are identical in structure
and
function to track carriage 86 and track 138 of snow cycle 10, but are scaled
in size
and weight as suitable for a human-powered snow bicycle application. Traction
paddles 142 of track 138 are proportionately smaller to be suitable to the
requirements for snow bicycle use.
Snow compacting ramp assembly 562 of snow bicycle 410 is simpler in
structure, lighter, and less costly than articulating snow compacting ramp
assembly
162 of snow cycle 10. A non-articulating ramp is used since the vertical
suspension
travel of track carriage 86 below swing arm frame 464 and main frame 414 of
snow
bicycle 410 is substantially less than the vertical suspension travel of track
carriage
86 below swing arm 64 and main frame 14 of snow cycle 10. It is believed that
a
smaller and shorter snow compacting ramp is adequate for snow bicycle use.
Snow
compacting ramp assembly 562 is rigidly attached to track carriage frame 112,
and
thus moves vertically, inclines, and declines with the suspension movement of
track
carriage 86. Ramp 566 slides over and compresses the snow ahead of track 138
to
a height about equal to the front of the lower run of track 138, preventing
snow
from packing up in front of track 138.
The bicycle drive train 423 shown in Figs. 37-39 has the same structure and
operation that drive trains of most mountain bicycles of present manufacture
have.
A wide range of gearing ratios offered by bicycle drive train 423 enables the
snow
bicycle operator to select a gearing ratio suited to the incline of the
terrain and the
effort the operator wishes to expend in pedaling the snow bicycle. Chain
hanger
429 is deployed to allow the full suspension articulation of track carriage 86
below
swing arm frame 464 without interference between primary drive chain 424 and
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
track shield 156. Chain hanger 429 also helps to maintain correct tension in
primary
drive chain 424 under the jarring that occurs when the snow bicycle traverses
rough
terrain. Snow bicycle 410 has only one snow traction device, namely track 138,
and requires only one brake and brake actuator. A disc brake such as disc
brake
5 581 is desirable to provide strong, reliable braking in snowy, icy and wet
conditions.
Steering extension frame 192, ski 204, and ski pivot bracket 206 of snow
bicycle 410 are practically identical in structure and operation to steering
extension
frame 192, ski 204, and ski pivot bracket 206 of snow cycle 10. The size,
weight,
and strength of these components is reduced in the snow bicycle embodiment as
is
10 acceptable and desirable for a relatively lightweight human-powered
vehicle. In
snow bicycle 410, elastomeric spring 610 (visible in Figs. 34 and 37) is used
to urge
the front of ski 204 upward, allowing it to more easily plane up onto the
surface of
the snow. The contraction force of elastomeric spring 610 also causes ski 204
to
incline when snow bicycle 410 becomes airborne to help prevent the ski tip
from
15 burrowing into the snow upon landing.
In the snow bicycle embodiment of stabilizer 250 illustrated in Figs. 39-42,
the stabilizer is driven from the snow bicycle drive train. Gyroscope 252 is
driven to
spin at an RPM, for example, that is nominally twice the RPM of intermediate
hub
466. Referring to Fig. 42, freewheel 330 comprising pawl assembly 330a and
20 toothed freewheel 330b is inserted between bevel gear 320 and viscous
coupler
324'. Freewheel 330 transmits motive torque to gyroscope 252 only in one
rotational direction to accelerate or maintain the rotational velocity of
gyroscope
252. When the operator stops pedaling or brakes snow bicycle 410, freewheel
330
allows gyroscope 252 to spin freely and maintain rotational momentum, helping
to
25 preserve the energy expended in accelerating the gyroscope. It is
particularly
important in a human-powered snow bicycle to optimize the energy efficiency of
stabilizer 250 to help minimize the effort expended by the human operator in
powering both snow bicycle 410 and stabilizer 250. Stabilizer 250 of snow
bicycle
410 is smaller and lighter than stabilizer 250 of snow cycle 10 as is adequate
and
30 appropriate for snow bicycle use.
The main frames for the snow vehicles described are made of welded metal
tubing or some other structurally stable, preferably lightweight, material.
Other
CA 02555039 1999-02-23
CA 02321860 2000-08-23
WO 99/43540 PCT/US99/03868
41
structural components such as the swing arm, swing arm frame, track carriage
frame and the snow compacting ramp frame are made of any suitable structurally
stable material and cross section. Further, although only the principal
bearings are
specifically shown on the drawings and described above, it is desirable to use
bearings, bushings and the like on all pivot connections and rotating hubs to
reduce
wear and facilitate the relative movement of the parts. It is expected that
the ski
will be manufactured from an ultra-high molecular weight plastic or other
suitable
structural material offering low friction with the snow, adequate durability,
and good
resistance to abrasion and wear.
INDUSTRIAL APPLICABILITY
The snow cycle and the snow bicycle embodiments herein described can be
manufactured with existing manufacturing technologies and processes using
presently available materials and components. The snow cycle and snow bicycle
could each be manufactured and sold as complete vehicles, or as kits for
converting
commercially available off-road motorcycles or mountain bicycles to over-snow
vehicles. Such a conversion kit would comprise the track carriage, track,
swing
arm, bell crank and connecting rod, intermediate hub, brake, drive chains,
snow
compacting ramp assembly, ski, fork extension frame, optional gyroscope, and
additional mounting frames or brackets required to mount the swing arm and
snow
compacting ramp to the specific motorcycle or mountain bicycle main frame, and
the
fork extension frame to the fork of the motorcycle or mountain bicycle. Thus,
the
motorcycle or mountain bicycle could be seasonably configured for over-snow
use or
for conventional wheeled use as desired.
Although the invention has been shown and described with reference to the
foregoing embodiments, alternative embodiments may be made without departing
from the spirit and scope of the invention as defined in following claims.
