Note: Descriptions are shown in the official language in which they were submitted.
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CROSS-REFERENCE TO RELATED APPLICATIONS
This application claims foreign priority under 35 U.S.C. 1 19 to Czech
Republic
(CZ) Application No. PUV 2005-16347 filed 03/02/2005, and Czech Republic (CZ)
Application No. PUV 2005-16348 filed 03/02/2005, both of which are
incorporated
by reference in their entirety.
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BACKGROUND
The present invention relates generally to relatively small implement machines
and
more particularly to machines used to remove snow from e.g. sidewalks,
driveways,
and/or from other surfaces which a user desires to clear of snow. Such
machines are
frequently referred to by names such as snow blowers, snow throwers, and
others.
Some snow blowers are user propelled, or non-self propelled. Such snow blowers
advance and/or regress under the power of the user, whereby the user pushes,
pulls, or
otherwise manipulates the device as desired.
By contrast, some snow blowers are self propelled devices, whereby the device
advances and/or regresses at least partially under its own power. These self
propelled
snow blowers can be relatively easier to use, as compared to non-self
propelled snow
blowers. As one example, a user can devote relatively less energy to advancing
the snow
blower forward, and can concentrate more energy toward e.g. steering the
device,
laterally controlling, and/or otherwise controlling, the device.
Typical self propelled snow blowers have an engine, a pair of drive wheels, an
auger, and a discharge chute. The engine provides power to all power requiring
components of the snow blower, namely the drive wheels and the auger.
A typical method to transmit power from the engine to the drive wheels is by
way of
a friction drive, solid axle, and sleeved or other wheel hubs. The friction
drive includes a
drive disc or platter which is rotatably driven by the power produced by the
engine. When
the friction drive is engaged, an outwardly facing surface of the drive disc
or platter
frictionally engages the outer circumferential surface of a wheel or other
circumferentially-
defined surface which is fixedly mounted to the solid axle.
The user engages the friction drive by way of a belt tensioning mechanism
which
includes one or more belts. Such belts are prone to slippage, breakage, and/or
other
failure over time. The belt tensioning mechanism is actuated by depressing a
drive-lever
located on a handlebar.
Depressing the drive-lever can require substantial force. Plus, to keep the
friction
drive engaged, the user must continuously hold the drive-lever in the
depressed,
engaged, position, against a substantial retractive force, whereby the use of
such friction
drive can prove tiresome for the user.
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Still referring to known technology, one of the drive wheels is fixedly
attached to
the solid axle. The other wheel rotates freely with respect to the solid axle,
e.g. is a free
wheel assembly. Specifically, the free wheel assembly includes a cylindrical
hub-sleeve
portion which extends axially outwardly from a central portion thereof. The
inside
diameter of the free wheel hub-sleeve is larger than the outside diameter of
the solid axle,
enabling the hub-sleeve to slide concentrically over the end of the solid
axle.
As desired, the hub-sleeve of the free wheel is rotatably connected to the
solid axle
by way of, for example, an engaging pin, inserted through bores which extend
radially
through the hub-sleeve and the solid axle. Accordingly, to disengage a wheel
from its
rotatable connection with the axle, a user removes the respective engagement
pin from
the assemblage of the axle and wheel. Then, to reengage the wheel into a
rotatable
connection with the axle, the user aligns the holes in the axle and sleeve,
and reinserts
the engagement pin.
However, removing and/or reinserting the engagement pin can prove relatively
difficult, at least in certain circumstances and/or environmental conditions.
As one
example, the corresponding bores of the wheel hub sleeve and the solid axle
must be in
suitable alignment, both radially and axially, to enable a user to insert an
engagement pin
therethrough. This task can be further complicated by certain factors such as
limited
lighting conditions, snow and/or ice which can accumulate in the bores, poor
user
dexterity if the user wears mittens or gloves, or under cold ambient
temperature exposure
to bare skin if the user does not wear mittens or gloves, or others.
A typical auger mechanism is driven by a worm and gear, e.g. worm gear type,
drive which interfaces the auger at a medial portion thereof. Specifically, in
many two-
stage auger mechanisms, in which the auger defines a first stage and an
impeller defines
a second stage, a shaft is driven by power from the engine and extends axially
through
the center of an impeller. This shaft rotates the impeller and extends axially
outwardly
beyond the impeller.
The end of this shaft includes a worm gear which is adapted and configured to
rotatably drive a corresponding gear that is keyed, or otherwise fixedly
connected to, a
medial portion of the auger. Thus, when the impeller rotates, so does the
auger.
However, worm gear drive configurations, which interface with the medial
portion of
the a uger, d efine a p ortion o f t he a uger w hich is not occupied by the
auger blade.
Namely, the worm gear drive is generally encapsulated by a housing structure.
The
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housing is typically located in the middle-most portion of the auger, and
extends radially
outwardly from the auger shaft.
The auger blade which extends spirally outwardly from the auger shaft is
discontinuous along the entire length of the auger. In other words, a typical
auger defines
a center-most portion where the worm gear drive housing is located, and first
and second
auger blade portions which extend laterally outwardly from respective lateral
sides of the
worm gear drive housing. The first and second auger blade portions are capable
of
removing snow along their respective paths of travel; whilst the worm gear
drive housing
defines an uncut path of remaining snow along its respective path of travel.
Similar to the engagement of the means for engaging the friction drive to
provide
power to the drive wheels, the conventional auger mechanism is typically
engaged by a
belt tensioning mechanism which includes one or more belts. These belts are
also prone
to slippage, breakage, and/or other failure over time.
As with the conventional friction wheel drive mechanism, the belt tensioning
mechanism of the auger is actuated by depressing a drive-lever located on a
handlebar.
Depressing the drive-lever can require substantial force. Plus, to keep the
auger drivingly
engaged, the user must continuously hold the auger-lever in the depressed,
engage,
position, whereby the use of such auger drive mechanism can prove tiresome for
the
user. And when the user releases the auger-lever, the auger and impeller tend
to spin
until the inertial energy of the rotating parts has suitably been depleted,
which can prove
dangerous for the user and/or others in the vicinity of the snow blower.
On a conventional snow blower, the snow discharge chute has a lower portion
with
a generally cylindrical outer wall defining a generally cylindrical inner
passage. The outer
wall includes a circular flange which extends radially outwardly therefrom,
adjacent the
bottom of the discharge chute. The circular flange includes a toothed flange
gear which
interfaces with a corresponding worm gear. The worm gear and flange gear
enable a
user to rotate the snow discharge chute by rotating the worm gear and thus the
flange
gear.
The circular flange is rotatably mounted within an annular housing which has a
housing lower plate and a housing upper plate which are spaced vertically from
each
other. Namely, the circular flange is rotatably mounted between the upper and
lower
housing plates.
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Typically, the circular flange and the upper and lower housing plates are made
from ferrous, e.g. steel and other, materials. Such materials are susceptible
to rust
and/or other corrosion. In addition, in light of the intended use environment,
the circular
flange and the upper and lower h ousing p lates a re v ulnerable t o f reezing
t ogether.
Accordingly, these components of the snow discharge chute are prone to e.g.
rusting
together, and/or otherwise realizing an increase in the amount of friction
therebetween,
which compromises the ability of a user to rotate the discharge chute
according to its
intended function.
Accordingly, there are times when it might be desirable to provide snow blower
machines and/or apparatus which include a snow discharge chute rotatably
mounted on
idler wheels. In addition, it might prove desirable to provide snow blower
machines andlor
apparatus which include a cable actuated snow discharge chute assembly.
It might prove beneficial to provide snow blower machines and/or apparatus
which
include an axle assembly with a differential mechanism.
It might prove beneficial to provide snow blower machines and/or apparatus
with a
selectively lockable differential mechanism.
It might prove beneficial to provide snow blower machines and/or apparatus
with a
chain drive auger that realizes generally no uncut path along the length of
such auger.
It might prove beneficial to provide snow blower machines and/or apparatus
with
an adaptive speed control mechanism which requires relatively less user energy
input to
operate.
It might prove beneficial to provide snow blower machines and/or apparatus
with a
pulley mechanism communicating with an engine output shaft, and a first pulley
which is
always in rotational unison with the engine output shaft and provides power to
a
transmission input shaft, and a second pulley which is selectively coupled in
rotational
unison with the engine output shaft and selectively provides power to an auger
assembly.
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SUMMARY
The invention generally provides snow blowers which exhibit improved
efficiencies
through, inter alia, a rotatable discharge chute, guided in rotation by at
least one idler
wheel communicating with such chute, the rotatable discharge chute being
rotatably
actuated by a cable assembly attached thereto, first and second ground-
engaging wheels
which are attached to each other through an open carrier differential
mechanism, a
selectable lock assembly which selectively locks the first and second drive
wheels with
each other, into rotational unison with each other, as desired by a user, a
chain-driven
auger, hydraulically adaptive speed control, and/or a transmission drive
pulley and belt
between the engine and an intervening clutch.
In a first family of embodiments, the invention comprehends a walk-behind snow
blower apparatus, comprising: (a) a chassis; (b) an axle assembly
communicating with the
chassis; (c) a hydrostatic drive assembly drivingly communicating with the
axle assembly;
(d) a control handle, movement of the walk-behind snow blower apparatus being
controlled by an operator through the handle; and (e) a user input device
controllingly
attached to the hydrostatic drive assembly, the walk-behind snow blower
apparatus being
movable in a first, forward direction of travel, or in a second, opposite and
reverse,
direction of travel, at speeds which are continuously variable between a first
relatively
slower speed of travel and a second substantially faster speed of travel, and
multiple
intermediate speeds between the first and second speeds, the user input device
and the
hydrostatic drive assembly, in combination, being adapted and configured to
adaptively
control the walk-behind snow blower apparatus based on a user input applied to
the user
input device which continuously variably and adaptively influences and/or
controls the real
time speed of travel of the walk-behind snow blower apparatus.
In some embodiments, the user input device controls both direction of travel
and
the continuously variable speed of travel.
In some embodiments, the user input device is a handle which effects control
movements by pivoting the handle about an axis of pivotation.
In some embodiments, when the handle is urged in a first direction, the walk-
behind snow blower apparatus correspondingly travels in a such first direction
and when
the pivotably handle is urged in a second, opposite, direction, the walk-
behind snow
blower apparatus correspondingly travels in a such second, opposite,
direction.
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In some embodiments, the handle has a resting, neutral, position, a maximum
forward position, and a maximum reverse position, the handle being
continuously variably
movable between the maximum forward position and the maximum reverse position.
In some embodiments, the magnitude of the distance by which the handle is
displaced from the resting, neutral, position corresponds to the magnitude of
the speed at
which the walk-behind snow blower travels whereby pivotation of the handle a
relatively
greater distance from such resting, neutral, position corresponds to a
correspondingly
greater rate of speed at which the walk-behind snow blower travels.
In a second family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) a running gear assembly which includes (i) a
chassis; (ii) a first
wheel assembly and a second wheel assembly; (iii) an axle assembly
communicating with
the chassis, the axle assembly extending between the first and second wheel
assemblies
and including a differential mechanism between the first and second wheel
assemblies;
and (b) an auger assembly communicating with the running gear assembly; the
axle
assembly having a first axle shaft having an inwardly facing end and a
outwardly facing
end, and a second axle shaft having an inwardly facing end and an outwardly
facing end,
the inwardly facing ends of the first and second axle shafts being proximate
each other
and each being coupled to the differential mechanism, whereby the first and
second axle
shafts are rotatable about a generally common axis of rotation and are always
coupled to
each other by way of the differential mechanism.
In some embodiments, the differential mechanism comprises a generally hollow
differential case rotatable about an axis of rotation which is coaxial with
the axis of
rotation of the first and second axle shafts, each of the first ends of the
first and second
axle shafts having an axle inner-end gear affixed thereto, the axle inner-end
gears being
rotatable with respective ones of the first and second axle shafts and the
axle inner-end
gears being rotatably housed in the differential case.
In some embodiments, the axle inner-end gears are bevel gears and the
differential mechanism further includes fast and second spider gears which are
rotatably
housed in the differential case, each of the first and second spider gears
being rotatable
about an axis of rotation which is generally perpendicular to the axis of
rotation of the
differential case and the first and second axle shafts, each of the spider
gears spanning
between and rotatably connecting the axle inner-end gears to each other.
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In some embodiments, the snow blower further comprising a ring gear mounted to
the differential case, the ring gear and the differential case being generally
locked in
rotational unison whereby rotation of the ring rear corresponds to rotation of
the
differential case.
In some embodiments, the outwardly facing ends of the first and second axle
shafts is connected to respective ones of the first and second wheel
assemblies.
In some embodiments, the snow blower further comprising a selectable lock
assembly adapted and configured to selectively lock the first and second wheel
assemblies in rotational unison with respect to each other.
In a second family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) a chassis; (b) a first wheel assembly and a second
wheel
assembly; (c) an axle assembly communicating with the chassis, the axle
assembly
extending between the first and second wheel assemblies; and (d) a selectable
lock
assembly adapted and configured to selectively lock the first and second wheel
assemblies in rotational unison with respect to each other, the selective lock
assembly
including a tie shaft which extends in a generally common direction with, and
displaced
from, the axle assembly.
In some embodiments, the snow blower further comprising an inner hub gear
attached to one of the first and second wheel assemblies, the inner hub gear
being
selectively engageable with and disengageable from the tie shaft.
In some embodiments, the snow blower further comprising a first inner hub gear
attached to the first wheel assembly, and a second inner hub gear attached to
the second
wheel assembly, at least one of the first and second inner hub hears being
selectively
engageable with the tie shaft, and disengageable from the tie shaft.
In some embodiments, the tie shaft includes a tie shaft gear mounted
thereupon,
the tie shaft gear being adapted and configured to cooperate with a respective
one of the
hub gears.
In some embodiments, the tie shaft includes a first tie shaft gear mounted
thereon
and a second tie shaft gear mounted thereon and the first and second tie shaft
gears
being adapted and configured to cooperate with and to selectively interface
with,
respective ones of the first and second hub gears.
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In some embodiments, the tie shaft is movable between a first wheel locked
position and a second wheel unlocked position, wherein when the tie shaft is
in the wheel
locked position, the first and second wheel assemblies are generally locked in
rotational
unison with respect to each other and when the tie shaft is in the wheel
unlocked position,
the first and second wheel assemblies are generally not locked in rotational
unison with
respect to each other.
In some embodiments, the tie shaft is pivotably movable between such wheel
locked position and such wheel unlocked position.
In some embodiments, the tie shaft is resiliently pivotably movable between
such
wheel locked position and such wheel unlocked position.
In some embodiments, the tie shaft is resiliently pivotably movable between
such
wheel locked position and such wheel unlocked position and such selectable
lock
assembly further includes a biasing member which provides a resilient force
generally
resisting such pivotable movement of the tie shaft.
In some embodiments, the biasing member is a spring.
In some embodiments, the snow blower further comprising a foot-pedal
operatively
connected to the tie shaft, the foot-pedal being movable between a first
position and a
second position, whereby the foot-pedal in the first position corresponds to
the tie shaft in
the wheel unlocked position and the foot-pedal in the second position
corresponds to the
tie shaft in the wheel locked position.
In some embodiments, the snow blower further comprising a handle operatively
coupled to the tie shaft and adapted and configured for hand manipulation by a
user, the
handle being movable between a first position and a second position, whereby
the handle
in the first position corresponds to the tie shaft in the wheel unlocked
position and the
handle in the second position corresponds to the tie shaft in the wheel locked
position.
In some embodiments, the snow blower further comprising a lever assembly and a
cable assembly, operatively connected to each other, the cable assembly
actuatingly
communicating with the tie shaft, and the lever assembly being adapted and
configured
for use by a hand of a user, the communicating actions of the lever to thereby
cause
locking and unlocking actions of the tie shaft.
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In some embodiments, the axle assembly includes a first axle shaft and a
second
axle shaft, the first and second axle shafts being in generally coaxial
alignment with each
other.
In some embodiments, the tie shaft has a length dimension which is greater in
magnitude than the magnitude of length dimensions of ones of the first and
second axle
shafts, collectively.
In some embodiments, the magnitude of the length dimension of the tie shaft
corresponds generally to the sum of the length dimensions of the first and
second axle
shafts.
In a fourth family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) a running gear assembly which includes a prime
mover; (b) an
auger assembly communicating with the running gear assembly, the auger
assembly
including: (i) a chain driven auger, driven by a chain; and (ii) a shaft
driven impeller, driven
by a shaft; the auger and the impeller rotatable at first and second different
angular
rotational speeds, respectively; (c) a force transmission device having an
input shaft and
an output shaft, the input shaft and the output shaft extending in respective
directions
which are non-parallel to each other, the output shaft having a sprocket
mounted
thereupon; and the chain extending between and drivingly connecting the force
transmission device and the auger assembly.
In some embodiments, the drive chain is driven by such shaft which drives the
impeller.
In some embodiments, the force transmission device input shaft includes a
sprocket mounted thereupon.
In some embodiments, the engine output shaft extends in a direction which is
generally p arallel t o t he d irection i n w hich t he force transmission
device input shaft
extends.
In a fifth family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) a running gear assembly; (b) an auger assembly,
including an
auger housing which communicates with the running gear assembly; and (c) a
discharge
chute assembly, having a lower chute flange, and an idler wheel communicating
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therewith; the lower chute flange being rotatable about a first axis of
rotation and the idler
wheel being rotatable about a second axis of rotation, the first axis of
rotation and the
second axis of rotation extending generally parallel to each other, whereby
the idler wheel
generally guides rotating travel of the chute lower flange.
In some embodiments, the snow blower comprises first and second idler wheels,
the chute lower flange extending generally between the first and second idler
wheels,
wherein the chute lower flange is adapted and configured to rollingly and/or
slidingly
communicate with ones of the first and second idler wheels.
In some embodiments, the chute flange generally defines an outer perimeter and
the snow blower comprises a plurality of idler wheels, the plurality of idler
wheels rollingly
and/or slidingly communicating with the chute lower flange, the idler wheels
being spaced
generally equidistant from other respective ones of the idler wheels about the
outer
perimeter of the chute flange.
In some embodiments, the idler wheel defines an outer circumferential surface,
a
groove extending into the outer circumferential of the idler wheel and
optionally about the
entire circumference of the idler wheel.
In some embodiments, the chute lower flange defines a thickness dimension and
the idler wheel includes an outer circumferential surface and a groove
extending into the
outer circumferential surface, the groove defining a groove opening width, and
a groove
depth, and wherein the magnitude of the groove width is greater than the
magnitude of
the chute lower flange thickness dimension.
In some embodiments, the idler wheel defines an outer circumferential surface,
a
groove extending into the outer circumferential of the idler wheel, a portion
of the chute
flange being housed in, optionally slidingly housed in, a corresponding
portion of the
groove which extends into the idler wheel outer circumferential surface.
In some embodiments, the idler wheel defines an outer circumferential surface
and
a groove extends into the outer circumferential of the idler wheel, the chute
flange being
received in the idler wheel groove, the idler wheel and the chute flange
generally rollingly
interfacing with each other.
In some embodiments, the idler wheel is made from polymeric material.
In a s ixth f amity o f a mbodiments, t he i nvention c omprehends a s now
blower
apparatus, comprising: (a) a running gear assembly; (b) an auger assembly,
including an
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auger housing which communicates with the running gear assembly; (c) a
discharge
chute, having an outer wall, the discharge chute being rotatably connected to
the auger
housing; and (d) a control handle, movement of the snow blower apparatus being
controlled by an operator through the control handle, the control handle
having a proximal
end proximate the running gear assembly and a remote end displaced from the
running
gear assembly; (e) a cable assembly attached to the discharge chute outer wall
and
having a first cable segment and a second cable segment; and (f) a cable
receptacle and
controller assembly mounted on the handle proximate the remote end of the
handle,
wherein when a force is applied in a first direction to the first cable
segment, the
discharge chute rotates in a first direction of chute rotational travel and
when a force is
applied in such first direction to the second cable segment, the discharge
chute rotates in
a second, opposite, direction of chute rotational travel.
In some embodiments, the discharge chute defining an outer perimeter, wherein
the first cable segment extends around the discharge chute outer perimeter in
a first
direction and the second cable segment extends around t he d ischarge c hute o
uter
perimeter in a second, opposite, direction.
In some embodiments, the snow blower apparatus further comprising a rotatable
handle o n the cable receptacle and controller assembly, the rotatable handle
being
rotatable in a first direction of handle rotational travel and in a second,
opposite, direction
of handle rotational travel, thereby to rotate the cable receptacle and
controller assembly,
the first direction of handle rotational travel corresponding to the first
direction of chute
rotational travel and the second direction of handle rotational travel
corresponding to the
second direction of chute rotational travel.
In some embodiments, the cable receptacle and controller assembly comprising a
generally cylindrical idler spool, the idler spool being adapted and
configured to windingly
store portions of the cable thereupon and to windingly release portions of the
cable
therefrom, upon rotation of the handle.
In a seventh family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) an engine having an output shaft; (b) a
transmission; (c) a
plurality of drive wheels drivingly connected to the transmission; and (d) an
electromagnetic clutch and pulley assembly communicating with the engine
output shaft
and comprising (i) a first pulley connected to, and locked in rotational
unison with, the
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engine output shaft and located relatively proximate the engine; (ii) a second
pulley,
located relatively distal from the engine, which selectively rotates with the
engine output
shaft; and (iii) an electromagnetic clutch connected to the engine output
shaft and
selectably coupled to the second pulley, the electromagnetic clutch being
selectable
between a first engaged condition and a second disengaged condition, the
second pulley
generally rotating with the engine output shaft when the electromagnetic
clutch is in such
engaged condition, and the second pulley generally not rotating with the
engine output
shaft when the electromagnetic clutch is in such disengaged condition.
In some embodiments, the transmission includes a transmission input shaft, the
transmission input shaft and the engine output shaft being generally
perpendicular to
each other.
In some embodiments, a third pulley is mounted upon the transmission input
shaft,
the snow blower further comprising a belt connecting the second pulley and the
third
pulley to each other.
In some embodiments, a third pulley is mounted upon the transmission input
shaft,
the transmission input shaft and the engine output shaft being oriented
generally
perpendicular to each other, the snow blower further comprising a belt
operatively
extending between the second and third pulleys.
In some embodiments, a first idler wheel mounted between the second pulley and
the third pulley and communicating with the belt.
In some embodiments, the snow blower further comprising a first idler wheel
mounted between the second pulley and the third pulley and communicating with
the belt,
the second idler wheel having an outer circumferential surface, the belt, at
any given time,
extending along about 25% of the outer circumferential surface of the idler
wheel.
In some embodiments, the belt defines about 90 degrees change in direction of
the
belt about the outer circumferential surface of the idler wheel.
In some embodiments, the electromagnetic clutch further comprises a brake,
wherein when the electromagnetic clutch is in a disengaged condition, the
brake is in an
engaged condition.
In an eighth family of embodiments, the invention comprehends a snow blower
apparatus, comprising: (a) an engine having an output shaft; (b) a
transmission; and (c) a
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plurality of drive wheels drivingly connected to the transmission; and (d) a
pulley
assembly attached to the engine output shaft; the pulley assembly including a
first pulley,
a second pulley, and a belt mounted about the first pulley, the first pulley
being fixedly
secured to the engine output shaft and rotating in unison therewith, the belt
being
constantly tensioned, and thereby being constantly driven by the first pulley,
the second
pulley selectively rotating in unison with the engine output shaft.
In some embodiments, the second pulley is connected to a clutch mechanism, the
clutch mechanism being attached to the engine output shaft whereby the second
pulley
clutchingly selectively rotates in unison with the engine output shaft.
In some embodiments, the clutch mechanism is an electromagnetic clutch.
In some embodiments, the belt also engages, and drives, first and second drive
wheels which are constantly connected to each other and wherein the first and
second
drive wheels can be driven at first and second speeds at a given point in
time.
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BRIEF DESCRIPTION OF THE DRAWINGS
FIGURE 1A shows a first pictorial view of snow blower apparatus of the
invention.
FIGURE 1 B shows a second pictorial view of the snow blower apparatus of
FIGURE 1A.
FIGURE 2A shows an exploded, pictorial, view of parts of the running gear
assembly and various adjacent parts of the snow blower apparatus of FIGURE 1A.
FIGURE 2B shows a cut-away view of portions of the differential assembly.
FIGURE 3 shows an exploded, pictorial, view of the auger assembly and various
adjacent parts of the snow blower apparatus of FIGURE 1A.
FIGURE 4 shows an exploded, pictorial, view of the handle assembly and various
adjacent parts of the snow blower apparatus of FIGURE 1A.
FIGURE 5 shows an enlarged, pictorial, view of a portion of the handle
assembly
of FIGURE 1A.
FIGURE 6 shows an exploded, pictorial, view of parts of the running gear
assembly
and various adjacent parts, including a wheel assembly, of the snow blower
apparatus of
FIGURE 1A.
FIGURE 7 shows a pictorial view of parts of the running gear assembly, with
one
wheel assembly and other components removed, including a first embodiment of
selectable lock assemblies of the invention.
FIGURE 8 shows a pictorial view of parts of the running gear assembly, with
one
wheel assembly and other components removed, including a second embodiment of
selectable lock assemblies of the invention.
FIGURE 9A shows a side elevation of the selectable lock assembly of FIGURE 7
in a wheel unlocked position.
FIGURE 9B shows a side elevation of the selectable lock assembly of FIGURE 7
in a wheel locked position.
FIGURE 10 shows an exploded, pictorial, view of parts of the auger assembly
and
discharge chute assembly of FIGURE 1A.
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FIGURE 11 shows an exploded, pictorial, view of parts of the discharge chute
assembly of the snow blower apparatus of FIGURE 1A.
FIGURE 12 shows a schematic diagram of exemplary electrical circuits of snow
blowers of the invention.
The invention is not limited in its application to the details of construction
or the
arrangement of the components set forth in the following description or
illustrated in the
drawings. The invention is capable of other embodiments or of being practiced
or carried
out in other various ways. Also, it is to be understood that the terminology
and
phraseology employed herein is for purpose of description and illustration and
should not
be regarded as limiting. Like reference numerals are used to indicate like
components.
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DESCRIPTION OF THE ILLUSTRATED EMBODIMENTS
FIGURES 1 A and 1 B show different pictorial views of a first embodiment of
snow
blower apparatus 1 of the invention. In a typical implementation of the
invention, a snow
blower 1 includes running gear assembly 5, prime mover 100, handle assembly
200,
auger assembly 300, and discharge chute assembly 391.
Although the exemplary embodiments illustrated herein illustrate snow blower 1
as
being adapted and configured as a self-propelled, walk behind, apparatus, at
least some
of the novel and non-obvious features, components, combinations,
subassemblies,
assemblies, and methods, are equally applicable to other various snow removal
devices
and are well within the scope of the invention in such implementation. Such
other various
snow removal devices include, but are not limited to, those operably mounted
to lawn
tractors, skid-steer tractors, full-size tractors, all-terrain-vehicles,
pickup trucks, full-size
trucks, and/or others, and are well within the scope of the invention.
As will be described in greater detail hereinafter, running gear 5 is
operatively
attached, by way of, for example, power transmission assembly 60 (FIGURE 2A),
to
prime mover 100, whereby prime mover 100 generally provides power to the snow-
engaging elements of snow blower 1. Handle assembly 200 is attached to a first
end
portion of running gear assembly 5 and is adapted and configured to transmit
user control
input to the remainder of the assemblage of snow blower 1. Auger assembly 300
is
attached to a second, opposite, end portion of running gear assembly 5, is
adapted and
configured to pull, drag, sweep, or otherwise draw and/or receive e.g. snow
thereinto, and
generally defines a first-stage of snow blower 1. Discharge chute assembly 391
is
mounted generally between, and communicates with each of, running gear
assembly 5
and auger assembly 300. The discharge chute assembly 391 is adapted and
configured
to remove snow from auger assembly 300 and/or to otherwise accept snow from
the
auger assembly and blow, throw, propel, and/or otherwise discharge such snow
from the
snow blower apparatus.
Referring now to FIGURES 2A, 3 and 6, running gear assembly 5 includes chassis
7, transaxle assembly 10, and wheel assemblies 20. Chassis 7 includes chassis
top-
plate 7A, first and second chassis sidewalls 7B, 7C, chassis lower flanges 7D,
7E, and
chassis frame rails 7F, 7G.
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As desired, a plurality of bores "B" extend through various suitable portions
and
locations of chassis 7, e.g. through ones of chassis top-plate 7A, first and
second chassis
sidewalls 7B, 7C, and chassis lower flanges 7D, 7E. Chassis 7 generally
defines the
structure, e.g. support structure, frame structure, and/or mounting structure,
upon which
various other parts, components, subassemblies, and assemblies are mounted, by
way of
bores "B" or otherwise.
Chassis top-plate 7A is generally planar, has a length, and a width defined
between two lateral edges. Each of the first and second chassis sidewalls 7B,
7C is a
planar member which has an upper edge, a lower edge, and two lateral edges
which
define a width therebetween.
The upper edge of chassis sidewall 7B is connected to the first lateral edge
of
chassis top-plate 7A. Sidewall 7B extends generally angularly downwardly and
outwardly,
along a generally straight line path, from the point of intersection with top-
plate 7A. In
other words, chassis sidewall 7B slopes downwardly and outwardly from top-
plate 7A.
Elongate bore "EB" extends through the thickness of sidewall 7B, and has a
bore length
and a bore width. The bore length of elongate bore "EB" is greater in
magnitude than the
magnitude of the bore width, whereby elongate bore "EB" defines a slot which
extends
through sidewall 7B.
The upper edge of chassis sidewall 7C is connected to the second lateral edge
of
chassis top-plate 7A. Sidewall 7C extends generally angularly downwardly and
outwardly, along a generally straight line path, from the point of
intersection with top-plate
7A. In other words, chassis sidewall 7C slopes downwardly and outwardly from
top-plate
7A, in generally the opposite direction from the direction of extension of
sidewall 7B.
Like chassis sidewall 7B, an elongate bore "EB" extends through the thickness
of
sidewall 7C, and has a bore length and a bore width. The bore length of
elongate bore
"EB" is greater in magnitude than the magnitude of the bore width, whereby
elongate bore
"EB" defines a slot which extends through sidewall 7C. The elongate bores "EB"
of the
sidewalls 7B, 7C are generally in coaxial alignment with each other.
Each o f t he c hassis I ower flanges 7D, 7E is a planar member which has an
inwardly facing edge, an outwardly facing edge, and two end edges. Lower
flanges 7D
and 7E are generally coplanar with each other and are generally parallel to
chassis top-
plate 7A. The inwardly facing edges of lower flanges 7D and 7E are connected
to the
lower edges of sidewall 7B and sidewall 7C, respectfully. Each lower flange
7D, 7E
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extends outwardly away from the respective chassis sidewall 7B, 7C, whereby
the lower
flanges 7D, 7E extend outwardly from the sidewalls in generally opposite
directions.
Each of chassis frame rails 7F, 7G is an elongate, rigid member which is
adapted
and configured to hold, carry, and/or otherwise support various components of
snow
blower 1. In addition, frame rails 7F, 7G, are adapted and c onfigured t o o
ffer, f or
example, relatively increased rigidity and/or strength to certain portions of
the chassis 7.
As illustrated, each of frame rails 7F, 7G has a generally upright portion
which
defines a top and bottom thereof, and first and second transversely extending
flanges and
each is connected to the remainder of chassis 7 through, for example, chassis
top-plate
7A. The first flange extends from the top of the upright portion, toward the
other
respective frame rail, and the second flange extends from the bottom of the
upright
portion, toward the other respective frame rail and generally parallel to the
first flange,
whereby each of the frame rails generally defines a channel configuration.
The first and second flanges of frame rails 7F, 7G extend along planes which
are
generally parallel to the plane defined by chassis top-plate 7A. In the
complete
assemblage of chassis 7, chassis top-plate 7A overlies and generally
interfaces with a
portion of the length of frame rails 7F, 7G
Transaxle assembly 10 is operatively attached to and receives power from prime
mover 100 and includes drive housing "D-H," hydrostatic drive assembly 10A,
transaxle
pulley 10B, and axle assembly 12. Transaxle assembly 10, alone and/or in
combination
with other various components, e.g. controls, of snow blower 1, is adapted and
configured
to enable a user to adaptively control the speed and/or direction of travel of
snow blower
1.
Hydrostatic drive assembly 10A includes drive input shaft "I-S," at least one
hydraulic pump, namely at least one variable displacement hydraulic pump, at
least one
hydraulic motor which can have a motor output shaft, a drive assembly output
shaft which
can include a pinion gear e.g. pinion gear "P" (FIGURE 2B), optionally a
sprocket and
chain assembly, optionally other force suitable force transmitting devices, at
the end
thereof. H ydrostatic d rive a ssembly 1 OA further i ncludes v arious a ser c
ontrol i nput
devices, which include, but are not limited to, input control shaft 30A, input
arm 30B, input
bracket 30C, roll-release shaft 32, roll-release arm 40, roll-release lever
50, and/or others,
as well as various pieces of suitable hydraulic plumbing e.g. various suitable
tubes,
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hoses, pipes, fittings, valves, switches, hardware, housings, linkages, force
transmission
devices and/or others.
Drive housing "D-H" is a multiple walled enclosure structure which has, for
example, a top wall, a bottom wall, and a front wall, a back wall, and first
and second
sidewalls. Ones of the various walls of drive housing "D-H" are connected to
other
respective ones of the walls, so that the entire assemblage is generally
liquid tight,
capable of suitably holding e.g. hydraulic fluid therein.
Also, drive housing "D-H" is adapted and configured to enclosingly house ones
of,
for example, the variable displacement hydraulic pump, the hydraulic motor,
various
pieces of suitable hydraulic plumbing e.g. various suitable tubes, hoses,
pipes, fittings,
valves, switches, hardware, housings, at least part of the drive input shaft
"I-S," and/or
other components of hydrostatic drive assembly 1 OA, therein. In other words,
the interior
space of drive housing "D-H" generally defines the operating environment of
hydrostatic
drive assembly 10A.
Hydrostatic drive assembly 10A realizes a continuously, e.g. infinitely,
variable
rotational speed output of the hydraulic motor output shaft, whereby the speed
by which
snow blower 1 moves along the ground is continuously, infinitely, e.g. without
step
changes in magnitude, variable between a minimum speed and a maximum speed, in
each of a forward direction and an opposite, reverse, direction.
Drive input shaft "I-S" is an elongate, rotatable, shaft which defines an
outside
diameter and is cooperatively coupled to the variable displacement hydraulic
pump.
Namely, input shaft "I-S" transmits the energy, e.g. the rotational energy, to
the variable
displacement hydraulic pump.
An end of input shaft "I-S" extends outwardly beyond the drive housing "D-H."
Input shaft "I-S" rotatably interfaces with drive housing "D-H" by way of, for
example, a
seal assembly and/or a bearing assembly which enables the input shaft to
rotate with
respect to the drive housing while having a generally liquid tight seal
between the shaft
and housing.
The variable displacement hydraulic pump and the hydraulic motor,
hydraulically
communicate with each other. The variable displacement hydraulic pump is
adapted and
configured to drive the hydraulic motor which effectuates rotational movement
of a motor
output shaft which extends from the hydraulic motor.
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In the entire assemblage of hydrostatic drive assembly 10A, the rotational
energy
of input shaft "I-S" is converted to fluid flow and thus fluid energy by way
of the hydraulic
pump, whereby the pump transmits the fluid to the hydraulic motor. The
hydraulic motor
receives the fluid flow, and converts the fluid flow energy back to rotational
energy and
motion.
In use of snow blower 1, a user controls, as desired, the volume and velocity
of
hydraulic fluid which flows from the variable displacement hydraulic pump to
and/or from
the hydraulic motor, and the direction of rotational travel of the hydraulic
motor. In other
words, a user of snow blower 1, as desired, adaptively controls the speed
and/or direction
of travel of snow blower 1. The user at least partially controls the direction
and speed
output of the hydraulic motor by way of input control shaft 30A, input arm
30B, and input
bracket 30C.
Input control shaft 30A is pivotable, about an axis of pivotation, in first
and second
directions of pivotation. The control shaft 30A operably communicates with
ones of the
components of hydrostatic drive assembly 10A, whereby the direction of
pivotation and
magnitude of pivotal travel correspond to direction and magnitude of
rotational speed
output of the hydraulic motor and thus the direction and magnitude of movement
of snow
blower 1 along the ground.
Input arm 30B is an elongate, rigid, member which has a bore extending through
the thickness thereof. The bore of input arm 30B concentrically accepts the
end of input
control shaft 30A therein. And the shaft 30A and input arm 30B are fixedly
attached to
each other, by way of e.g. cooperating splines, keys and keyways, aligned
bores and
insertable pins, press fit, friction fit, weldments, and/or others.
Accordingly, input arm 30B pivots about an axis of pivotation common to that
of
control shaft 30A. Since the shaft 30A and arm 30B are fixedly attached to
each other,
pivotal movement of arm 30B causes a corresponding pivotal movement of shaft
30A,
and thus a corresponding output of the hydrostatic drive assembly 10A.
Input bracket 30C is adapted and configured to enable various control devices,
remote from the hydrostatic drive assembly 10A, to be operably coupled to
input arm 30B
and thus input control shaft 30A. Input bracket 30C is generally planar and
has various
bores extending through the thickness thereof which are adapted and configured
to
suitably receive and/or house various components of e.g. user input devices
therein. As
desired, input bracket 30C includes, for example, first and second tabs which
extend
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generally perpendicularly from the remainder of the bracket, toward the
hydrostatic drive
assembly 10A. Each tab communicates with a respective lateral side surface of
input
arm 30B which generally increases the ability of input bracket 30C to transmit
a force
applied thereto to the input arm 30B.
Roll-release shaft 32 extends outwardly from the top wall of drive housing "D-
H"
and is pivotably movable between a first and second position. Roll-release
shaft 32 is
adapted and configured to e.g. release axle shafts 15A, 15B, from ones of the
other
components of transaxle assembly 10 and/or to otherwise enable wheel
assemblies 20 to
freewheel with respect to transaxle assembly 10. Namely, when roll-release
shaft 32 is in
the first position, wheel assemblies 20 generally freely rotate with respect
to ones of the
components of transaxle assembly 10 and when roll-release shaft 32 is in the
second
position the wheel assemblies do not generally freely rotate with respect to
ones of the
components of transaxle assembly 10.
Roll-release arm 40 is a generally elongate, planar bracket with a first,
relatively
wider end, and a second, relatively less wide, end. Each of the first and
second ends of
roll-release arm 40 has a bore which extends through the thickness thereof.
The bore of
the first roll-release arm end is adapted and configured to, at least in part,
fixedly attach
roll-release arm 40 to roll-release shaft 32. Namely, roll-release shaft 32
and roll-release
arm 40 are attached to each other by way of, for example, keys and
corresponding
keyways, corresponding splines, setscrews, and/or otherwise. Thus, roll-
release arm 40
pivots about a common axis, and in unison, with roll-release shaft 32.
The bore of the second end of roll-release arm 40 is adapted and configured to
pivotably house part of roll-release lever 50 therein. Roll-release lever 50
is an e.g. S-
shaped rigid member with first and second ends, and extends through, for
example, an
aperture in a locating bracket which generally positionally locates the lever
with respect to
transaxle assembly 10. The first end of roll-release lever 50 is pivotably
housed in the
bore of the second roll-release arm end, whereby a force imparted to roll-
release lever 50
is transferred therethrough, upon roll-release arm 40, and thus to roll-
release shaft 32.
The second end of roll-release lever 50 is adapted and configured for
manipulation
by a user. In other words, a user can, for example, grasp the second end of
roll-release
lever 50 and push and/or pull the lever, which pivots roll-release arm 40 and
roll-release
shaft 32 so as to either release or un-release wheel assemblies 20 from ones
of the
components of transaxle assembly 10, as desired.
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In some embodiments, a medial portion of roll-release lever 50 has an annular
groove which extends around the circumferential surface thereof. The annular
groove is
adapted and configured to interface with portions of locating bracket, whereby
the
mechanical interfacing of the locating bracket and the annular groove
generally
positionally secures roll-release lever 50 with respect to transaxle 10.
Transaxle pulley 1 OB is adapted and configured to transmit rotational energy
from
e.g. prime mover 100 by way of, for example power transmission assembly 60, to
input
shaft "I-S" of transaxle assembly 10. Pulley 10B defines an outside diameter,
an inside
diameter, and an outer circumferential surface. The inside diameter of pulley
10B
corresponds to the outside diameter of the drive input shaft "I-S" and pulley
10B is
mounted, in rotational unison, to the drive input shaft. Accordingly, as
pulley 10B rotates,
input shaft "I-S" correspondingly rotates.
The outside diameter of pulley 1 OB is selected so that pulley 1 OB, alone
and/or in
combination with other components of snow blower 1, provides the desired
rotational
speed reduction, optionally desired rotational speed increase, between e.g.
the output
shaft of prime mover 100 and drive input shaft "I-S."
The outer circumferential surface of pulley 10B is adapted and configured to
suitably interface with a means of transmitting and/or otherwise conveying
power from
e.g. prime mover 100 to input shaft "I-S" such as belts and/or other
continuous bands of
material adapted and configured to transmit power.
Referring now to FIGURES 2A, and 2B, axle assembly 12 communicates with
and/or is attached to hydrostatic drive assembly 10A. Optionally, as desired,
axle
assembly 12 and hydrostatic drive assembly 10A are integral and generally
define a
unitary body of transaxle assembly 10.
Axle assembly 12 includes axle housing 13, differential mechanism assembly 14,
and first and second axle shafts 15A, 15B. Axle housing 13 is connected to the
front wall
of d rive h ousing D-H a nd g enerally a nvelopes a nd a ncloses differential
mechanism
assembly 14 and parts of axle shafts 15A, 15B. In embodiments in which the
hydrostatic
drive assembly 10A and axle assembly 12 are integral, drive housing "D-H" and
axle
housing 13 are correspondingly also integral, whereby drive housing "D-H" can
be
generally devoid of a front wall and the front-most portion of transaxle
assembly 10 is
generally defined by the front-most portion of axle housing 13.
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Referring now to FIGURE 2B, axle housing 13 includes first and second lateral
portions 13A, 13B, and medial portion 13C. First portion 13A is elongate, has
an outer
circumferential wall which has an inner surface and an outer surface. The
inner surface
of the outer circumferential wall generally defines an outermost perimeter of
a generally
cylindrical cavity which extends axially through the first portion 13A.
Axle housing first lateral portion 13A generally concentrically houses first
axle shaft
15A therein, whereby axle shaft 15A is generally free to rotate with respect
to first lateral
portion 13A, defining an axis of rotation. Specifically, axle shaft 15A is
rotatably housed
in a bearing e.g. bearing "BR" which is in turn housed, by way of press-fit or
otherwise,
concentrically within first lateral portion 13A.
The number of bearings "BR" used and the spacing distance, for example,
between respective bearings "BR" along the length of first lateral portion
13A, as well as
the particular bearing design, size, and/or other characteristics, correspond
at least in part
to the particular intended use environment and expected loads of snow blower
1. As one
example, as desired, first lateral portion 13A includes a bearing "BR"
adjacent each end
thereof, which provides radial and rotational support to axle shaft 15A at at
least two
distinct locations along its length.
The axle housing second lateral portion 13B is elongate, has an outer
circumferential wall which has an inner surface and an outer surface. The
inner surface
of the outer circumferential wall generally defines an outermost perimeter of
a cylindrical
cavity which extends axially through second lateral portion 13B.
Second lateral portion 13B generally concentrically houses second axle shaft
15B
therein, whereby axle shaft 15B is generally free to rotate with respect to
the housing
second lateral portion 13B, defining a n a xis o f r otation. N amely, a xle s
haft 1 5B i s
rotatably housed in a bearing e.g. bearing "BR" which is in turn housed, by
way of press-
fit or otherwise, concentrically within second lateral portion 13B.
Like first lateral portion 13A, the number of bearings "BR" used and the
spacing
distance between respective bearings "BR," along the length of second lateral
portion
13B, as well as the particular bearing design, size, and/or other
characteristics
correspond, at least in part, to the particular intended use environment and
expected
loads of snow blower 1. As one example, second lateral portion 13B can include
a
bearing "BR adjacent each end thereof, which provides radial and rotational
support to
axle shaft 15B adjacent the first and second ends of second lateral portion
13B.
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Axle housing medial portion 13C extends between and connects the inwardly
facing ends of first and second lateral portions 13A, 13B. Medial portion 13C
has first
and second ends which define a length therebetween, and a cavity generally
defined
there within. The cavity within medial portion 13C generally encapsulates and
houses
differential mechanism assembly 14, and at least portions of axle shafts 15A,
15B.
As desired, medial portion 13C includes suitable bearing mounting structure to
mount ones of bearings "BR" adjacent the ends of axle shaft 15A and/or axle
shaft 15B.
Such suitable bearing mounting structure includes, but is not limited to, e.g.
a cast web
such as casting "C" and a corresponding bearing retaining member such as
bearing cap
"BC." Bearing cap "BC" is adapted and configured to clampingly secure bearing
"BR"
against casting "C," whereby to generally locationally fix the bearing within
the cavity of
medial portion 13C.
Each of the first and second ends of medial portion 13C has a relatively
lesser
diameter as compared to the remainder of medial portion 13C. Thus, medial
portion 13C
defines a greatest diameter portion thereof, between the first and second
ends, whereby
from the first end, along the length of medial portion 13C, the medial portion
radially
increases toward the greatest diameter portion thereof, then, from the
greatest diameter
portion thereof, radially decreases toward the second end of medial portion
13C.
Differential mechanism assembly 14 includes ring gear 111, differential case
112,
spider gears 113A, 1138, spider gear shaft 114, and axle inner end gears 115A,
115B.
The differential mechanism assembly 14 connects axle shafts 15A, 15B, to each
other
and enables the axle shafts to rotate in a common direction at generally the
same speed,
in a common direction at generally different speeds, in opposite directions at
generally the
same speed, or in opposite directions at generally different speeds, while
still attached to
each other through the differential mechanism assembly.
Ring gear 111 is a generally annular bevel gear, optionally a spiral-cut bevel
gear,
optionally other suitable configurations. Ring gear 111 has a toothed e.g.
front surface
facing a first direction and a generally planar e.g. back surface facing a
second, opposite
direction. R ing g ear 1 11 i s a dapted a nd c onfigured t o t ransmit t
orque p rovided b y
hydrostatic drive assembly 10A, alone or in combination with other components,
from
hydrostatic drive assembly 10A into rotational motion of the differential
mechanism
assembly 14 and correspondingly to the axle shafts 15A, 15B.
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Namely, ring gear 111 is adapted and configured to operatively interface with
and
be rotated by pinion gear "P" which extends from the hydrostatic drive
assembly 10A. In
other words, pinion gear "P" and ring gear 111 are generally perpendicular to
each other
and generally define an interfacing gear-mesh relationship therebetween.
Differential case 112 includes a generally circular plate e.g. case back-plate
112A,
a circumferential outer wall e.g. case outer wall 1128, and a top wall. The
surface of
case back-plate 112A which faces the remainder of differential case 112
interfaces with
the generally planar e.g. back surface of ring gear 111.
Ring gear 111 and differential case 112 are connected to each other, and thus
in
rotational unison with each other, by way of, for example, but not limited to,
corresponding
bores and threaded bores in the case back-plate and ring gear, respectively,
and suitable
hardware. As one example, bores extend through case back-plate 112A and
threaded
bores extend into the generally planar back surface of ring gear 111. Bores of
the back-
plate 112A are coaxially aligned with corresponding threaded bores of the ring
gear and
suitable bolts extend therethrough, whereby ring gear 111 is threadedly
secured to case
back-plate 112A
Case outer wall 1128 extends generally axially outwardly from the case back-
plate
112A. The inwardly facing surface of outer wall 1128 generally defines an
outer
perimeter of a cavity within differential case 112. The cavity within
differential case 112
houses Spider gears 113A, 1138, spider gear shaft 114, and axle inner end
gears 115A,
1158.
As desired, outer wall 1128 includes at least one opening extending
therethrough,
into the case cavity. First and second bores extend through outer wall 1128
and into the
case cavity. These first and second bores are generally coaxially aligned with
each other.
Also, the top wall of differential case 112 and case back-plate 112A each has
a bore
which extends axially and medially therethrough. The bores of the top wall and
back-
plate 112A are coaxially aligned with each other and are adapted and
configured to
accept the end of axle shaft 15A and the end of axle shaft 158 therethrough,
respectively.
Each of spider gears 113A, 1138 is a bevel gear, optionally a spiral-cut bevel
gear,
optionally other suitable configurations, which communicates with case outer
wall 1128
and has a bore which extends axially and medially therethrough. The spider
gears 113A,
1138 generally face each other and are rotatably mounted to generally opposite
portions
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of case outer wall 112B, w hereby t he t oothed s urfaces o f t he g ears g
enerally f ace
inwardly into the cavity of differential case 112.
Spider gear shaft 114 is an elongate, columnar, rod or pin which extends
between
the first and second spider gears 113A, 113B. Namely, first and second ends of
shaft
114 extend through the bores of spider gears 113A and 113B, respectively.
Thus, the
first end of shaft 114 extends outwardly beyond spider gear 113A and into one
of the
bores which extends through differential case sidewall 112B. The second end of
shaft
114 extends outwardly beyond spider gear 113B and into the other one of the
bores
which extends through differential case sidewall 112B.
The spider gears 113A, 113B are rotatably mounted to spider gear shaft 114. In
particular, spider gears 113A, 113B are independently rotatably mounted to
spider gear
shaft 114, whereby the spider gears can rotatably travel in generally the same
direction or
in generally opposite directions with respect to each other.
Axle inner a nd g ear 1 15A i s a b evel g ear, o ptionally a s piral-cut b
evel g ear,
optionally other suitable configurations, which communicates with the
differential case top
wall and has a bore which extends axially and medially therethrough. End gear
115A
rotates about and axis of rotation which is generally perpendicular to spider
gear shaft
114 and thus to spider gears 113A, 113B.
The bore of end gear 115A defines a splined inner circumferential surface
which is
adapted and configured to slidingly insert onto a correspondingly splined
outer
circumferential surface of the inwardly facing end of axle shaft 15A. Thus,
when end gear
115A is mounted to axle shaft 15A, the axle shaft 15A and end gear 115A are
connected
in rotational unison which each other.
The toothed surface of axle inner end gear 115A is adapted and configured to
cooperate with the toothed surfaces of spider gear 113A and spider gear 113B,
simultaneously. In other words, end gear 115A and the spider gears 113A, 113B
generally define an interfacing gear-mesh relationship therebetween.
Like axle inner end gear 115A, axle inner end gear 115B is also a bevel gear,
optionally a spiral-cut bevel gear, optionally other suitable configurations.
End gear 115B
communicates with the differential case back-plate 112A and has a bore which
extends
axially and medially therethrough. End gear 115B rotates about an axis of
rotation which
is generally perpendicular to spider gear shaft 114 and thus spider gears
113A, 113B.
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The bore of end gear 1158 defines a splined inner circumferential surface
which is
adapted and configured to slidingly insert onto a correspondingly splined
outer
circumferential surface of the inwardly facing end of axle shaft 158. Thus,
when end gear
1158 is mounted to axle shaft 158, the axle shaft 158 and end gear 1158 are
connected
in rotational unison which each other.
The toothed surface of axle inner end gear 1158 is adapted and configured to
cooperate with the toothed surfaces of spider gear 113A and spider gear 1138,
simultaneously. In other words, end gear 1158 and the spider gears 113A, 1138
generally define an interfacing gear-mesh relationship therebetween.
In use, pinion gear "P" rotatably drives ring gear 111. As ring gear 111
rotates,
correspondingly so does differential case 112. In other embodiments, such as
embodiments which use a chain or other force transmission device to rotate the
differential case, the chain or other device operably interfaces with and
rotatably drives
the differential case 112.
The rotating differential case 112 ultimately rotates axle end gears 115A,
1158, by
way of spider gears 113A, 1138. When spider gears 113A, 1138 rotate along a
first axis
of rotation dictated by the rotation of differential case 112, yet do not
rotate upon spider
gear shaft 114, the spider gears 113A, 1138 collectively rotate the axle end
gears 115A,
1158 and thus axle shafts 15A, 158 at generally the same speed and in the same
direction.
By contrast, when spider gears 113A, 1138 rotate upon spider gear shaft 114
and
thus about an axis of rotation generally defined by the spider gear shaft, in
addition to
and/or in lieu of the rotation dictated by the rotation of differential case
112, the spider
gears 113A, 1138 generally, rotatably, and gear-meshingly e.g. advance and/or
regress
with respect to respective ones of axle end gears 115A, 1158, whereby the axle
end
gears and correspondingly axle shafts 15A, 15B rotates at, for example,
generally
different rotational speeds with respect to each other.
The particular manner, e.g. magnitude of speed and direction, in which ones of
the
differential case 112, spiders gears 113A, 1138, and/or axle end gears 115A,
1158 rotate
with respect to each other, corresponds to direction and speed of rotational
travel realized
at each of axle shaft 15A and axle shaft 158. In other words, differential
mechanism
assembly 14 enables the axle shafts 15A, 158, t o r otate i n a c ommon d
irection a t
generally the same speed, in a common direction at generally different speeds,
in
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opposite directions at generally the same speed, or in opposite directions at
generally
different speeds, while still attached to each other through the differential
mechanism
assembly.
Referring now to FIGURE 2A, prime mover 100 includes internal combustion
engine 105, fuel tank 107, starting mechanism 108, and mounting plate 110.
Internal
combustion engine 105 can be any suitable internal combustion engine as
desired,
including but not limited to, various 4-stroke engines, 2-stroke engines,
gasoline powered
engines, diesel powered engines, and/or others. In addition, the particular
internal
combustion engines 105 utilized include corresponding suitable fuel delivery
systems to
provide fuel/air mixtures to the internal combustion engine. Such suitable
fuel delivery
systems include, but are not limited to, carburetor based fuel delivery
systems, fuel
injection based fuel delivery systems e.g. throttle body injection systems,
multi-port
injection systems, direct injection systems, and/or others.
Fuel tank 107 is a generally enclosed, liquid tight, cell adapted and
configured to
hold fuel for a se b y t he i nternal c ombustion a ngine 1 05. N amely, f uel
t ank 1 07 i s
plumbed to, or otherwise operably connected to, for example, the fuel delivery
system of
internal combustion engine 105.
Starting mechanism 108 communicates with internal combustion engine 105 and is
adapted and configured to enable a user to start the engine. Starting
mechanism 108
includes, but in not limited to, one or more of various suitable starting
devices such as
starting rope devices, electric motor starting devices, and/or others.
Preferably, starting
mechanism 108 includes a 12 Volt Direct Current electric starting motor which
utilizes an
on-board 12 Volt Direct Current battery e.g. battery 966 (FIGURE 4) and
further includes
e.g. a rope-or cable based recoil, manual start backup mechanism.
Battery 966 is generally housed within an enclosure structure defined at least
in
part by battery tray 610, battery box 969, battery cover 970, and/or others.
Battery tray
610 extends between frame rails 7F and 7G (FIGURE 4). Cushion 615 lies between
and
provides at least some shock absorption between battery tray 61 and part of
the bottom
surface of battery 966.
Battery box 969 generally covers e.g. the side surfaces of battery 966. The
battery
is restrained in the enclosure structure by way of e.g. threaded draw rod 967
which is
connected at a first end to battery tray 610 and which clampingly draws upper
bracket
968 angularly downwardly against an upper edge of battery 966. Battery cover
970
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generally overlies battery 966 and a major portion of upper bracket 968 and
generally
defines the uppermost portion of the battery enclosure structure.
Starting mechanism 108 further includes ignition switch 961 (FIGURE 4) and a
remotely located starter solenoid, namely solenoid 965 (FIGURE 6), as part of
a suitable
starter switching and activating assembly. Optionally, solenoid 965 is not
remotely
located from starting mechanism 108, rather is integrally housed in the
starter motor
housing.
Mounting plate 110 is connected to a portion of internal combustion engine
105,
e.g. the bottom surface of internal combustion engine 105. The mounting plate
110 is
adapted and configured to mountingly interface with, for example, the upper
surface of
chassis top-plate 7A. Mounting plate 110 and thus prime mover 100 is attached
to
chassis top plate 7A and thus to chassis 7 by various suitable methods of
attachment
and/or joinder. Such suitable methods include, but are not limited to, e.g.
hardware such
as bolt, nuts, screws, rivets, and/or others.
An exemplary suitable prime mover 100 is available under the trade name SNOW
KING ENGINE available from Tecumseh Products Company of Tecumseh, Michigan.
Power transmission assembly 60 includes bracket 70, idler support member 72,
spring 78, idler support bracket 79, idlers 80A, 80B, belt 122,
electromagnetic clutch 130,
input pulley 131, clutched pulley 132, pulley brake 135, and belt 140. The
power
transmission assembly is adapted and configured to transmit power generated by
the
internal combustion to various other components of snow blower 1, namely
transaxle
assembly 10 and auger assembly 300.
Bracket 70 is e.g. a piece of angle-iron or other suitable stock which is
adapted
and configured to pivotably support idler support member 72. A first portion
of bracket 70
is generally parallel to the ground and is attached to the upper surface of
chassis top
plate 7A, distal prime mover 100. The second portion of bracket 70 extends
generally
perpendicularly upwardly from the first bracket portion.
A bore extends through the thickness of the second portion of the bracket, for
example horizontally, adjacent a first end of bracket 70. The horizontally
extending bore
of the first end of bracket 70 houses a pin upon which idler support member 72
is pivotally
attached.
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The second end of bracket 70, namely the end which is proximate prime mover
100, includes an upwardly extending tab, which extends upwardly from the
remainder of
the second, upright, portion of the bracket. The tab includes a bore which
extends
through the thickness thereof. The tab bore is adapted and configured to
securingly
accept an end of spring 78 therethrough.
Idler support member 72 has first and second ends and defines a length
therebetween. A bore extends through thickness of idler support member 72,
adjacent
the first end thereof. The bore of the idler support member first end is
adapted and
configured to securingly accept an end of spring 78 therethrough.
A cylindrical shaft extends generally perpendicularly outwardly from the
second
end of idler support member 72. The cylindrical shaft functions as the axle
shaft upon
which idler 80A is mounted and rotates.
An aperture extends through the thickness of idler support member 72, at a
medial
portion thereof. The medial portion aperture concentrically accepts, or
otherwise is
attached to, the pin which extends from bracket 70, which enables idler
support member
72 to generally pivot about an axis of pivotation defined by the bracket pin.
Spring 78 is a tension spring with first and second arcuate ends. The first
arcuate
end of spring 78 hookingly inserts through the tab bore of the second end of
bracket 70,
whereby the first end of spring 78 is attached to bracket 70. The second
arcuate end of
spring 78 hookingly inserts through the bore of the first end of idler support
member 72,
whereby the second end of spring 78 is attached to idler support member 72.
Since spring 78 is a tension spring, it tends to urge the first end of idler
support
member 72 toward the second end of bracket 70 and thus prime mover 100.
Correspondingly, idler support member 72 tends to urgingly pivot about the
bracket pin,
which arcingly and pivotably moves the second end of idler support member 72,
and the
cylindrical shaft extending therefrom, generally away from prime mover 100.
Spring 78 is selected so that its length, spring rate, and/or other qualities
are
suitable for the intended use, so as to provide the desired magnitude of
biasingly resilient
force upon the pivotable idler support member 72.
Idler support bracket 79 is e.g. a piece of angle-iron or other suitable stock
which is
adapted and configured to rotatably support an idler wheel, namely idler 80B
therein. A
first portion of idler support bracket 79 is generally parallel to the ground
and is attached
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to the lower surface of chassis top plate 7A, distal prime mover 100. The
second portion
of idler support bracket 79 extends generally perpendicularly downwardly from
the first
bracket portion, thus the second portion is generally upright.
A cylindrical shaft extends generally perpendicularly outwardly from the
second,
generally upright, portion of idler support bracket 79. The cylindrical shaft
functions as
the axle shaft upon which idler 80B is mounted and rotates.
Idlers 80A, 80B are adapted and configured to guide and support, for example,
belt
122 and thus to help transmit rotational energy from e.g. prime mover 100 to
input shaft
"I-S" of transaxle assembly 10. Namely idlers 80A, 80B are adapted and
configured to
generally perpendicularly change the direction of travel of belt 122, whereby
belt 122
extends generally vertically upwardly from idlers 80A, 80B and extends
generally
horizontally toward handle 200 from idlers 80A, 80B. In other words, idlers
80A, 80B
enable a single belt to realize both rotational travel along a generally
vertical plane and
rotational travel about a generally horizontal plane, generally perpendicular
thereto.
Each of idlers 80A, 80B defines an outside diameter, an inside diameter, and
an
outer circumferential surface. The inside diameter of ones of idlers 80A, 80B
correspond
to the outside diameter of corresponding ones of the cylindrical shafts of
idler support
member 72 and idler support bracket 79. In other words, idlers 80A and 80B are
rotatably mounted to idler support member 72 and idler support bracket 79,
respectively.
The outside diameters of idlers 80A, 80B are selected so that the idlers
suitably
change the direction of rotational advance of belt 122 while generally
mitigating
undesirable stresses imposed upon the belt, associated with such change in
direction of
advance.
Belt 122 has a cross-sectional profile, and/or other dimensional
characteristics,
which enable it to suitably rotate about pulleys and/or idlers, and change
directions and/or
planes of rotational travel about e.g. idlers 80A, 80B. Belt 122 can be any of
a variety of
suitable b elts a nd/or o ther c ontinuous b ands o f m aterial a dapted and
configured to
transmit power. Such suitable belts include, but are not limited to, various
belts e.g.
polyurethane based belts, neoprene based belts, Kevlar based belts and Kevlar
reinforced belts, polyester based belts, rubber based belts, steel reinforced
belts, cable
reinforced belts, cordedly reinforced belts, and/or others.
Electromagnetic clutch 130 includes an electromagnetic clutch mechanism, input
pulley 131, clutched pulley 132, and pulley brake 135. Electromagnetic clutch
130 is
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electrically selectable, b y a a ser, b etween a n a ngaged c ondition a nd a
d isengaged
condition, whereby the user selects whether or not force is transmitted
through the clutch.
In o ther w ords, a lectromagnetic c lutch 1 30, a lone a nd/or i n c
ombination with other
components of snow blower 1, functions as a power take off (PTO) device. The
PTO
enables the user to selectively transmit power to various components, such as
auger
assembly 300.
Input pulley 131 is attached to, and locked into rotational unison with, the
output
shaft of prime mover 100 and has an outer circumferential surface with is
adapted and
configured to drivingly interface with belt 122.
Preferably, the prime mover output shaft and input pulley 131 are attached to
each
other by means of aligned keyways which extend into the output shaft outer
circumferential surface and the pulley inner circumferential surface, and a
corresponding
key. Optionally, other suitable methods of attachment are utilized, including,
but not
limited to, correspondingly splined surfaces, set screws, and/or others.
Accordingly, when the output shaft of prime mover 100 rotates, input pulley
131
correspondingly rotates. And when input pulley 131 rotates, it generally
drives belt 122
across at least part of the pulley outer circumferential surface, whereby belt
122 is driven
by input pulley 131, traverses one of idlers 80A, 80B, thereby generally
perpendicularly
changing direction of travel, drivingly rotates transaxle pulley 10B,
traverses the other one
of idlers 80A, 80B, and returns to input pulley 131, generally continuously.
In other words, the portion of belt 122 which arcuately extends about the
outer
circumferential surface of idlers 80A, 80B, at any given point in time,
communicates with
about 25% of the outer circumferential surfaces of idlers 80A, 80B. And since
belt 122
extends between pulley 131, which has generally horizontal axis of rotation,
and transaxle
pulley 10B, which has a generally vertical axis of rotation, the belt
generally arcuately
defines about a 90 degree change of direction about the outer circumferential
surfaces of
idlers 80A, 80B.
The outside diameter of input pulley 131 is selected i n c ombination w ith t
he
outside diameter of transaxle pulley 10B to realize a desired overall
rotational speed
reduction or rotational speed increase, between the prime mover output shaft
and
transaxle input shaft "I-S", as desired.
In transmitting power from pulley 131, changing directions about idlers 80A,
80B,
to transaxle pulley 10B, belt 122 is generally maintained in a suitable state
of tension
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and/or tightness by the belt tensioner mechanism defined by bracket 70, idler
support
member 72, and spring 78, in combination. Namely, the spring force provided by
spring
78 biases, by pivoting idler support member 72, idler 80A generally away from
prime
mover 100, which tightens and/or tensions belt 122 which generally prevents
the belt from
non-desired slippage across the surface of e.g. transaxle pulley 10B and/or
input pulley
131.
Input pulley 131 further includes an output shaft which extends into and is
operably
connected to the input mechanism of the electromagnetic clutch mechanism. The
electromagnetic clutch mechanism includes a magnetic coil therein which
engages the
clutch when energized and disengages the clutch when de-energized. The output
device
of the electromagnetic clutch mechanism includes an output shaft which is
attached to
clutched pulley 132.
As desired, a user energizes the electromagnetic clutch mechanism which
engages the clutch and clutchingly couples input pulley 131 to clutched pulley
132. Then
as desired, the user de-energizes the electromagnetic clutch mechanism which
clutchingly disengages input pulley 131 and clutched pulley 132 from each
other.
Clutched pulley 132 has an outer circumferential surface with is adapted and
configured to drivingly convey a belt, e.g. belt 140, across at least a
portion thereof. And
clutched pulley 132 has an outside diameter which is selected, for example, in
combination with corresponding outside diameters of cooperating pulleys and/or
idlers to
realize a desired overall rotational speed reduction and/or rotational speed
increase at the
driven component.
Pulley brake 135 is adapted and configured to mechanically and frictionally
mitigate the rotational travel of clutched pulley 132 e.g. when
electromagnetic clutch 130
is de-energized. In other words, when electromechanical clutch 130 is not
energized,
pulley brake 1 35, o r c omponents t hereof, a ctuate s o a s t o, f or a
xample, f rictionally
interface with the outer circumferential surface, of clutched pulley 132, or a
flange or disc
which is in rotational unison with the clutched pulley. Such frictional
interface is realized
in numerous suitable ways, including but not limited to, pressing, squeezing,
biasing,
and/or otherwise frictionally interfacing. Pulley brake 135 can be a separate,
distinct,
component from other components of the electromagnetic clutch and pulley
assembly,
optionally integral therewith.
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Belt 140 has a cross-sectional profile, and/or other dimensional
characteristics,
which enable it to suitably rotate about pulleys and/or idlers and change
directions and/or
planes of rotational travel. Belt 140 can be any of a variety of suitable
belts and/or other
continuous bands of material adapted and configured to transmit power. Such
suitable
belts include, but are not limited to, various belts e.g. polyurethane based
belts, neoprene
based belts, Kevlar based belts and Kevlar reinforced belts, polyester based
belts, rubber
based b elts, s teel reinforced b elts, c able reinforced belts, cordedly
reinforced belts,
and/or others.
Referring n ow t o F IGURES 2 A a nd 3 , b elt 140 t ransmits t he r otational
force
provided by clutched pulley 132 to force transmission device 290, which in
turn transmits
force to e.g. auger assembly 300.
Force transmission device 290 includes sprocket 321, pulley 351, belt
tensioner
352, sprocket 355, chain 356, sprocket 358, gearbox 360, sprocket 371, chain
382, and
chain slides 390. Sprocket 321 is, for example, a toothed gear or sprocket
which is
operably attached to e.g. rotatable components of auger assembly 300, and is
adapted
and configured to be drivingly rotated by a chain.
Pulley 351 is positioned generally below electromagnetic clutch 130, and
rotates
about an axis of rotation which is generally parallel to the axis of rotation
of input pulley
131 and clutched pulley 132. Pulley 351 has an outer circumferential surface
adapted
and configured to interface with and be driven by belt 140 which is powered by
clutched
pulley 132.
Belt tensioner 352 is attached to a bracket which extends upwardly from the
upper
surface of chassis top wall 7A and includes an idler which is positioned
generally between
clutched pulley 132 and pulley 351. The belt tensioner 352 is adapted and
configured to
communicate with belt 140, whereby belt 140 traverses the outer
circumferential surface
of the idler. Belt tensioner 352 is manually adjustable, optionally
automatically or self
adjusting.
In manually adjustable embodiments of belt tensioner 352, the tensioner
includes,
for example, a mounting plate, an actuating mechanism, and an idler which is
rotatably
mounted to the actuating mechanism. By, for example, rotating a threaded rod
portion of
the actuating mechanism, a user can, as desired, move the idler in at least
first and
second directions, which corresponds to applying relatively more or relatively
less force
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upon belt 140 through the tensioner idler, which corresponds to a relatively
greater belt
tension or a relatively lesser belt tension.
Sprocket 355 is, for example, a toothed gear or sprocket which is operably
attached to pulley 351 and generally transmits power, in combination with a
chain, to
gearbox 360. Namely sprocket 355 is generally coaxially aligned, and locked
into
rotational unison, with pulley 351, whereby rotation of the pulley
correspondingly realizes
a rotation of the sprocket enabling pulley 351 and sprocket 355 to rotate at
the same
speed of rotation.
Chain 356 drivingly and rotatably connects sprocket 355 with gearbox 360. In
other words, the rotational force of sprocket 355 is transmitted to e.g. an
input shaft of
gearbox 360, by way of chain 356.
Sprocket 358 is, for example, a toothed gear or sprocket which is operably
attached to, and rotates in unison with, an input shaft of gearbox 360.
Suitable methods
of a ttaching s procket 3 58 t o the gearbox input shaft include, but are not
limited to,
corresponding keyways and keys, correspondingly splined surfaces, set screws,
and/or
others. The outside diameter of sprocket 358 is selected in light of e.g. the
outside
diameter of sprocket 355, pulley 351, and/or others, to realize a desired
rotational speed
reduction and/or speed increase, whereby the input shaft of gearbox 360
rotates with a
desired rotational speed.
Gearbox 360 includes a gearbox housing, an input shaft, a gear assembly, an
output shaft, and sprocket 371 which is connected to the output shaft. Gearbox
360 is
attached to a generally planar mounting plate which extends generally parallel
to the
ground, and outwardly and back from auger assembly 300 (FIGURE 10).
The gearbox housing is a generally sealed unit, whereby lubricating fluid can
be
generally and suitably retained therein, as desired. The input and output
shafts each
extend outwardly from respective, e.g. sidewalls of the gearbox housing, and
extend
generally perpendicularly to each other. The input shaft is operably coupled
to sprocket
358 and the output shaft is operably coupled to sprocket 371.
The gear assembly of gearbox 360 includes any of a variety of suitable
cooperating gears and corresponding hardware, adapted and configured to
transmit
rotational movement, generally perpendicularly. Exemplary of such suitable
cooperating
gears and corresponding hardware arrangements include, but are not limited to,
ring and
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pinion gear arrangements, corresponding bevel gear arrangements, corresponding
spiral-
cut bevel gear arrangements, corresponding worm gear arrangements, and/or
others.
Sprocket 371 is, for example, a toothed gear or sprocket, attached to the
output
shaft of gearbox 360, and adapted and configured to transmit rotational energy
from the
gearbox output shaft to sprocket 321 which communicates with auger assembly
300.
Suitable methods of attaching sprocket 371 to the gearbox output shaft
include, but are
not limited to, corresponding keyways and keys, correspondingly splined
surfaces, set
screws, and/or others.
The outside diameter of sprocket 371 is selected in light of e.g. the outside
diameter of sprocket 321, to realize a desired rotational speed reduction
and/or speed
increase, whereby rotatable components of auger assembly 300 generally rotate
at a
desired rotational speed.
Chain 382 drivingly and rotatably connects sprocket 321 with sprocket 371 and
thus with gearbox 360. In other words, the rotational energy of the gearbox
output shaft
is transmitted through sprocket 371, through chain 382, to sprocket 321, and
ultimately to
auger assembly 300.
Chain slides 384, 390 are generally cylindrical, preferably polymeric members.
Brackets which extend upwardly from one of, for example, the upper surface of
chassis
top wall 7A or an upper surface of chute assembly 300, provide the mounting
mechanism
through which respective ones of chain slides 384, 390 are attached to the
remainder of
snow blower 1. The outer circumferential surfaces of chain slides 384, 390
interface with
the outwardly facing surfaces of chains 356 and 382, respectively, whereby the
chain
slides 384, 390 generally mitigate any non-desired slack in chains 356, 382
while in
operation.
Preferably, t he b rackets to w hich c hain s tides 3 84, 3 90 a re mounted
include
elongate slots which enable a user to adjust and/or otherwise modify the
respective
positions of chain slides 384, 390 relative to chains 356, 382. In other
words, chain slides
384, 390 are preferably adjustable, whereby a user can e.g. move ones of the
slides
relatively more proximate the respective chain and/or move ones of the slides
relatively
more distal the respective chain, which allows relatively less or more slack
in such chain
and/or chains.
Snow blower 1 preferably includes various shields and/or guards which
generally
encapsulate at least portions of movable chain assemblies, such as various
components
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which cooperate with chain 356 and/or chain 382, and/or other components. Such
shields offer protection to users from certain hazards posed by moving parts
and offer
protection to the moving parts themselves from e.g. environmental exposure.
Exemplary
of such shields are chain back covers 520, 530 chain front covers, 550, 560,
and clutch
cover 570.
Referring now to FIGURE 3, auger assembly 300 includes auger housing 301,
auger shaft 312, auger brackets 315, auger blade 320, sprocket 321, impeller
housing
325, and impeller 350.
Auger housing 301 includes housing top wall 301A, housing back wall 301 B,
housing sidewalls 301 C, 301 D, skids 304, 304, and scraper 310. Auger housing
301 and
the auger generally define a first stage, e.g. the snow collection stage, of
snow blower 1.
Housing top wall 301A is a generally planar sheet, panel and/or plate with an
upper
surface, a lower surface and front and back edges. Top wall 301A generally
defines an
uppermost portion of auger housing 301.
Housing back wall 301 B has, for example, three distinct sections which in
combination define a generally angulated back wall structure, each of which is
a generally
planar sheet, panel and/or plate. The uppermost section of back wall 301 B
intersects
with and is attached to the back edge of housing top wall 301 A, and extends
generally
downwardly and back therefrom. The second section of back wall 301 B extends
downwardly from the first back wall section, generally perpendicular to the
ground. The
third section of back wall 301 B extends generally downwardly and forward of,
e.g.
generally toward the front of snow blower 1, the second back wall portion. I n
other words,
the three sections of back wall 301 B, in combination, define a forward facing
surface
which is generally concave.
Back wall 301 B further includes an opening 302 which extends therethrough,
and
which includes a leading tapered section 303. The opening communicates with
impeller
housing 325, whereby the impeller and auger housings are cooperatively joined.
Housing sidewalls 301 C, 301 D generally define the lateral sides of auger
housing
301. Each of sidewalls 301 C, 301 D is a generally planar sheet, panel and/or
plate, and
each is attached to housing top wall 301 A and back wall 301 B. The sidewalls
301 C,
301 D are positioned generally perpendicular to the ground, and define
inwardly facing
surfaces, which face toward each other. Portions of the perimeter of housing
sidewalls
301 C, 301 D match the profile of the combination of top wall 301 A and back
wall 301 B.
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Accordingly, auger housing 301 defines a partially enclosed structure which is
open at its front-most portion and lower-most portion, enabling the auger to
generally
freely interface the snow while in use. Various surfaces such as the lower
surface of top
wall 301A, the forward facing surface of back wall 301 B, and the inwardly
facing surfaces
of sidewalls 301 C, 301 D, define the outer perimeter of an auger housing
cavity.
Preferably, the auger housing cavity, and thus auger housing 301, houses the
auger and various components of the auger drive mechanism, e.g. sprocket 321,
at least
a portion of chain 382, and/or others, therein. In such embodiments, an
aperture extends
through ones of top wall 301 A and/or back wall 301 B, which enables passage
of chain
382 into and out of the auger housing cavity. As desired, the assemblage of
auger
housing 301 further includes chain guard 510 which generally covers,
envelopes, and/or
otherwise encloses, for example, sprocket 322 and/or the portion of chain 382
which
passes into the auger housing cavity.
Skids 304, 305, and scraper 310 generally protect various portions of auger
housing 301 from excessive wear, such as abrasive wear, gouging wear, cutting
wear,
and/or other wear, during use. Skids 304, 305 are adjustably attached to the
lower, front,
corners of sidewalls 301 D and 301 C, respectively. Thus, skids 304, 305,
generally
interface with the ground or other underlying surface, e.g. concrete or
asphalt surface,
during use, and can be adjusted so that the lower edges of sidewalls 301 C,
301 D are
spaced relatively further from or relatively nearer to such underlying
surface, as desired.
Scraper 310 is a generally elongate, rigid, member which is adjustably
attached to
the lowermost portion of back wall 301 B. Thus, scraper 310 generally
interfaces with the
ground surface during use, and can be adjusted so that the lower edges of back
wall
301 B and/or sidewalls 301 C, 301 D are spaced relatively further from or
relatively nearer
to such underlying surface, as desired.
The auger includes auger shaft 312, auger brackets 315, auger blade 320,
sprocket 321, and flange 322. Auger shaft 312 is an elongate, generally
cylindrical
member which extends across the width of, and generally medially through, the
auger
cavity. In other words, auger shaft 312 extends generally between, and is
rotatably
mounted to, sidewalls 301 C and 301 D. Namely, auger shaft 312 is rotatably
mounted to
the inwardly facing surfaces of sidewalls 301 C, 301 D by way of, for example,
bearings
330 and adapter 331. Bearings 330 are mounted to the first and second ends of
auger
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shaft 312. Adapters 331 housingly capture the bearings and are mounted to
sidewalls
301 C, 301 D, thus rotatably mounting the auger to auger housing 301.
Auger brackets 315 extend radially outwardly from the outer circumferential
surface of auger shaft 312. The auger brackets 315 are radially and axially
spaced from
each other upon the outer circumferential surface of auger shaft 312. The ends
of auger
brackets 315 which are distal auger shaft 312 are connected to auger blade
320.
Auger blade 320 extends generally helically along the length of and radially
spaced
from auger shaft 312. Auger blade 320 is adapted and configured to pull, drag,
scoop,
and/or otherwise draw, snow into the auger housing cavity and move such snow
generally
toward the rearmost portion of the auger cavity. Since the auger drive
mechanism is
adjacent at least one of sidewalls 301 C, 301 D, auger blade 320 helically
extends
generally continuously along a major portion of the length of auger shaft 312,
e.g. along
the full length of the auger shaft as shown, generally without any
discontinuities in the
blade. In other words, auger blade 320 defines a generally continuous cut path
along the
width of the auger housing, without any uncut portion which ordinarily
corresponds to a
discontinuous blade.
Impeller housing 325 and impeller 350 generally define a second stage, e.g. a
snow discharge stage, of snow blower 1. Impeller housing 325 is a generally
cylindrical
tube, having an outer wall. The inner surface of the outer wall generally
defines the outer
perimeter of a cavity, namely an impeller cavity.
The front-most portion of the impeller housing outer wall, namely at tapered
section 3030 of opening 302, is attached to back wall 301 B. From this locus
of joinder
with auger housing 301, the impeller housing outer wall extends toward the
rear of the
snow blower. The outer perimeter defined by the impeller housing outer wall
corresponds
generally in size, shape, and configuration to the outer perimeter defined by
the opening
which extends through auger housing back wall 301 B, whereby the auger cavity
generally
opens into the impeller cavity.
The rearmost portion impeller housing 325 has an opening extending
therethrough,
which permits access to the impeller cavity from e.g. the portion of impeller
housing 325
which is proximate prime mover 100. Cover 500 is removably attached to the
rearmost
portion of impeller housing 325, whereby cover 500 is adapted and configured
to
selectively seal and/or cover the rear opening of the impeller cavity, as
desired by the
user.
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The upper portion of impeller housing 325 includes housing top flange 327.
Housing top flange 327 is generally planar, and has upper and lower surfaces.
An
opening extends generally medially through the thickness of flange 327 and
extends into
the impeller cavity. At lease one bore, preferably at least three, more
preferably at least
four bores, extend vertically through the thickness of flange 327, adjacent
the flange outer
perimeter.
Impeller 350 includes impeller back plate 350A and impeller blades 350B, and
is
adapted a nd c onfigured t o rotate w ithin t he i mpeller c avity a nd t
hrow, p ush, and/or
otherwise propel, snow from the impeller cavity.
Impeller back plate 350A is a generally planar, circular, member which is
positioned generally upright. Back plate 350A has a forward facing surface and
a
rearward facing surface, and a bore which extends generally medially and
axially
therethrough. The forward facing surface of back plate 350A faces the auger
and the
rearward facing surface faces e.g. prime mover 100.
Impeller blades 350B are each a generally rigid member which extends axially
from
the forward facing s urface o f b ack p late 3 50A, a nd c an a xtend r
adially b eyond t he
perimeter of the back plate. Preferably, ones of the ends of blades 350B which
are
proximate the back plate medial bore communicate with and/or are attached to
respective
other ones of the ends of blades 350B, whereby the blades are generally
attached to
each other as well as to the back plate.
Impeller 350 rotates within the impeller cavity through an attachment of the
impeller to, for example, shaft 345 (FIGURE 3) which runs axially through and
is attached
to pulley 351, sprocket 355, and/or otherwise is suitably locked into
rotational unison with
e.g. pulley 351 and/or sprocket 355 (FIGURE 2A).
Shaft 345, is locked in rotational unison with impeller 350, and receives
rotational
energy from pulley 351, sprocket 355, and/or others, directly or indirectly.
Impeller shaft
345, and thus impeller 350 are rotatably mounted to impeller housing 325 by
way of, for
example, bearing housing 340 and bearings 344.
Bearing housing 340 is attached to a rearmost portion of impeller housing 325,
at
bores 353 (FIGURE 6). Bearings 344 are housed in bearing receiving cavities of
bearing
housing 340, on generally opposite axial sides thereof. Impeller shaft 345
operably
extends through bearings 344, thus through bearing housing 340, outwardly
beyond
impeller housing 325, and is cooperatively coupled to a suitable, selectively
rotating,
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component, such as pulley 351, sprocket 355, and/or others, directly or
indirectly, which is
driven by prime mover 100.
Referring now to FIGURES 10 and 11, discharge chute assembly 391, includes
cable 240, chute lower member 392, chute rotation body 392A, chute lower
flange 392B,
chute upper flange 392C, chute upper member 400, transition member 401,
discharge
deflector 410, and idlers 421.
Chute lower member 392 includes chute rotation body 392A, chute lower flange
392B, and chute upper flange 392C. Chute rotation body 392A is a generally
cylindrical
structure with a generally continuous, annular, outer wall. A vertically
extending bore
extends axially through the chute rotation body and extends into and
communicates with
the impeller cavity.
Chute lower flange 392B is generally annular, has an upper surface, a lower
surface, and extends radially outwardly from the lower end surface of chute
rotation body
392A. Lower flange 392B extends along a major portion, optionally the
entirety, of the
outer circumferential surface of chute rotation body 302A.
Chute upper flange 392C has an upper surface, a lower surface, and extends
radially outwardly from the upper end surface of chute rotation body 392A.
Upper flange
392C extends along a major portion, optionally the entirety, of the outer
circumferential
surface of chute rotation body 302A. Upper flange 392C further includes a
plurality of
bores which extend through the thickness thereof and are adapted and
configured to
enable chute upper member 400 to mount thereto.
Chute upper member 400 is attached to upper flange 392C by way of the flange
bores and corresponding hardware, and has a back wall and two sidewalls. The
upper
member back wall extends upwardly and angularly from upper flange 392C and has
first
and second lateral edges. The upper member sidewalls extend from respective
ones of
the first and second back wall lateral edges, whereby the entire assemblage of
chute
upper member 400 generally defines a 3-sided, generally upright, trough.
Transition member 401 is an elongate, generally rectangular member which
extends across generally the entire width of, and is attached to, the
uppermost portion of
the chute upper member back wall. A plurality of rivets 403 attach transition
member 401
to the upper portion of chute upper member 400. Preferably, transition member
401 is
made from a deflectable, resilient, and/or otherwise bendable, material.
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Discharge deflector 410 is pivotably attached to the upper portion of chute
upper
member 400, has a back wall, and first and second sidewalls. Each of the
sidewalls of
discharge deflector 410 is pivotably attached to an upper portion of a
corresponding
sidewall of chute upper member 400.
Knob 418 is a securing structure with e.g. a threaded stem portion and a
handle
portion. By way of the threaded stem portion, or otherwise, knob 418 is
adapted and
configured to generally lock discharge deflector 410 in place, when in a
tightened state,
and generally permit discharge deflector 410 to pivot, when in a loosened
state.
Accordingly, a user uses knob 418 and discharge deflector 410 to generally
direct the
vertical angle component at which snow is discharged from discharge chute
assembly
391.
Idlers 421 are adapted and configured to guide and support, for example,
discharge chute assembly 391. Namely, idlers 421 generally support and guide
chute
rotation body 302A, enabling the rotation body to rotate, through an e.g.
rotatably rolling,
sliding, gliding, and/or other suitable interfacing relationship between the
rotation body of
lower flange 392B of lower chute 392, and the idlers.
Each of idlers 421 is generally cylindrical, in other words a wheel type
structure,
which is positioned with the circular surfaces facing generally upwardly and
downwardly,
whereby each idler 421 is adapted and configured to rotate about a generally
vertical axis
of rotation.
The outer circumferential surface of each idler 421 has a groove, channel,
and/or
other depression, extending thereinto. Namely, groove 422 extends into the
outer
circumferential surface of ones of idlers 421. In some embodiments, groove 422
extends
along a minor portion of the outer circumferential surface of idler 421. In
some
embodiments, groove 422 extends along a major portion of the outer
circumferential
surface of idler421. In some embodiments, groove 422 extends along the
entirety of the
outer circumferential surface of idler 421. In some embodiments, ones of
idlers 421
include a plurality of grooves extending into the respective outer
circumferential surfaces
of each idler. Ones of the grooves 422 are generally parallel, optionally
generally not
parallel, to other ones of the grooves on any particular idler 421.
The outside diameter of each idler 421, and the depth, width, profile,
contour,
and/or other characteristics of groove 422 are selected so that sufficient
surface area of
various portions of idlers 421 interface with corresponding portions of e.g.
chute lower
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flange 392B, to yield the desired result and functionality. Accordingly,
groove 422 defines
a groove width which is greater in magnitude than the magnitude of the
thickness
dimension of chute lower flange 392B. And groove 422 defines a depth dimension
having a magnitude that corresponds to the magnitude of the distance from
which lower
flange 392B radially extends from chute rotation body 392A.
Regardless, idlers 421 generally rotationally capture chute lower member 392,
whereby the chute lower member is generally free to rotate with respect to
e.g. impeller
housing 325, as desired. Also, idlers 421 interface with chute lower member
392 so as to
retain a sufficiently close distance relationship between the lower surface of
chute lower
flange 392B and the upper surface of impeller housing top flange 327, thereby
suitably
mitigating the amount of non-desired snow escape between the impeller housing
and the
discharge chute assembly during use.
Specifically, ones of idlers 421 are mounted, rotatably, optionally fixedly,
to the
impeller housing top flange 327 (FIGURE 11 ), by way of the bores which extend
through
top flange 327. Grooves 422 on respective idlers 421 are generally coplanar
with respect
to each other.
Idlers 421 are made from any of a variety of suitable, preferably polymeric,
materials. Preferably, idlers 421 are made from nylon or a blended nylon
material, which
enables portions of discharge chute assembly 391 to pivot, rotate, and or
otherwise
move, for example smoothly, within the movement boundary generally defined by
the
idlers.
Lower flange 3928 is housed generally concentrically within an imaginary
circle
defined arcuately connecting the idlers. The flange 392B is generally captured
in a
portion of each of the grooves 422, in each of the idlers 411.
The upwardly facing surface of the annular projection generally at the bottom
of
422 generally provides load bearing support to discharge chute assembly 391,
generally
supporting the chute assembly 391 from impeller housing 325.
The downwardly facing surface of groove 422 generally provides a vertical
retaining functionality to discharge chute assembly 391. Thus, the downwardly
facing
surface of the groove 422 generally resists forces which tend to urge removal
of the chute
assembly 391, upwardly away from impeller housing 325.
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The portion of an idler 421 which is laterally adjacent the inwardly extending
most
portion of groove 422 generally provides lateral retaining functionality to
discharge chute
assembly 391. Thus, the portion of idler 421 which is laterally adjacent the
inwardly
extending most portion of groove 422 at least partially resists forces with
tend to urge
lateral removal of chute assembly 391 from impeller housing 325.
Spacers 424 are insertably housed in the inner bores of idlers 422. Spacers
424
enable idlers 421 to rotate upon and around, for example, mounting bolts which
extend
axially therethrough. In addition, spacers 424 are sufficiently durable,
tough, hard, and/or
resilient enabling the spacers to generally reduce the likelihood that idlers
421 will be
damaged during installation by, e.g. axially crushing and/or otherwise
damaging the idlers
by over-tightening of the idler mounting bolts. Spacers 424 can include a
variety of
suitable structures, including, but not limited to, various spacers, sleeves,
collars,
bearings, bearing assemblies, and/or others.
Preferably idlers 421 are rotatably mounted to impeller housing 325, whereby
the
idlers and chute rotation body rotate during rotation of discharge chute
assembly 391.
However, idlers 421 can remain static as long as the coefficient of friction
realized
between chute lower flange 3928 and idlers 421 is sufficiently low to enable
the flange to
suitably slide across the idlers.
To rotate chute assembly 391, a user applies a force to cable 240. Cable 240
includes f first c able s egment 2 40A a nd s econd c able s egment 2 408.
Cable 240 is
elongate, generally flexible, and includes any of a variety of suitable
structures which
include, but are not limited to, various cables, ropes, bands, and/or other
generally flexible
elongate and generally non-extensible members.
First and second cable segments 240A, 2408 extend around at least a portion of
the outer circumferential surface of chute rotation body 3928, in respectively
opposite
directions. Namely, first and second cable segments 240A, 2408 extend, in
different
directions, about rotation body 392A and are each attached to the rotation
body wall,
optionally at a generally common locus.
Accordingly when a force is applied to first cable segment 240A, urging the
cable
segment in a direction generally away from rotation body 392A, the force is
transferred
through cable segment 240A, to the point of attachment of the cable to the
rotation body,
whereby the rotation body correspondingly rotates. In other words, as a
portion of first
cable segment 240A is pulled away from the rotation body, a portion of second
cable
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segment 240B is pulled toward the rotation body, whereby relatively less of
first cable
segment 240A interfaces with and lies upon rotation body 392A and relatively
more of
second cable segment 240B interfaces with and lies upon rotation body 392A.
Namely, a
portion of first cable segment 240A is unwound from rotation body 392A and
second
cable segment 2408 is wound upon the rotation body.
When a force is applied to second cable segment 240B, in a direction generally
away from rotation body 392A, the force is transferred through cable segment
240B, to
the point of attachment of the cable to the rotation body, whereby the
rotation body
correspondingly rotates. In other words, as a portion of second cable segment
240B is
pulled from the rotation body, a portion of the first cable segment 240A is
pulled toward
the rotation body, whereby relatively less of second cable segment 240B
interfaces with
and lies upon rotation body 392A and relatively more of first cable segment
240A
interfaces with and lies upon rotation body 392A. Namely, a portion of second
cable
segment 240B is unwound from rotation body 392A and an additional portion of
first cable
segment 240A is wound upon the rotation body.
Regarding various user control mechanisms, and referring now to FIGURES 4 and
5, handle assembly 200 includes handle arms 201A, 202A, handle arm angled
portions
201 B, 202B, handle mounting plates 201 C, 202C, handle cross member 203A,
panel
mounting bracket 203B, and panel assembly 590. Handle assembly 200 functions
as a
lever arm, which enables a user to control snow blower 1 by way of e.g.
pushing, pulling,
pivoting, and/or otherwise moving the snow blower.
***Handle arm 201A is an elongate, generally rigid member which alone and/or
in
combination with other components provides mounting structure to which e.g.
handle
cross member 203A, panel mounting bracket 203B, and panel assembly 590 are
mounted. As illustrated, handle arm 201A is an elongate piece of C-channel
metal stock,
although other suitable materials and configurations are considered and well
within the
scope of the invention. Such other suitable materials and configurations
include, but are
not limited to, various configurations of metal tubing, angle iron, I-beam,
and/or other
metallic or nonmetallic stock.
A first end of handle arm 201A is relatively distal running gear 5 and a
second,
opposite, end of handle arm 201 A is relatively proximate running gear 5. The
second end
of handle arm 201 A generally defines a beveled surface, as viewed from above,
which is
adapted and configured to interface with handle arm angled portion 201 B.
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Handle arm angled portion 201 B is an elongate, generally rigid member which
has
a shorter length than, and is made from e.g. generally the same material as,
handle arm
201A. Angled portion 201 B has first and second ends, each of which defines a
beveled
terminal surface.
The uppermost end of angled portion 201 B, and its beveled surface, interfaces
with the beveled surface of the lowermost end of handle arm 201A. As desired,
handle
arm 201A and angled portion 201B are welded to each other, optionally
integral,
optionally otherwise suitably joined or communicating with each other. In the
complete
assemblage of handle assembly 200, angled portion 201 B extends from handle
arm 201 A
inwardly toward, for example, chassis 7 and handle mounting plate 201 C.
Handle mounting plate 201C is a generally planar member which has an inwardly
facing surface which faces toward e.g. chassis 7 and an outwardly facing
surface which
faces a generally opposite direction. Handle arm angled portion 201 B is
connected to the
outwardly facing surface of mounting plate 201 C. The inwardly facing surface
of
mounting plate 201 C interfaces with an outwardly facing surface of chassis
frame rail 7G
(FIGURE 4). Mounting plate 201 C is attached to the frame rail 7G by way of,
for
example, coaxially aligned bores on the frame rail 7G and mounting plate 201 C
and
suitable hardware which extends through such aligned bores, including various
bolts,
rivets, screws, and/or others.
Like handle arm 201A, handle arm 202A is an elongate, generally rigid member
which alone and/or in combination with other components provides mounting
structure to
which e.g. handle cross member 203A, panel mounting bracket 203B, and panel
assembly 590 are mounted. As illustrated, handle arm 202A is an elongate piece
of C-
channel metal stock, although other suitable materials and configurations are
considered
and well within the scope of the invention. Such other suitable materials and
configurations include, but are not limited to, various configurations of
metal tubing, angle
iron, I-beam, and/or other metallic or nonmetallic stock.
A first end of handle arm 202A is relatively distal running gear 5 and a
second,
opposite, end of handle arm 202A is relatively proximate running gear 5. The
second end
of handle arm 202A generally defines a beveled surface, as viewed from above,
which is
adapted and configured to interface with handle arm angled portion 202B.
Handle arm angled portion 202B is an elongate, generally rigid member which
has
a shorter length than, and is made from e.g. generally the same material as,
handle arm
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202A. Angled portion 2028 has first and second ends, each of which defines a
beveled
terminal surface.
The uppermost end of angled portion 202B, and its beveled surface, interfaces
with the beveled surface of the lowermost end of handle arm 202A. As desired,
handle
arm 202A and angled portion 202B are welded to each other, optionally
integral,
optionally otherwise suitably joined or communicating with each other. In the
complete
assemblage of handle assembly 200, angled portion 202B extends from handle arm
202A
inwardly toward, for example, chassis 7 and handle mounting plate 202C.
Handle mounting plate 202C is a generally planar member which has an inwardly
facing surface which faces toward e.g. chassis 7 and an outwardly facing
surface which
faces a generally opposite direction. Handle arm angled portion 202B is
connected to the
outwardly facing surface of mounting plate 202C. The inwardly facing surface
of
mounting plate 202C interfaces with an outwardly facing surface of chassis
frame rail 7F
(FIGURE 4). Mounting plate 202C is attached to the frame rail 7F by way of,
for example,
coaxially a ligned b ores o n t he f rame r ail 7 F a nd m ounting p late 2
02C a nd suitable
hardware w hick a xtends t hrough s uch a ligned b ores, i ncluding v arious b
olts, r ivets,
screws, and/or others.
Thus, handle assembly 200 is operatively attached to e.g. running gear 5
though
the attachment of handle mounting plates 201 C, 202C and chassis frame rails
7G, 7F,
respectively.
Handle cross member 203A extends generally perpendicularly between, and is
attached to, the uppermost ends of handle arms 201 A and 202A. Handle cross
member
203A is attached to handle arms 201A, 202A by way of, for example, but not
limited to,
screws, bolts and nuts, rivets, weldments, and/or others.
Handle cross member203A has a generally straight-line, linear, medial portion
and
first and second generally arcuate ends. The first and second ends arcuately
span
approximately 90 degrees, whereby the ends arcingly transition from the handle
arms
201A, 202A, to the medial portion of cross member 203A.
Preferably, handle cross member 203A has an outer circumferential surface
which
is relatively comfortably for a user to grasp. In other words, handle cross
member 203A is
preferably devoid of any generally sharp angles and/or protuberances which
might prove
uncomfortable during normal use. Accordingly, handle cross member 203A has an
e.g.
generally cylindrical outer circumferential surface, and/or other suitably
outer surface.
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Panel mounting bracket 2038 is an elongate member which extends between
handle arms 201A, 202A, generally parallel to the medial portion of handle
cross member
203A. Panel mounting bracket 2038 is e.g. a piece of angle-iron type stock
material,
which has first and second elongate portions, generally perpendicular to each
other.
In the complete assembly of handle assembly 200, one of the first and second
elongate portions of panel mounting bracket 2038 extends along a plane which
is
generally parallel the plane defined by the two out-jutting, C-channel,
portions of handle
arms 201A, 202A. The other one of the first and second elongate portions of
panel
mounting bracket 2038 is generally perpendicular thereto, thus extends
generally
perpendicularly between the two out-jutting, C-channel, portions of handle
arms 201A,
202A.
Panel mounting bracket 2038, as desired, has various apertures, bores, slots,
and/or other structures or voids, which enable various components of e.g. user
input
assembly 208 to be mounted thereto.
User input assembly 208 includes drive handlebar 210, power take off (PTO)
bail
211, pins 216, drive control draw rod 220, lower draw rod 221, pivotable
bracket 260,
spring 261, panel assembly 590, power take off safety switch 964A, neutral
safety switch
9648, solenoid 965, draw rod guide-plate 982, and neutral safety switch ramp-
plate 984.
Drive handlebar 210 is a generally U-shaped, preferably tubular, member, and
is
pivotably connected adjacent the upper ends of handle arms 201A, 202A.
A first bore extends through each of the generally planar portions or mounting
tabs,
of t he f first a nd second handlebar ends, generally coaxially with each
other. In the
complete assemblage of handle assembly 200, the first bore of the first and
second
handle bar ends generally define the point of pivotation from which the drive
handlebar
210 pivots.
A second bore extends through the generally planar portion or mounting tab of
the
handlebar end which is proximate handle arm 201A. This second bore is adapted
and
configured to operably connect, by way of, for example other components, drive
handlebar 210 t o t ransaxle a ssembly 1 0. I n s ome a mbodiments, t his s
econd b ore
extends through a separate component, such as a pivotable bracket, which is
operatively
connected, for example, by way of keys and corresponding keyways,
corresponding
splines, setscrews, and/or otherwise, to drive handlebar 210.
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The outer circumferential surface of is relatively comfortably for a user to
grasp.
Thus, drive handlebar 210 is preferably devoid of any generally sharp angles
and/or
protuberances which might prove uncomfortable during normal use.
In addition to the configuration of the outer circumferential surface, drive
handlebar
210 has a suitable overall shape, profile, and/or other characteristics,
whereby the drive
handlebar 210 is generally ergonomically acceptable to the user. Accordingly,
handle
cross member 203A has an e.g. generally cylindrical outer circumferential
surface, other
suitably outer surface, and/or is generally U-shaped, V-shaped, split U-
shaped, split V-
shaped, or otherwise suitably shaped to enable a user to enjoy a relatively
comfortable
arm and hand position, as well as gate, while using snow blower 1 e.g. while
pushing,
pulling, and/or otherwise manipulating drive handlebar 210.
***PTO safety bail 211 is a generally U-shaped member and a generally straight-
line linear, lower cross member. The lower cross member has relatively tightly
radiused
arcuate ends, which extend between and connect the two ends of the lower cross
member to the U-shaped member of bail 211. The terminal most portion of each
end of
PTO bail 211 includes a bore which extends therethrough. The bores of the ends
of PTO
bail 211 generally define a point of pivotation, whereby safety bail 211 is
pivotably
attached to handle arms 201A, 202A.
Accordingly, both the U-shaped member and the lower cross member pivot about
a point of pivotation defined by the PTO bail end bores. Since the U-shaped
member
extends relatively further from the end bores as compared to the lower cross
member, the
lower cross member travels relatively less linear distance as compared to the
U-shaped
member, for any given pivotation of PTO bail 211 about the end bores.
Referring specifically to FIGURE 5, in the complete assemblage of user input
assembly 208, the bores of PTO bail 211 and the first bores of drive handlebar
210 are
generally coaxially aligned with each other. Thus, drive handlebar 210 and the
U-shaped
member of PTO bail 211 generally pivot about the same points of pivotation.
Also, drive
handlebar 210 and the U-shaped member of PTO bail 211 define a generally
similar U-
shaped profile which enables the handlebar and PTO bail to pivotably move in
unison
with each other. In other words, a user can grasp both drive handlebar210 and
PTO bail
211 simultaneously in a given hand and correspondingly and conveniently
manipulate the
handlebar and bail simultaneously with the same hand. Accordingly, drive
handlebar 210
and PTO bail 211, in combination, define a pivotable user control device, e.g.
an infinitely
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variable push and go and/or pull and go device which is generally
ergonomically
acceptable to the user.
Each of pins 216 pivotably attaches a respective end of handlebar 210 and PTO
bail 211 to the corresponding ones of handle arms 201A, 202A. Each pin 216 is
elongate, has a bore which extends axially therethrough, and has a first
portion and a
second portion. The first portion of pin 216 defines a multiple sided outer
surface and an
end surface. As one example, the end surface of the first portion appears
hexagonal
when viewed in elevation and the outer surface includes six elongate flat
surfaces
intersecting each other at respective ends.
The second portion of pin 216 has a generally round end surface of relatively
lesser diameter than the width of the first portion. In other words, the
second portion
extends axially from the first portion, is generally cylindrical, and thus
defines a generally
smooth outer circumferential surface. Pin 216 includes a shoulder which steps
down the
pin diameter from the first portion to the second portion. In other words, pin
216 includes,
but is not limited to, various suitable hexagonal standoffs and/or spacers.
One pin 216 extends outwardly from the inwardly facing surface of handle arm
201 A, w ith t he a nd s urface o f the first pin portion interfacing with
such handle arm
inwardly facing surface. A second pin 216 extends outwardly from the inwardly
facing
surface of handle arm 202A, with the end surface of the first pin portion
interfacing with
such handle arm inwardly facing surface.
As desired, pins 216 can further include spacers 217. Each spacer 217 is a
generally cylindrical member and is adapted and configured to e.g. slidingly,
rollingly,
press-fittingly, and/or otherwise, be concentrically housed within the bores
of ones of
handlebar 210 and/or PTO bail 211 and thus relatively reduces the amount of
friction
between respective ones of handlebar 210, PTO bail 211, and pins 216.
Drive control draw rod 220 is an elongate, generally rigid member with an
upper
end and a lower end. The upper end of drive control draw rod 220 includes a
projection
which extends generally perpendicularly from the remainder of the draw rod
220. The
projection of the draw rod upper end is insertably and rotatably housed in a
second bore
which extends through the generally planar portion or mounting tab of the end
of
handlebar 210, adjacent handle arm 201A. Namely, the connection between
handlebar
210 and drive control draw rod 220 enables motion e.g. pivotable motion of the
handlebar
to translate to a corresponding generally linear motion of draw rod 220.
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The lower end of drive control draw rod 220 includes, for example, a threaded
portion and an adjustment mechanism 224 threaded thereupon (FIGURE 2A). The
adjustment mechanism is adapted and configured to enable a user to adjust the
overall
length dimension of the assemblage of drive control draw rod 220 and lower
draw rod
221. Non-limiting examples of such suitable adjustment mechanisms include, but
are not
limited to, hexagonal spacers with two female ends, threaded rod couplers,
and/or other
suitable hardware, adapted and configured to e.g. threadedly draw drive
control rod 220
and lower draw rod 221 relatively nearer to each other and/or to threadedly
push drive
control rod 220 and lower draw rod 221 relatively further from each other.
Lower draw rod 221 is an elongate, generally rigid member with an upper end
and
a lower end, and is relatively shorter than drive control draw rod 220. The
upper end of
lower draw rod 221 includes a threaded portion thereof which threadedly and
adjustably
interfaces with the adjustment mechanism and therefore with drive control draw
rod 220.
The lower end of lower draw rod 221 includes a projection which extends
generally
perpendicularly from the remainder of the draw rod 221. The projection of the
lower draw
rod upper end is insertably and rotatably housed in an aperture which extends
through
input bracket 30C (FIGURE 2A). Namely, the rotatable connection between the
bracket
and lower draw rod 221 enables motion e.g. linear motion of draw rod 221 to
translate to
a corresponding generally pivotal motion of input bracket 30C, thus pivotal
motion of input
arm 30B and input control shaft 30A.
Referring now to FIGURES 2A, 4, and 5, various components of user input
assembly 208, namely drive handlebar 210, pins 216, drive control draw rod
220, lower
draw rod 221, and/or others, enable a userto adaptively, with infinite
variation in machine
output, and within certain predetermined parameters e.g. maximum speed,
control the
speed and travel direction of snow blower 1 along the ground or other
underlying surface.
In other words, as desired, a user applies an input force such as a push or
pull to
drive handlebar 210 which correspondingly pivots about pins 216. This pivotal
motion is
translated into a generally linear motion through a linkage defined by drive
control draw
rod 220 and lower draw rod 221. The linear motion of drive control draw rod
220 and
lower draw rod 221 is translated to another pivotal motion at the c ontrol p
ortion o f
transaxle assembly 10, namely input control shaft 30A, which correspondingly
influences
the mechanical output of transaxle assembly 10.
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Accordingly, when a user presses forward on drive handlebar 210, from a
neutral
rest position, snow blower 1 advances, thus travels forward. When a user pulls
back on
drive handlebar 210, snow blower 1 regresses, thus travels backward. The
magnitude of
the realized speed of snow blower 1 corresponds to the magnitude with which
the user
presses or pulls drive handlebar 210, forward or backward respectively, and
wherein
there are substantially no step changes between speeds, rather the speed of
snow blower
1 is continuously variable according to the continuous variation in distance
by which
handlebar 210 can be moved.
A user rotates chute rotation body 392A and thus discharge chute assembly 391,
by, for example, rotating chute rotation handle 230. Chute rotation handle 230
includes a
handle body, and a grip assembly.
The chute rotation handle body is generally L-shaped, has a first elongate
member
and a second member which extends generally perpendicularly from an end of the
first.
The second member extends though a bore which extends through handle arm 202A,
axially through generally annular spacer 231, axially through bushing 232, and
is locked
into rotational unison with idler 233. Thus, rotation of chute rotation handle
230 realizes a
corresponding rotation of idler 233.
Chute rotation handle 230 further includes a handle assembly which generally
lies
laterally outside of handle arm 202A. The handle assembly including first and
second
grip members 236, 239, and bolt 237. Bolt 237 extends axially though grip
member 236
and rotatably mounts grip member 236 to the end of the handle body first
member, distal
the handle body second member. Second grip member 239 sleevingly inserts over
and
generally encapsulates first grip member 236 and bolt 237. Accordingly, to
rotate handle
member 230 and idler 233, a user grips and rotates the handle assembly of e.g.
grip
members 236, 237.
Idler 233 is adapted and configured to windingly store portions of cable 240
thereupon, and generally lies laterally inside of handle arm 202A. Namely,
first and
second cable segments 240A, 240B are wound upon idler 233 in opposite
directions of
winding. Thus, when first cable segment 240A is relatively further wound upon
idler 233,
relatively more of second cable segment 240B is unwound therefrom.
Accordingly,
generally the same magnitude of length of cable is always wound upon idler
233, but the
relative amounts of each cable segment wound thereupon changes, as desired by
a user,
through the rotational manipulation of chute rotation handle 230 by the user.
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Cable 240 extends between idler 233 and discharge chute assembly 391, and
along the length of the cable, passes over, and generally changes direction of
extension
over, idler 250. Spacer 251 is concentrically housed in idler 250. Idler 250
and spacer
251 are rotatably mounted, optionally fixedly mounted, to and laterally inside
of handle
arm 202A.
Thus, cable 240 extends in a first direction of extension to idler 250. Cable
240
wraps around a portion of the outer circumferential surface of idler 250, and
continues to
extend along a second direction of extension, generally perpendicularly toward
chute
rotation body 392A, and is attached thereto as previously described.
Accordingly, to rotate discharge chute assembly 391 in a first direction, the
user
rotates chute rotation handle 230 in a first direction, which rotates idler
233 in a first
direction. Upon so doing, relatively more of first cable segment 240A is wound
upon idler
233 and relatively more of second cable segment 240B is unwound therefrom.
Correspondingly, some of first cable segment 240A unwinds from rotation body
392A and
some of second cable segment 240B winds further upon the rotation body, which
rotates
chute assembly 391 in the first direction.
Then to rotate discharge chute assembly 391 in a second, opposite direction,
the
user rotates chute rotation handle 230 in a second, opposite, direction, which
rotates idler
233 in a second, opposite, direction. Upon so doing, relatively more of second
cable
segment 240B is wound upon idler 233 and relatively more of first cable
segment 240A is
unwound therefrom. Correspondingly, some of second cable segment 240B unwinds
from rotation body 392A and some of first cable segment 240A winds further
upon the
rotation body, which rotates chute assembly 391 in the second direction.
Snow blower 1 preferably includes various safety mechanisms, namely various
electronically switchable safety mechanisms. Components of these
electronically
switchable safety mechanisms include, pivot bracket 260, spring 261, PTO
safety switch
964A, neutral safety switch 964B, switch extension 964C, draw rod guide-plate
982,
neutral switch ramp-plate 984.
These safety mechanisms are adapted and configured to, for example, disable
various components of snow blower 1 upon an open circuit condition within the
electric
circuit of the corresponding device. Specifically, certain switches in the
electrical system
must be actuated, so as to c lose t he c orresponding c ircuit, i n o rder f
or a .g. s tarter
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mechanism 108 to operate and thus start the internal combustion engine, to
enable the
PTO system to operate, and/or others.
Referring now to FIGURES 4 and 5, pivot bracket 260 has first and second ends,
an upper surface and a lower surface. The upper surface of pivot bracket faces
toward
panel mounting bracket 203B and operably interfaces PTO safety switch 964A.
The first end of pivot bracket 260 includes a tab or other protuberance which
extends outwardly therefrom. This tab is captured in and rockingly housed in
an aperture
which extends through panel mounting bracket 203B. Thus, through the
communication
between the first end tab and the panel mounting bracket 203B, pivot bracket
260 is
pivotally attached to panel mounting bracket 203B.
The second end of pivot bracket 260 is distal handle arm 202A and has a bore
extending therethrough. T he s econd a nd b ore o f t he p ivot b racket i s a
dapted a nd
configured to attach an end of spring 261 to pivot bracket 260.
Spring 261 extends between and connects pivot bracket 260 and the lower cross
member of PTO bail 211. The first end of spring 261 extends through the second
end
bore of pivot bracket 260. The second end of spring 261 wraps at least
partially around
the circumference of, and is captured by, a circumferential groove which
extends into and
about the outer circumferential surface of the lower cross member of PTO bail
211.
Accordingly, when the U-shaped member of PTO bail 211 is pivoted forward and
down, the bail lower cross member is relatively nearer pivot bracket 260,
whereby spring
261 is generallylin a relaxed, resting, state and pivot bracket 260 is pivoted
outwardly
away from panel mounting bracket 203A. When the U-shaped member of PTO bail
211
is pivoted upwardly and back, the bail lower cross member is relatively
further from pivot
bracket 260, whereby spring 261 is generally extended and in a state of
tension. The
tensile force of spring 261 is transmitted to pivot bracket 260 which biases
the bracket
260 toward panel mounting bracket 203A, which communicates with PTO safety
switch
964A.
PTO safety switch 964A is preferably a plunger-type switch. In other words,
PTO
safety switch 964A includes a switch body that houses the switching mechanism
and a
plunger which extends outwardly from the switch body and functions as the
actuation
mechanism of the switch, and with biases between a first position and a second
position.
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In the first position, the plunger is depressed inwardly toward, at least
partially into,
the switch body, whereby the switch is closed and the PTO system can freely
operate, if
the remainder of the circuit is also closed. In the second position, the
plunger is biased
outwardly, extending at least partially from the switch body, whereby the
switch is open
and the PTO system will not operate. In other words, when the remainder of the
PTO
electrical circuit is closed, if a user desired to use the PTO system and thus
auger
assembly 300, the user must pivot the PTO bail upwardly and back to depress
the
plunger of PTO safety switch 964A by way of pivot bracket 260 and spring 261.
Neutral safety switch 9648 is preferably a plunger-type switch which
electrically
communicates with the electric starter circuit. Namely, neutral safety switch
964 includes
a switch body that houses the switching mechanism and a plunger which extends
outwardly from the switch body and functions as the actuation mechanism of the
switch
and with biases between a first position and a second position.
In the first position, the plunger is depressed inwardly toward, at least
partially into,
the switch body, whereby the switch is closed and the starter motor can be
energized, if
the remainder of the circuit is also closed. In the second position, the
plunger is biased
outwardly, extending at least partially from the switch body, whereby the
switch is open
and the starter motor can not be energized. In other words, when the remainder
of the
electrical starting m echanism c ircuit i s c losed, i f a a ser d esired t o
s tart t he i nternal
combustion engine, the user must ensure that the plunger of neutral safety
switch 9648 is
depressed.
The plunger of neutral safety switch 9648 is depressed when various
cooperating
components are suitably aligned therewith. Namely, the plunger of neutral
safety switch
9648 is depressed when various ones of switch extension 964C, draw rod guide-
plate
982, and neutral switch ramp-plate 984 are suitably positioned with other ones
of switch
extension 964C, draw rod guide-plate 982, neutral switch ramp-plate 984, and
neutral
safety switch 9648.
Switch extension 964C is a generally rigid, cylindrical member which is
coaxially
aligned with and connected to the plunger of neutral safety switch 9648.
Switch
extension 964C has a first end which interfaces with the safety switch and a
second end
which defines a generally conical, optionally hemispherical, optionally
otherwise tapering,
terminal end portion. Switch extension 964C is adapted and configured to
transmit forces
therethrough, and to the plunger of neutral safety switch 9648. In other
words, switch
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extension 964C effectively generally elongates the operable length of the
safety switch
plunger.
Draw rod guide-plate 982 is, for example, an angle bracket which slidingly
communicates with drive control upper draw rod 220. A first portion of draw
rod guide-
s plate 982 interfaces with and is connected to the lower surface of panel
mounting bracket
203B. A second portion of draw rod guide-plate 982 extends perpendicularly
away from
the first guide-plate portion and has an inwardly facing surface and an
outwardly facing
surface.
The inwardly facing surface of guide-plate 982 slidingly interfaces with a
portion of
the outer circumferential surface of upper draw rod 220, which generally faces
handle
arm 201 A. Thus, draw rod guide-plate 982 offers lateral support to upper draw
rod 220,
generally mitigating non-desired lateral movement thereof, in the direction
toward handle
arm 201 A.
Neutral switch ramp-plate 984 has first and second end portions, and a medial
portion, and is connected to the outer surface of upper draw rod 220, by way
of e.g.
weldments, mechanical fasteners, adhesive, and/or otherwise. The first and
second ends
of neutral switch ramp-plate 984 are generally planar and generally coplanar
with each
other. The lower surfaces of the ramp-plate first and second ends interface
with a portion
of the outer circumferential surface of upper draw rod 220, which generally
faces handle
arm 202A.
The medial potion of neutral ramp-plate 984 defines two generally ramped
surfaces. The ramped surfaces each originates at a respective point of
intersection with
ones of the ramp-plate first and second ends. From the respective points of
intersection,
each of the ramped surfaces generally angularly extends outwardly from the
respective
point of intersection with ones of the ramp-plate first and second ends,
toward each other,
and terminate at a locus of joinder between the ramped surfaces. Thus, the
surface of
neutral ramp-plate 984 from which the medial portion extends generally defines
a convex
outer surface.
Accordingly, in the complete assemblage, the first and second ends of neutral
ramp-plate 984 are attached to upper draw rod 220 and the medial portion of
the ramp-
plate extends outwardly from upper draw rod 220, toward handle arm 202A. And
since
neutral ramp-plate 984 is attached to upper draw rod 220, the ramp-plated
travels in
unison with the draw rod, w hereby a ser i nput to h andlebar 210 w hich t
ranslates t o
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generally linear motion of upper draw rod 220 correspondingly translates to
generally
linear motion of neutral ramp-plate 984.
The second, generally tapered, end portion of switch extension 964C slidably
interfaces with the convex outer surface of neutral ramp-plate 984. Neutral
safety switch
9648 provides a biasing force, transmitted through the switch plunger, to
switch extension
964C which biases the extension outwardly in the direction of neutral ramp-
plate 984,
whereby the second end of switch extension 964C is generally biasingly held in
an
interfacing relationship with the convex outer surface of neutral ramp-plate
984,
irrespective of which particular portion of the ramp-plate is in actually
interfacing
communication with the extension 964C.
However, when switch extension 964C communicates with, for example, the first
or
second ends of neutral ramp-plate 984 or with portions of the ramped surfaces
which are
adjacent the first and second ends of the ramp-plate, the plunger of neutral
safely switch
964B is in a generally outwardly extended position. And when switch extension
964C
communicates with, for example, the apex of the medial portion of neutral ramp-
plate 984
or with portions adjacent the intersection of the ramped surfaces, the plunger
of neutral
safely switch 964B is in a generally depressed position, whereby the switch is
closed.
Switch extension 964C generally communicates with the apex of the medial
portion
of neutral ramp-plate 984 when handlebar 210 is in a resting, neutral, state.
Thus, if
handlebar 210 is pivoted sufficiently far forward or backward, switch
extension 964C
communicates with e.g. the first or second ends of neutral ramp-plate 984,
whereby the
switch plunger is outwardly extended, the starting circuit is open, the
starter motor can not
be energized, and the internal combustion engine can not be started by way of
the
electrical starting mechanism.
Panel assembly 590 includes panel housing 591 A, panel lower cover 591 B,
ignition switch 961, PTO switch 962, and headlight switch 963. Panel housing
591 A
includes an upper wall, and a plurality of sidewalls. The panel housing upper
wall is
generally planar, has a plurality of apertures which extend therethrough, and
outer
perimeter edges. The sidewalls extend generally perpendicularly downwardly
from the
outer perimeter edges of the panel housing top wall. Respective ones of the
sidewalls
are connected to each other, at interfacing edge surfaces, whereby the lower
surface of
the upper wall and the inwardly facing surfaces of the sidewalls generally
define an outer
perimeter of a void, e.g. cavity, within panel housing 591A.
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As desired, each of the lateral-most sidewalls of panel housing 591 A includes
a
slot which extends thereinto, toward the panel housing upper wall. The opening
dimensions of such slots corresponds to respective outside dimensions of
mounting
bracket 2038, whereby the sidewall slots sliding accept panel mounting bracket
2038
thereinto. Accordingly, the panel housing 591A can be mounted to mounting
bracket
2038, by way of e.g. bolts extending though aligned bores passing through the
respective
structures, with the mounting bracket 2038 housed in the sidewall slots and
generally
extending through the panel housing cavity.
Panel lower cover 591 B includes a back wall and a plurality of sidewalls,
e.g. three
or more sidewalls. Panel lower cover 591 B is securingly attached to panel
housing 591 A
by way of, for example, bolts, corresponding snap-lock structures, screws,
rivets, and/or
others.
The panel housing back wall is generally planar and defines a generally
continuous
surface and outer perimeter edges. The sidewalls extend generally
perpendicularly
upwardly from the outer perimeter edges of the panel housing top wall.
Respective ones
of the sidewalls are connected to each other, at interfacing edge surfaces.
Panel lower cover 591 B has an outer perimeter which is generally smaller than
the
inner perimeter defined by panel housing 591A. Namely, panel housing 591A is
adapted
and configured to receive at least part of lower cover 591 B thereinto, into
the panel
housing cavity. Preferably, the overall dimensions and other properties and
characteristics of panel housing 591 A and lower cover 591 B enable the
assemblage of
the two components to suitably separate and provide an adequate barrier
between the
panel housing cavity and the ambient. In other words, the assemblage of panel
housing
591 A and lower cover 591 B provide a substantially weather-proof environment
inside the
cavity enclosure defined thereby.
Ignition switch 961, PTO switch 962, and headlight switch 963 are each housed
in
a respective a perture, sized and configured for the particular switch, which
extends
through the housing upper wall. Namely, each of ignition switch 961, PTO
switch 962,
and headlight switch 963, extends through the panel housing upper wall, into
the panel
housing cavity, and is snap lockingly, frictionally, boltingly, and/or
otherwise suitably,
secured to panel housing 591A.
Referring now to FIGURE 12, various electronic circuits enable a user to
control
various corresponding electrical and/or electromechanical components of snow
blower 1,
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as desired. Battery 966 (FIGURES 12 and 4) provides electrical power to
various circuits
and components of snow blower 1. Ignition switch 961 provides the primary
switching
functions for the electrical components of snow blower 1.
Ignition switch 961 is in electrical communication with at least parts of
engine/prime
mover 100, electromagnetic clutch 130, headlight 204, PTO switch 962,
headlight switch
963, PTO safety switch 964A, safety neutral switch 964B, starter solenoid 965,
and
battery 966. Headlight switch 963 is in electrical communication with
headlight 204,
ignition switch 961, battery 966, and/or others. PTO switch 962 is in
electrical
communication with ignition switch 961, PTO safety switch 964A,
electromagnetic clutch
130, battery 966, and/or others.
Referring now to FIGURES 6, 7, 8, 9A, and 9B, snow blower 1 enables a user to
as desired, selectively lock the first and second wheel assemblies 20, into
rotational
unison with respect to each other.
Each of wheel assemblies 20 includes wheel 21 A, tire 21 B, and various pieces
of
mounting hardware. Wheel 21A is preferably a steel, optionally aluminum,
optionally
other metallic, type-wheel. Wheel 21A further includes a hub mounting
structure, at the
inwardly facing, medial portion thereof. A through bore extends axially
through the hub
mounting structure and defines an inner circumferential surface. A keyway
extends into
this inner circumferential surface, and along the length thereof. The keyway
is adapted
and configured to accept key 24 therein, which mechanically locks the hub
mounting
structure and thus wheel 21A to axle shaft 15A. In addition, washers 25, 26,
ring 17, one
or more threaded nuts, cover 28, and/or other suitable hardware, removably
attach wheel
assembly 20 to axle shaft 15A and/or 15B.
The inwardly facing end of the hub mounting structure, e.g. the end which
faces
transaxle assembly 10, defines an end surface with alternating projections
extending
therefrom and recesses extending thereinto. The projections and recesses of
the hub
mounting structure end is adapted and configured to cooperatively interface
with
corresponding structure of components of selectable lock assembly 780.
Selectable lock assembly 780 includes tie shaft 800, bracket 801, base plate
802,
washer 803, pin 804, pivot pins 804A, 804B, locking arm 820, protuberance 821,
pivot
arm 825, spring 826, pedal 830A, 830B, drive gear 838, driven hub gear 840,
interlock
hub 842 and cover 850.
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Tie shaft 800 is an elongate, rigid, generally cylindrical member, which
extends
through chassis 7, generally between the first and second wheel assemblies.
Tie shaft
800 is adapted and configured to rotate about an axis of rotation, and to
pivotably and/or
otherwise move or translate which enables various components of selectable
lock
assembly 780 to selectively cooperate with other, corresponding, components of
selectable lock assembly 780
Each end of tie shaft 800 includes a portion which defines a generally lesser
diameter than the remainder of shaft 800. In other words, each end of tie
shaft 800 is a
generally stepped-down, shoulder portion. A bore extends radially into each
end of tie
shaft 800, adjacent the respective shoulder portions.
Bracket 801 is an e.g. L-shaped bracket which movably houses tie shaft 800 and
movably attaches the tie shaft to running gear assembly 5. Namely, the
generally
horizontal portion of bracket 801 is attached to an upper surface of an outer
end of
transaxle assembly 10, optionally to frame rail 7F, optionally elsewhere on
chassis 7. The
generally vertical portion of bracket 801 extends upwardly from the outermost
later edge
of the horizontal portion, and has an elongate aperture which extends through
the
thickness of the generally vertical portion. The shape, configuration, and/or
other
characteristics of the elongate aperture correspond to the desired travel path
of tie shaft
800.
Base plate 802 is an e.g. elongate plate member which has a lower flange
extending generally perpendicularly outwardly from a lower portion thereof.
Base plate
802 movably houses tie shaft 800 and movably attaches the tie shaft to running
gear
assembly 5. Namely, the lower flange of base plate 802 is attached to an upper
surface
of an outer end, opposite the end to which bracket 801 is attached, of running
gear
assembly 5. Optionally base plate 802 is attached to frame rail 7F, optionally
elsewhere
on chassis 7. The generally vertical oriented plate portion of base plate 802
extends
upwardly from the lower flange, and has an elongate aperture which extends
through the
thickness of the generally vertical portion. The shape, configuration, and/or
other
characteristics of the elongate aperture correspond to the desire travel path
of tie shaft
800.
Base plate 802 defines an inwardly facing surface and an outwardly facing
surface.
The inwardly facing surface of base plate 802 faces toward chassis 7 and the
outwardly
facing surface of base plate 802 faces outwardly away from chassis 7. Cover
mounting
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structure, such as, for example, first and second elongate screw bosses extend
outwardly
from the outwardly facing surface of base plate 802.
Although tie shaft 800 moves generally vertically within bracket 801 and base
plate
802, as enabled at least partially by the respective elongate apertures of the
bracket and
plate, tie shaft 800 is held generally laterally static with respect thereto.
Namely, pins 804
are inserted into the bores adjacent the ends of tie shaft 800. Pins 804
generally laterally
restrain washers 803, which are mounted inwardly of bracket 801 and base plate
802.
The interfacing relationship between washers 803 and the inwardly facing
surfaces of
bracket 801 and base plate 802, generally mechanically prevent non-desired
lateral
movement of tie shaft 800.
Pivot pins 805A and 805B extend outwardly from the inward facing surface of
base
plate 802, e.g. toward chassis 7. Pivot pins 805A and 805B are adapted and
configured
to pivotably house locking arm 820 and pivot arm 825 thereon, respectively.
Lock arm 820 is an elongate, generally plate like member with an upper edge, a
lower edge, a pivot bore, and a shaft bore. The shaft bore extends through the
thickness
of lock arm 820, through generally a medial portion thereof. Tie shaft 800
extends
through the shaft bore of lock arm 820, whereby the shaft is rotatably housed
in lock arm
820. As desired, tie shaft 800 is rotatably housed in directly in lock arm
820, optionally
separated therefrom by e.g. suitable spacers, bushings, bearings, and/or other
suitable
interfacing members.
The pivot bore of lock arm 820 extends through the thickness of lock arm 820,
adjacent the forward most end of the arm. The pivot bore of arm 820 pivotably
rides upon
pivot pin 804A, which generally defines an axis of pivotation of the arm.
Protuberance 821 is attached to the upper edge of lock arm 820, adjacent the
rearward most end of the arm. Protuberance 821 is adapted and configured to
attach a
first end of spring 826 thereto.
Pivot arm 825 is an elongate, generally plate like member with an upper
surface, a
lower surface, front and back ends, and a pivot bore. The front end and the
upper
surface of the arm 825 generally define first 827 and second 828 vamped
surfaces, with
are adapted and configured to interface, separately, with the lower edge 829
surface of
lock arm 820.
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The pivot bore of pivot arm 825 extends through the thickness of pivot arm
825,
adjacent a medial portion of the arm. The pivot bore of arm 825 pivotably
rides upon
pivot pin 804B, which generally defines an axis of pivotation of the arm.
The pivot position of pivot arm 825 determines which of the first 827 and
second
828 tamped surfaces of arm 825 interfaces the lower surface 829 of lock arm
820.
Namely, when pivot arm 825 is pivoted downwardly, so that the front end
thereof is
relatively higher, the first camped surface 827, proximate the end of arm 825,
interfaces
the lower surface 829 of lock arm 820, as illustrated in FIGURE 9A. As the
first tamped
surface 827 of pivot arm 825 interfaces lock arm 820, lock arm 820 is pushed
generally
upwardly and forwardly, pivoting about pivot pin 804A.
When pivot arm 825 is pivoted relatively less far, so that the front end
thereof is
relatively lower, second tamped surface 828, which angularly extends upwardly
and back
from first ramp surface 827 toward and about the pivot bore, the second tamped
surface
interfaces with lower surface 829 of lock arm 820, as illustrated in FIGURE
9B. As the
second tamped surface of pivot arm 825 interfaces lock arm 820, lock arm 820
can be
pivoted generally downwardly and back, about pivot pin 804A.
Spring 826 extends between and connects lock arm 820 and chassis 7. Namely, a
first end of spring 826 is attached to protuberance 821 and the second end of
spring 826
is attached to a chassis lower flange. Spring 826 is a tension spring whereby
the spring
urges lock arm 820 downwardly and back, pivotably about pivot pin 804A.
In some embodiments, such as that illustrated in FIGURE 7, snow blower 1
includes one base plate 802 and set of corresponding, cooperating components
(base
plate 802 is removed in FIGURE 7 to show various corresponding components). In
other
embodiments, s uch a s t he o ne a xemplarily i Ilustrated i n F IGURE 8 ,
snow blower 1
optionally includes two base plates 802 and two sets of corresponding,
cooperating
components, e.g. communicating with each of the two wheel assemblies 20 (base
plates
802 is removed in FIGURE 8 to show various corresponding components).
In embodiments which include a s ingle b ase p late 8 02, t he a ssemblage c
an
include a single actuating mechanism, namely a single pedal 830A. In
embodiments
which include two base plates 802, the assemblage includes first and second
actuating
mechanism, namely two-pedal assembly 830B, or a single actuating mechanism
which
actuates both base plate lever assemblies. Regardless of the particular
implementation,
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each pedal 830A, 830B includes an elongate member which attaches the pedal to
the
back end of the respective pivot arms) 825.
Optionally, snow blower 1 can include a cable actuation mechanism in addition
to,
or in lieu of, pedals 830A, 830B. Such mechanism can include, for example
first and
second cables, one which pulls the back end of pivot plate 825 upwardly, the
other which
pulls the back end of pivot plate 825 downwardly, so as to pivot the pivot
plate, as
desired, about pivot pin 804B. Such cable actuation mechanism can be
manipulated by
the hand of a user, and the end of such cable actuation mechanism can be
mounted to
e.g. panel assembly 590.
Drive gears 838 have toothed outer circumferential surfaces and are fixedly
attached to respective ends of tie shaft 800, by way of e.g. press fit or
other suitable
attachment to lesser diameter, shouldered, end portions of the shaft. Thus,
drive gears
838 rotate in unison with tie shaft 800 and/or vertically, pivotably, or
otherwise movingly
translate in unison with the tie shaft.
Driven hub gears 840 are fixedly attached to respective ones of axle shafts
15A,
15B, by way of e.g. press fit, corresponding keys and keyways, corresponding
splined
surfaces, setscrews, and/or other suitable means of attachment. In other
words, ones of
driven hub gears 840 rotate in unison with respective ones of axle shafts 15A,
15B.
Driven hub gears 840 each have an inwardly facing surface, an outwardly facing
surface, and a toothed outer circumferential surface which is adapted and
configured to
cooperatively interface with the toothed outer surface of drive gear 838. The
inwardly
facing surface of driven hub gear 840 faces chassis 7 and the outwardly facing
surface of
gear 840 faces wheel assembly 20.
The relationship between drive and driven hub gears 8 38 a nd 8 40 g enerally
defines two distinct operating conditions of selectable lock assembly 780. In
the first,
unlocked condition, the drive and driven hub gears 838 and 840 are generally
radially
spaced from each other and do not interface. In the second, locked, condition,
the drive
and driven hub gears 838 and 840 toothedly and operably interface with each
other,
whereby drive gear 838 can generally rotatably drive driven hub gear 840, and
vise versa.
Interlock hub 842 extends generally axially away from a medial portion of the
outwardly facing surface of driven hub gear 840, and rotates in unison
therewith.
Interlock hub 842 is adapted and configured to interface and operably couple
with the hub
mounting structure of wheel 21A.
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Namely, interlock hub 842 has an end surface with alternating right-angle
projections extending therefrom and right-angle recesses extending thereinto.
The
projections and recesses of interlock hub 842 mechanically interlock with
corresponding
recesses and projections of wheel 21A, thereby lockingly coupling driven hub
gear 840
with wheel assembly 20.
As desired, the assemblage further includes cover 850. Cover 850 envelopes,
shields, covers, and/or otherwise at least partially encapsulates, various
components of
selectable lock assembly 780, such as e.g. drive and driven hub gears 838,
840, and/or
others. Screws and/or bolts extend through bores of cover 850, and threadedly
insert into
the screw bosses of base plate 802, generally affixing the cover thereto.
Accordingly, as desired, to actuate the mechanism into the first unlocked
condition,
a user presses downwardly on e.g. pedal 830A, which pivots the front end of
pivot arm
825 about pivot pin 804B, upwardly and back. Namely, this pivotal motion of
pivot arm
825 slides second ramped surface 828 of arm 825 out from under bottom surface
829 of
lock arm 820, which pivots lock arm 820 about pivot pin 804A, upwardly and
forward, until
first ramped surface 827 of pivot arm 825 interfaces lower surface 829 of lock
arm 820.
The rearvvardly directed tensile biasing force provided by spring 826
generally holds the
locker and pivot arms 820, 825 in this condition, with first ramped surface
827 interfacing
lower surface 829 of lock arm 820 (FIGURE 9A), thus raising gear 838 out of
engagement
with gear 840.
In this unlocked condition, the drive and driven hub gears 838 and 840 are
generally radially spaced from each other and do not interface.
Correspondingly, wheel
assemblies 20 are generally not locked in rotational unison with each other,
whereby the
wheel assemblies are generally free to rotate with respect to each other as
permitted by
differential mechanism assembly 14.
To actuate the wheel lock mechanism into the second, locked condition, a user
pulls upwardly on e.g. pedal 830A, which pivots the front end of pivot arm 825
about pivot
pin 804B, downwardly and foreword. Namely, this pivotal motion of pivot arm
825 slides
first ramped surface 827 of arm 825 forwardly out from under bottom surface
829 of lock
arm 820, which enables spring 826 to draw lock arm 820 about pivot pin 804A,
downwardly and back, until second ramped surface 828 of pivot arm 825
interfaces lower
surface 829 of lock arm 820. The rearwardly directed tensile biasing force
provided by
spring 826 generally holds lock arm 820 and pivot arm 825 in this condition,
with second
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vamped surface 828 of the pivot arm 825 interfacing the lower surface 829 of
lock arm
820.
In the locked condition, the drive and driven hub gears 838 and 840 toothedly
and
operably interface with each other, whereby drive gear 838 can generally
rotatably drive
driven hub gear 840, and vise versa. Correspondingly, wheel assemblies 20 are
generally locked in rotational unison with each other, whereby torque applied
to one
wheel assembly 20 is necessarily applied to the other wheel assembly 20, as
transmitted
through a first wheel assembly, through a first driven hub gear 840 and drive
gear 838,
thence through tie shaft 800 to the second drive gear 838, through the second
driven hub
gear 840, and ultimately to the second wheel assembly 20.
In o ther w ords, i n t he I ocked c ondition, w heel assemblies 20 are locked
into
rotational unison with each other, by way of selectable lock assembly 780,
irrespective of
any force differentiation between first and second axle shafts 15A, 15B,
realized through
differential mechanism assembly 14.
Preferably, various components of snow blower 1 are suitably protected from
non-
desired forces and/or loads. Exemplary of such protection mechanisms are
readily
replaceable and relatively inexpensive components such as shear bolts, shear
pins,
and/or o thers, w hich w ill b reak a nder strain, load, or other force before
mechanical
damage is realized at the protected component.
Pivotable, rotatable, and/or other parts of snow blower 1, including, but not
limited
to, various one of the idlers, pulleys, handles, and/or others, include
bearings, spacers,
bushings, a nd/or o ther c ooperating c omponents, w hich a re, for example,
housed in
respective axial bores, recesses, or other suitably receiving structures,
which enable such
pivotable, rotatable, and/or other parts to suitably move e.g. pivot, rotate,
or otherwise
move relative to other parts, as desired and for the intended use life of the
respective
component.
Preferably, snow blower 1 is made of materials which resist corrosion, and are
suitably strong and durable for normal extended use. Those skilled in the art
are well
aware of certain metallic and non-metallic materials which possess such
desirable
qualities, and appropriate methods of forming such materials.
Appropriate metallic materials for components of snow blower 1 include, but
are
not limited to, anodized aluminum, aluminum, steel, stainless steel, titanium,
magnesium,
brass, and their respective alloys. Common industry methods of forming such
metallic
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materials include casting, forging, shearing, bending, machining, riveting,
welding,
powdered metal processing, extruding, molding, and others.
Non-metallic materials suitable for components of snow blower 1 such as ones
of
various idlers 80A, 80B, 233, 250, 421, various covers, shields, guards,
and/or others, are
various polymeric compounds, such as for example and without limitation,
various of the
polyolefins, such as a variety of the polyethylenes, e.g. high density
polyethylene, or
polypropylenes. There can also be mentioned as examples such polymers as
polyvinyl
chloride and chlorinated polyvinyl chloride copolymers, various of the
polyamides,
polycarbonates, and others.
For any polymeric material employed in structures of the invention, any
conventional additive package can be included such as, for example and without
limitation, slip agents, anti-block agents, release agents, anti-oxidants,
fillers, and
plasticizers, to control e.g. processing of the polymeric material as well as
to stabilize
and/or otherwise control the properties of the finished processed product,
also to control
hardness, bending resistance, and the like.
Common industry methods of forming such polymeric compounds will suffice to
form non-metallic components of snow blower 1. Exemplary, but not limiting, of
such
processes are the various commonly-known plastics converting processes.
Snow blower 1 is preferably manufactured as individual components, and the
individual components assembled as sub-assemblies, including but not limited
to, running
gear assembly 5, prime mover 100, handle assembly 200, auger assembly 300,
discharge chute assembly 391, selectable lock assembly 780, and others. Each
of the
aforementioned sub-assemblies is then assembled to respective other ones of
the sub-
assemblies to develop snow blower 1.
Those skilled in the art will now see that certain modifications can be made
to the
apparatus and methods herein disclosed with respect to the illustrated
embodiments,
without departing from the spirit of the instant invention. And while the
invention has
been described above with respect to the preferred embodiments, it will be
understood
that the invention is adapted to numerous rearrangements, modifications, and
alterations,
and all such arrangements, modifications, and alterations are intended to be
within the
scope of the appended claims.
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To the extent the following claims use means plus function language, it is not
meant to include there, or in the instant specification, anything not
structurally equivalent
to what is shown in the embodiments disclosed in the specification.
