Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
CA 02688935 2009-12-21
IMPROVED SELF-PROPELLED TRANSPORTABLE ROCK PICKER
FIELD OF THE INVENTION
The present invention relates to rock picker systems. More particularly, the
present
invention relates to an improved, self-propelled, collapsible and
transportable rock
picker with an integral lift-tilt dump body and infinitely controllable
speeds.
BACKGROUND
Since the introduction of plows to agriculture the need to remove rocks from
crop
fields has been a pressing concern. Rocks contacting plows can break the plow
blades or become jammed in the moving equipment causing gears and connectors
to
become misaligned or damaged. Rocks can also interfere with some types of
harvesting equipment and other agricultural machinery.
Problems caused by rock damage to agricultural equipment go beyond the damaged
equipment. Agriculture is a time-sensitive occupation where delays in planting
or
harvesting while equipment is repaired can cause the loss of part, or all, of
a crop.
Moreover, with more and more pressure to absorb farmland into urban
developments
there is greater imperative to put marginal agricultural land to use, such as
locations
with high rock content in the soil.
Existing rock picker apparatus are not able to optimize their operation to
varying
soil/terrain conditions. They are unable to automatically adjust their
collection
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systems to accommodate rocks of varying sizes. Existing systems cannot easily
be
optimized by adjusting speed ratios and relative positioning of components.
Adjustment is difficult in this regard, generally requiring machine shutdown
while a
mechanic (or mechanics) make physical adjustments through levers or by
replacing
gearboxes and belts. Operators cannot quickly stop individual components or
raise
them to clear obstacles thereby creating potentially unsafe conditions.
Operators
cannot reverse the direction of operation for components in the event of jams
or for
maintenance, leaving them very vulnerable to jamming by large rocks or non-
rock
obstacles, or due to very uneven ground. Additionally, existing systems have
low
storage volume for rocks removed from the field and they do not provide for
easy
offloading of rock. Existing apparatus generally require towing the rock
picker and
separator apparatus behind a tractor, which reduces their maneuverability and
prevents the forward facing operator from monitoring equipment during
operation.
Existing apparatus have focused on particular pieces of technology or gadgets
but
have not solved the problem of integrating an efficient machine which can be
operated by a single person from within an operating cab. Apparatus such as
described by Fahrenholz, below, require complex customized mechanical linkages
and gearing systems which are difficult to maintain, very exposed to damage
and
weather, and not amenable to optimization. Existing apparatus do not provide a
feedwheel mechanism to provide positive capture for efficient transfer of
material into
a collector mechanism. All of these shortcomings severely impact efficiency
and
increase the amount of skilled labor required to clear fields - and thus
increase costs.
Thus, there is a need for a self-propelled rock picker system that:
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1) is capable of extracting, storing and dumping a large volume of rock from a
field
with a high rate of efficiency; 2) can recover quickly and safely from jammed
components by operating components selectively in reverse; 3) provides easily
adjustable component speeds, speed ratios and heights for optimizing according
to
field conditions and worn components; 4) enhances safety by providing for an
emergency shutdown function for moving components without requiring engine
shutdown; 5) is forward mounted so an operator can easily monitor equipment
during
operation; 6) is forward mounted for improved maneuverability; 7) allows
operation of
all components from the cab of a tractor or other prime mover; 8) includes a
large
capacity articulated trailer controllable from an operator's cab for dumping
accumulated rocks; 9) includes a feedwheel for efficient collection of rock
material;
10) can be retrofitted onto the frames of existing combine tractors; 11) is
capable of
clearing three acres of cleared land per hour; 12) can be folded by a single
operator
for transport or stowage; 13) does not require complex customized mechanical
linkages and gear systems; 14) permits components to be changed to different
size or
style, which may require different speed ratios, without need to design new
linkages,
gearboxes, or belt systems; 15) facilitates use of remote operation of
components;
16) facilitates use of effective safety control interlocks.
A number of devices have provided rock pickers, but lack the flexibility,
safety,
reliability and capacity of the present invention. Presently known art
attempts to
address this problem, but has not completely solved the problem. The following
represents a list of known related art:
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Reference: Issued to: Date of Issue:
US 7,028,460 131 Fahrenholz April 18, 2006
US 4,345,655 Fahrenholz August 24, 1982
US 3,782,477 Fahrenholz January 1, 1974
US 3,117,631 Fahrenholz January 14, 1964
US 2,725,700 Fahrenholz December 6, 1955
US 6,702,034 B2 Clary March 9, 2004
US 6,041,866 Smith March 28, 2000
US 5,310,008 Dauvin May 10, 1994
US 5.027,906 Jeannotte et al July 2, 1991
US 4,609,050 Jacobs et at September 2, 1986
US 4,609,049 Migdal September 2, 1986
US 4,319,641 Degelman March 16, 1982
US 4,301,869 Dubois November 24, 1981
US 4,296,818 Malinowski et al October 27, 1981
US 4,282,932 Anderson August 11, 1981
US 4,221,265 Pratt September 9, 1980
US 4,153,114 Morlock May 8, 1979
US 4,059,158 Ranger November 22, 1977
US 4,040,489 Hulicsko August 9, 1977
US 3,739,855 Bliss June 19, 1973
US 3,431,979 Gregerson March 11, 1969
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US 3,261,408 Simonar July 19, 1966
US 2,924,284 Cykler et at February 9, 1960
US 2,686,394 Kalaus et at August 17, 1954
US 2,363,682 Madsen et al November 28, 1944
US 1,563,340 Christenson December 1, 1925 1
US 1,478,142 Ortmann December 18, 1923
US 946,115 Edens January 11, 1910
US 946,273 Richards January 11, 1910
US 624,852 Nugent May 9, 1899
US 047,566 Quimby May 2, 1865
US 019,430 Maydole February 23, 1858
None of the above inventions and patents, taken either singularly or in
combination, is
seen to describe the instant invention as claimed.
Fahrenholz in several patents teaches rock picker systems: US 7,028,460 131
(the
Fahrenholz `460 patent); US 4,345,655 (the Fahrenholz `655 patent); US
3,782,477
(the Fahrenholz `477 patent); US 3,117,631 (the Fahrenholz `631 patent); US
2,725,700 (the Fahrenholz `700 patent).
The Fahrenholz patents (collectively referred to here as "Fahrenholz") teach
towed
rock picker systems utilizing windrows, drum separators, and complicated
conveyor
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systems. Fahrenholz does not teach individually controlled components, but
rather
mechanically linked components using complicated systems of drive shafts,
sprockets, chains and mechanically clutched belts, with all parts operating at
fixed
speed ratios. Fahrenholz does not teach the use of independent drive motors
which
are infinitely adjustable and reversible, and individually operable from the
cab of a
prime mover. Fahrenholz teaches conveyors using manual cable-actuated
clutches,
which require the operator to operate levers requiring significant strength
and skill.
Towed systems such as Fahrenholz reduce maneuverability and visibility.
Fahrenholz does not teach a dynamically mounted feed wheel to handle rocks of
varying sizes. Fahrenholz does not teach mounting a rock picking system
forwardly
for improved visibility and maneuverability. Fahrenholz does not teach the use
of a
foldable system which can be folded by a single operator for transport or
stowage.
Fahrenholz `631 teaches a towed, single windrow apparatus for forming a
windrow of
rocks for a separate rock picker to collect. The apparatus utilizes a
transverse-
mounted frame supporting a roller powered by mechanical linkages from a
tractor
motor using a power-take-off (PTO).
Fahrenholz `655 teaches the use of a rock tumbler for separating rocks from
soil, and
windrows, but towed behind a tractor on a separate frame so that an operator
cannot
monitor the equipment while driving the tractor. Fahrenholz `655 teaches the
use of
mechanical belts and linkages for power transmission, with fixed gear ratios,
preventing adjustment of component speeds, heights or depth of ground
penetration.
There is no provision for reversing components in the event of jams. The
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arrangement of the overlaid conveyor belts is complicated and difficult to
maintain.
The intermediate storage conveyor in Fahrenholz `655 does not have high
capacity
and can only be off-loaded while running certain other equipment, such as the
rock
tumbler, due to the mechanical linkages. Fahrenholz requires a second tractor
to tow
a collection trailer in parallel with the rock picker in order to provide
adequate
intermediate storage. This adds a second operator and can be difficult in
uneven
terrain. It can even lead to serious accidents if the tractors collide or the
second
tractor/trailer gets tangled with the conveyor system.
Thus, while the foregoing body of art indicates it to be well known to have a
rock
picker, the art described above does not teach or suggest a rock picker system
which
has the following combination of desirable features: (1) the system can be
retrofitted
to the frame of a standard combine tractor or other prime mover with the
addition of a
hydraulic power supply; (2) the hydraulic power supply can run off the prime
mover
engine or an independent APU for flexibility; (3) the system folds for
transport on a
flatbed truck; (4) speeds of all components are infinitely adjustable in order
to
optimize operation for different rock/soil conditions or worn components; (5)
rotating
components are reversible to enable recovery from jams; (6) hydraulic drives
and
cylinders are easily stopped in emergency, greatly improving safety; (7) front
mounting providing an operator better visibility and safety; (8) front
mounting
providing improved maneuverability; (9) a large capacity articulated rock box
providing rapid unloading into any bulk container, or directly into fill, by a
single
operator; (10) independently driven components allowing rapid change out of
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damaged/worn parts; (11) independently driven components permitting a single
operator to control all operations from a position inside the cab of a prime
mover; (12)
ease of adjustability, maneuverability, and high capacity enabling a single
operator to
clear up to three acres per hour or more; (13) the ability to upgrade
individual
components; and (14) incorporates a feed wheel to increase efficiency of rock
collection.
Still other features would be desirable. For example, existing systems do not
facilitate
closed loop automation and computerized control. Existing apparatus do not
provide
for replacement or upgrading of modular components. Existing apparatus do not
provide a feed wheel to assist in the collection of larger rocks and breaking
down
aggregate chunks. Existing apparatus do not address the needs in the field
with an
integrated systems approach to address problems of optimization,
upgradeability,
maintenance, reliability, and safety.
SUMMARY AND ADVANTAGES
An improved self-propelled, transportable, rock picker system includes a prime
mover,
the prime mover including an operator's cab and towing means; a hydraulic
power
supply mounted to the prime mover; windrow means detachably and foldingly
mounted to and extending forward from the prime mover, for agitating soil and
causing rocky soil to move toward centrally mounted collector means; collector
means
mounted to the prime mover for collecting the rocky soil from said windrow
means
and moving the rocky soil to separator means; separator means mounted to the
prime
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mover for receiving the rocky soil from the collector means and separating
rocks from
the rocky soil and moving the rocks to transfer means; transfer means mounted
to the
prime mover for receiving rocks from the separator means and transferring the
rocks
to dump trailer means; dump trailer means detachably connectable to the prime
mover towing means for receiving and storing rocks from the transfer means,
transporting the rocks to an offloading location, and offloading said rocks;
hydraulic
power distribution means for hydraulically connecting the hydraulic power
supply to at
least the windrow means, the collector means, the separator means, the
transfer
means, and the dump trailer means, the hydraulic power distribution means
including
remotely operated hydraulic control valves; and, control means for controlling
at least
the hydraulic power supply, the hydraulic power distribution means, the
windrow
means, the collector means, the separator means, the transfer means, and the
dump
trailer means.
The improvements in safety and efficiency are a tremendous advance over
existing
systems. As an example, in testing, an embodiment of this novel rock picker
system
was run on eighteen acres of rocky farmland in Minnesota, removing eighteen
loads
of rock with each load totaling approximately 10-12 yards of material. This
was
accomplished in a single 8-hour day. Existing rock pickers would take at least
2 or 3
days to accomplish the same coverage. The incorporation of a feed wheel into
the
improved rock picker system greatly improved efficiency by actively assisting
in
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transferring rocks accumulating in front of the feed conveyor onto the feed
conveyor,
rather than simply relying on them to simply spill over onto the conveyor
inlet.
The rock picker system of the present invention presents numerous advantages,
including: (1) the system can be retrofitted to the frame of a standard
combine tractor
or other prime mover with the addition of a hydraulic power supply; (2) the
hydraulic
power supply can run off the prime mover engine or an independent APU for
flexibility; (3) the system folds for transport on a flatbed truck; (4) speeds
of all
components are infinitely adjustable in order to optimize operation for
different
rock/soil conditions or worn components; (5) rotating components are
reversible to
enable ejection of jammed material; (6) hydraulic drives and cylinders are
easily
stopped in emergency, greatly improving safety; (7) front mounting provides an
operator better visibility and safety; (8) front mounting provides improved
maneuverability; (9) a large capacity articulated rock box provides rapid
unloading
into any bulk container, or directly into fill by a single operator; (10)
hydraulic
components allow rapid change out of damaged/worn parts; (11) hydraulic
components permit a single operator to control all operations from a position
inside
the cab of a prime mover; (12) ease of adjustability, maneuverability, and
high
capacity enable a single operator to clear up to three acres per hour or more;
(13) the
ability to upgrade individual components; and, (14) a feed wheel is
incorporated to
increase efficiency of rock collection.
Additional advantages of the invention will be set forth in part in the
description which
follows, and in part will be obvious from the description, or may be learned
by practice
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of the invention. The advantages of the invention may be realized and attained
by
means of the instrumentalities and combinations particularly pointed out in
the
appended claims. Further benefits and advantages of the embodiments of the
invention will become apparent from consideration of the following detailed
description given with reference to the accompanying drawings, which specify
and
show preferred embodiments of the present invention.
BRIEF DESCRIPTION OF THE DRAWINGS
The accompanying drawings, which are incorporated into and constitute a part
of this
specification, illustrate one or more embodiments of the present invention
and,
together with the detailed description, serve to explain the principles and
implementations of the invention.
FIG. 1 shows a front perspective view of a rock picker system mounted to a
prime
mover.
FIG. 2 shows a front view of a rock picker system mounted to a prime mover.
FIG. 3 shows a side view of a rock picker system mounted to a prime mover
including
an articulated rock box.
FIG. 4 shows a perspective view of a dump trailer in an elevated dumping
position.
FIG. 4a shows a perspective view of a dump trailer.
FIG. 4b shows a side view of a dump trailer.
FIG. 4c shows a detail view of alignment pulleys on a dump trailer.
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FIG. 5 shows perspective view of a forward portion of a rock picker system.
FIG. 6 shows a top view of a rock picker system.
FIG. 7 shows a schematic representation of a hydraulic distribution and
control
system for a rock picker utilizing a power-take-off (PTO).
FIG. 7a shows a schematic representation of a hydraulic distribution and
control
system for a rock picker system.
FIG. 8 shows a schematic layout of a control panel.
FIG. 8a shows a schematic representation of a control switch.
FIG. 9 shows a detail view of a feed wheel.
FIG. 10 shows an interior perspective view of a drum separator.
REFERENCE NUMBERS USED IN DRAWINGS
The following list of reference numbers used in the Drawings is provided for
convenience:
10 ROCK PICER SYSTEM
12 PRIME MOVER
12a PRIME MOVER CAB
14 FORWARD SUPPORT FRAME
14a LEFT WINDROW ROLLER LOCKING HASP
14b RIGHT WINDROW ROLLER LOCKING HASP
16 PRIME MOVER ENGINE
18 RESERVOIR TANK
HYDRAULIC POWER SUPPLY
22 WINDROW ASSEMBLY
22a LEFT WINDROW ASSEMBLY
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22b RIGHT WINDROW ASSEMBLY
23a LEFT WINDROW ROLLER FOLDING LOCK
23b RIGHT WINDROW ROLLER FOLDING LOCK
24a LEFT WINDROW SUPPORT FRAME REMOVABLE
HINGE PIN
24b RIGHT WINDROW SUPPORT FRAME REMOVABLE
HINGE PIN
25a LEFT WINDROW CROSS BRACE
25b RIGHT WINDROW CROSS BRACE
26a LEFT WINDROW SUPPORT FRAME
26b RIGHT WINDROW SUPPORT FRAME
28a LEFT WINDROW ROLLER HEIGHT ADJUSTMENT
28b RIGHT WINDROW ROLLER HEIGHT ADJUSTMENT
29a LEFT WINDROW SUPPORT FRAME HINGE
CONNECTOR
29b RIGHT WINDROW SUPPORT FRAME HINGE
CONNECTOR
30 ROAD WHEELS
32 CASTER CONNECTORS
33 WINDROW ROLLER RIDGES
34a LEFT WINDROW ROLLER
34b RIGHT WINDROW ROLLER
35a LEFT WINDROW SUPPORT SHAFT
35b RIGHT WINDROW SUPPORT SHAFT
36a LEFT WINDROW ROLLER HYDRAULIC DRIVE
36b RIGHT WINDROW ROLLER HYDRAULIC DRIVE
38a LEFT WINDROW HINGE JOINT
38b RIGHT WINDROW HINGE JOINT
40 CENTRAL SUPPORT FRAME
41 CENTRAL SUPPORT FRAME HINGE CONNECTORS
42 COLLECTOR
48 FEED CONVEYOR
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48a FEED CONVEYOR FORWARD INLET
48b FEED CONVEYOR AFT DISCHARGE
48c FEED CONVEYOR ENDLESS BELT
48d FEED CONVEYOR IDLER
50 FEED CONVEYOR HINGE CONNECTOR
52 FEED CONVEYOR FRONT ROLLER
54 FEED CONVEYOR PARASITIC DRIVE
56 FEED CONVEYOR HYDRAULIC DRIVE
60 COLLECTOR HEIGHT ADJUST LEFT CYLINDER
60a LEFT CYLINDER FIRST END
60b LEFT CYLINDER SECOND END
62 COLLECTOR HEIGHT ADJUST RIGHT CYLINDER
62a RIGHT CYLINDER FIRST END
62b RIGHT CYLINDER SECOND END
66 COLLECTOR CONNECTION MEANS
70 DRUM SEPARATOR
70a DRUM SEPARATOR FORWARD INLET END
70b DRUM SEPARATOR AFT DISCHARGE END
72 DRUM SEPARATOR LONGITUDINAL SLATS
74 DRUM SEPARATOR BLADES
76 DRUM SEPARATOR DRIVE
80 TRANSFER CONVEYOR
80a TRANSFER CONVEYOR FORWARD INLET END
80b TRANSFER CONVEYOR AFT DISCHARGE END
80c TRANSFER CONVEYOR BELT
80d TRANSFER CONVEYOR BELT LIFTING PLATES
82 TRANSFER CONVEYOR HINGE CONNECTOR
84 TRANSFER CONVEYOR LEFT PIVOT CYLINDER
84a LEFT PIVOT CYLINDER FIRST END
84b LEFT PIVOT CYLINDER SECOND END
86 TRANSFER CONVEYOR RIGHT PIVOT CYLINDER
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86a RIGHT PIVOT CYLINDER FIRST END
86b RIGHT PIVOT CYLINDER SECOND END
88 TRANSFER CONVEYOR HYDRAULIC DRIVE
90 DUMP TRAILER
92 PRIME MOVER TOWING HITCH
94 ROCK BOX
98 DUMP TRAILER FORWARD LIFT CYLINDER
98a DUMP TRAILER FORWARD LIFT CYLINDER FIRST
CONNECTION
98b DUMP TRAILER FORWARD LIFT CYLINDER SECOND
CONNECTION
100 DUMP TRAILER AFT LIFT CYLINDER
100a DUMP TRAILER AFT LIFT CYLINDER FIRST
CONNECTION
100b DUMP TRAILER AFT LIFT CYLINDER SECOND
CONNECTION
102 ROCK BOX FORWARD GUIDE RAIL
104 ROCK BOX AFT GUIDE RAIL
106 LIFT FRAME
108 DUMP TRAILER HYDRAULIC CONNECTORS
109 PRIME MOVER HYDRAULIC CONNECTORS
110 DUMP TRAILER FRAME
112 DUMP TRAILER TOWING HITCH
116 DUMP TRAILER FORWARD TILT CYLINDER
116a DUMP TRAILER FORWARD TILT CYLINDER FIRST
CONNECTION
116b DUMP TRAILER FORWARD TILT CYLINDER SECOND
CONNECTION
118 DUMP TRAILER AFT TILT CYLINDER
118a DUMP TRAILER AFT TILT CYLINDER FIRST
CONNECTION
118b DUMP TRAILER AFT TILT CYLINDER SECOND
CONNECTION
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120 ROCK BOX HINGE CONNECTORS
122 FIRST ALIGNMENT CABLE
122a FIRST ALIGNMENT CABLE FIRST END
122b FIRST ALIGNMENT CABLE SECOND END
124 SECOND ALIGNMENT CABLE
124a SECOND ALIGNMENT CABLE FIRST END
124b SECOND ALIGNMENT CABLE SECOND END
126 FORWARD DOUBLE PULLEY
126a FORWARD PULLEY INNER PULLEY
126b FORWARD PULLEY OUTER PULLEY
128 AFT DOUBLE PULLEY
128a AFT PULLEY INNER PULLEY
128b AFT PULLEY OUTER PULLEY
140 FEED WHEEL
142 FEED WHEEL ARM
144 FEED WHEEL HINGE CONNECTOR
146 FEED WHEEL ADJUSTABLE SUPPORT BLOCKS
148 FEED WHEEL HYDRAULIC DRIVE
150 HYDRAULIC CONTROL VALVE BLOCK MANIFOLDS
150a FIRST VALVE BLOCK MANIFOLD
150b SECOND VALVE BLOCK MANIFOLD
150c THIRD VALVE BLOCK MANIFOLD
150d FOURTH VALVE BLOCK MANIFOLD
150e FIFTH VALVE BLOCK MANIFOLD
152 CONTROL PANEL
154 VOLTAGE SUPPLY
156 EMERGENCY STOP SWITCH
160 LEFT WINDROW HEIGHT ADJUST HYDRAULIC
CONTROL VALVE
162 RIGHT WINDROW HEIGHT ADJUST HYDRAULIC
CONTROL VALVE
164 COLLECTOR HEIGHT ADJUSTMENT CYLINDERS
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HYDRAULIC CONTROL VALVE
166 TRANSFER CONVEYOR PIVOT CYLINDERS
HYDRAULIC CONTROL VALVE
168 LEFT WINDROW ROLLER DRIVE HYDRAULIC
CONTROL VALVE
170 RIGHT WINDROW ROLLER DRIVE HYDRAULIC
CONTROL VALVE
172 FEEDWHEEL DRIVE HYDRAULIC CONTROL VALVE
174 FEED CONVEYOR DRIVE HYDRAULIC CONTROL
VALVE
176 DRUM SEPARATOR DRIVE HYDRAULIC CONTROL
VALVE
178 TRANSFER CONVEYOR DRIVE HYDRAULIC
CONTROL VALVE
180 ROCK BOX LIFT CYLINDERS HYDRAULIC CONTROL
VALVE
182 ROCK BOX TILT CYLINDERS HYDRAULIC CONTROL
VALVE
190 LEFT WINDROW HEIGHT ADJUST HYDRAULIC
SPEED CONTROL VALVE
192 RIGHT WINDROW HEIGHT ADJUST HYDRAULIC
SPEED CONTROL VALVE
194 COLLECTOR HEIGHT ADJUSTMENT CYLINDERS
HYDRAULIC SPEED CONTROL VALVE
196 TRANSFER CONVEYOR PIVOT CYLINDERS
HYDRAULIC SPEED CONTROL VALVE
198 LEFT WINDROW ROLLER DRIVE HYDRAULIC SPEED
CONTROL VALVE
200 RIGHT WINDROW ROLLER DRIVE HYDRAULIC
SPEED CONTROL VALVE
202 FEEDWHEEL DRIVE HYDRAULIC SPEED CONTROL
VALVE
204 FEED CONVEYOR DRIVE HYDRAULIC SPEED
CONTROL VALVE
206 DRUM SEPARATOR DRIVE HYDRAULIC SPEED
CONTROL VALVE
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208 TRANSFER CONVEYOR DRIVE HYDRAULIC SPEED
CONTROL VALVE
210 ROCK BOX LIFT CYLINDERS HYDRAULIC SPEED
CONTROL VALVE
212 ROCK BOX TILT CYLINDERS HYDRAULIC SPEED
CONTROL VALVE
220 LEFT WINDROW HEIGHT ADJUST HYDRAULIC
CONTROL VALVE CONTROL SWITCH
222 RIGHT WINDROW HEIGHT ADJUST HYDRAULIC
CONTROL VALVE CONTROL SWITCH
224 COLLECTOR HEIGHT ADJUSTMENT CYLINDERS
HYDRAULIC CONTROL VALVE CONTROL SWITCH
226 TRANSFER CONVEYOR PIVOT CYLINDERS
HYDRAULIC CONTROL VALVE CONTROL SWITCH
228 LEFT WINDROW ROLLER DRIVE HYDRAULIC
CONTROL VALVE CONTROL SWITCH
230 RIGHT WINDROW ROLLER DRIVE HYDRAULIC
CONTROL VALVE CONTROL SWITCH
232 FEEDWHEEL DRIVE HYDRAULIC CONTROL VALVE
CONTROL SWITCH
234 FEED CONVEYOR DRIVE HYDRAULIC CONTROL
VALVE CONTROL SWITCH
236 DRUM SEPARATOR DRIVE HYDRAULIC CONTROL
VALVE CONTROL SWITCH
238 TRANSFER CONVEYOR DRIVE HYDRAULIC
CONTROL VALVE CONTROL SWITCH
240 ROCK BOX LIFT CYLINDERS HYDRAULIC CONTROL
VALVE CONTROL SWITCH
242 ROCK BOX TILT CYLINDERS HYDRAULIC CONTROL
VALVE CONTROL SWITCH
D GAP DISTANCE BETWEEN FEED CONVEYOR 48 AND
FEED CONVEYOR FRONT ROLLER 52
H GAP HEIGHT BETWEEN FEED WHEEL 140 AND FEED
CONVEYOR FRONT ROLLER 52
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DETAILED DESCRIPTION
Before beginning a detailed description of the subject invention, mention of
the
following is in order. When appropriate, like reference materials and
characters are
used to designate identical, corresponding, or similar components in differing
figure
drawings. The figure drawings associated with this disclosure typically are
not drawn
with dimensional accuracy to scale, i.e., such drawings have been drafted with
a
focus on clarity of viewing and understanding rather than dimensional
accuracy. In
order to reduce clutter and render the drawings more readable, not every
component
is shown in each view.
In the interest of clarity, not all of the routine features of the
implementations
described herein are shown and described. It will, of course, be appreciated
that in
the development of any such actual implementation, numerous implementation-
specific decisions must be made in order to achieve the developer's specific
goals,
such as compliance with application- and business-related constraints, and
that these
specific goals will vary from one implementation to another and from one
developer to
another. Moreover, it will be appreciated that such a development effort might
be
complex and time-consuming, but would nevertheless be a routine undertaking of
engineering for those of ordinary skill in the art having the benefit of this
disclosure.
Referring to Figs. 1-10, an improved self-propelled, transportable, rock
picker system
is provided and includes a prime mover, the prime mover including an
operator's cab
and towing means; a hydraulic power supply mounted to the prime mover; windrow
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means detachably and foldingly mounted to and extending forward from the prime
mover, for agitating soil and causing rocks to move toward centrally mounted
collector
means; collector means mounted to the prime mover for collecting the rocks
from the
windrow means and moving the rocks to separator means; separator means mounted
to the prime mover for receiving the rocks from the collector means and
separating
rocks from soil and moving the rocks to transfer means; transfer means mounted
to
the prime mover for receiving rocks from the separator means and transferring
the
rocks to dump trailer means; dump trailer means detachably connectable to the
prime
mover towing means for receiving and storing rocks from the transfer means,
transporting the rocks to an offloading location, and offloading the rocks;
hydraulic
power distribution means for hydraulically connecting the hydraulic power
supply to at
least the windrow means, the collector means, the separator means, the
transfer
means, and the dump trailer means, the hydraulic power distribution means
including
remotely operated hydraulic control valves; and, control means for controlling
at least
the hydraulic power supply, the hydraulic power distribution means, the
windrow
means, the collector means, the separator means, the transfer means, and the
dump
trailer means.
Referring again to Figs. 1-10, an embodiment of an improved rock picker system
10 is
shown. Prime mover 12 preferably is a combine tractor powered by engine 16.
Prime mover 12 includes an operator cab 12a and rear mounted towing means 92,
preferably a standard towing hitch of adequate load capacity. Hydraulic power
supply
20 is coupled to the output of engine 16 at the back end of engine 16.
Alternatively,
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CA 02688935 2009-12-21
hydraulic power supply 20 could also be coupled to engine 16 through a power-
take-
off (PTO), through a separate transmission, or could be powered by a separate
auxiliary power unit (APU).
Referring again to Fig. 7, hydraulic power supply 20 includes a hydraulic
supply
pump, reduction gear for coupling the pump to the output shaft of engine 16, a
reservoir tank 18, and other necessary pressure regulators, relief valves,
pressure
gages, etc., which are routine for such devices and therefore not shown in
detail.
Hydraulic power supply 20 may also include an internal bypass valve
interlocked with
the starting circuit of engine 16 so that engine 16 does not have to start
under full
load. In an embodiment engine 16 is a diesel engine rated at 245hp and
hydraulic
power supply 20 includes a hydraulic pump rated at 90 gpm.
As shown in Figs. 1, 3, 5, 6, and 9, forward support frame 14 is mounted to
prime
mover 12 and extends forward of prime mover 12. Preferably forward support
frame
14 is removably mounted, but may be permanently mounted by welding as well.
Removably mounting forward support frame 14 allows conversion of the prime
mover
for different uses, and allows disassembly for long-term storage. Windrow
latches
14a and 14b, preferably attached to forward support frame 14, provide locking
means
in combination with latches 23a and 23b for locking left and right windrow
assemblies,
22a and b respectively, in the folded stowed position. Preferably latches 14a
and b
and 23a and b are simple hasp plates with cotter pins. In this way windrow
assemblies 22a and b may be locked in the folded position, but the rock picker
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system can still be driven with windrow assemblies 22a and b folded due to
caster-
style road wheels and connectors 30 and 32. Central support frame 40 is
connected
to forward support frame 14 by hinge connectors 41. Hinge connectors 41 allow
flex
between central support frame 40 and forward support frame 14 when traveling
over
uneven ground. Preferably hinge connectors 41 consist of sturdy hinge pins
which
can be disconnected for easy disassembly. Central support frame 40 includes at
least one, and preferably two, road wheels 30 for support during operation.
Road
wheels 30 are preferably "caster-style" wheels with vertical rotating caster
connectors
32, so that they can swivel 360 degrees for greater maneuverability.
Windrow assembly 22 includes left and right windrow assemblies 22a and b,
respectively. Windrow assemblies 22a and b extend in a forward-swept
orientation,
like a chevron with the open end forward, from central support frame 40 so as
to urge
material toward centrally mounted collector 42. Left and right windrow
assemblies
22a and b include, respectively, left and right windrow support frames 26a and
b
riding on roadwheels 30 and caster connectors 32. Windrow support frames 26a
and
b are tied to central support frame 40 by crossbraces 25a and b, respectively.
Crossbraces 25a and b are connected to central support frame 40 by removable
pin
connectors 24a and b, and are connected to windrow support frames 26a and b,
respectively, by removable hinge connectors 29a and b. Left and right windrow
support frames include road wheels 30 connected by caster connectors 32 for
support
and maneuverability. Preferably each of windrow support frames 26a and b are
supported by at least two roadwheels 30 for stability. Pin connectors 24a and
b and
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CA 02688935 2009-12-21
29a and b are removable to permit folding and stowage, as described below.
Windrow support frames 26a and b are preferably arranged in a "pigeon-toed"
alignment, angled slightly inward, to provide better turning ability.
Left and right windrow rollers 34a and b are supported by left and right
windrow roller
support shafts 35a and b. Left and right windrow roller hydraulic drives 36a
and b are
preferably mounted at the outside ends of windrow assemblies 22a and b for
easy
maintenance access. Preferably windrow roller hydraulic drives 36a and b are
coupled to windrow rollers 34a and b using chain drives for compactness and to
allow
for minor misalignments and movement, but other coupling methods could be
used.
Windrow roller hydraulic drives 36a and b are preferably reversible and
operable at
variable speeds. Windrow rollers 34a and b preferably include longitudinal
ridges 33
which assist in penetrating into and agitating the soil and rocks as they
rotate.
Windrow roller support shafts 35a and b connect to central support frame 40 by
hinge
joints 38a and b respectively. Windrow roller support shafts 35a and b connect
near
their outer ends to windrow support frames 26a and b, respectively, by means
of
windrow height adjusters 28a and b. Hinge joints 38a and b are preferably
located aft
of hinge pins 24a and b, so that windrow support frames 26a and b are not
parallel
with windrow roller support shafts 35a and b, when viewed from overhead, as
shown
in Fig. 6. This creates a triangle between connection points 24a/b, 29a/b and
38a/b
for strength and stability.
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Referring to Fig. 6, windrow folding means are demonstrated. An operator
simply
disconnects pins 24a and b and pushes windrow support frames 26a and b back.
Windrow assemblies 22a and b rotate about their respective hinge joints 38a
and b
and are locked in their folded position using locking means 23a and b and 14a
and b,
for left and right windrows 22a and b, respectively.
Windrow roller height adjustment means 28a and b preferably consist of simple
hydraulic piston-and-cam arrangements, wherein hydraulic cylinders push cams
(or
levers) on the respective windrow support shafts 35a and b to cause them to
rotate,
thereby causing windrow rollers 34a and b to raise or to dig deeper into the
soil. In
this regard, "height" adjustment includes a range from maximum height above
the soil
to maximum penetration into the soil. Windrow height adjustment means 28a and
b
also provide the connection between windrow roller support shafts 35a and b
and
windrow support frames 26a and b.
Again referring to Figs. 1-3, 5, 6, 7 and 9, an embodiment includes a
collector 42 for
receiving rocky soil from windrow rollers 34a and b. Collector 42 includes
feed
conveyor 48, feed wheel 140, and collector left and right height adjustment
cylinders
60 and 62, respectively. Feed conveyor 48 mounts to prime mover 12 by hinge
connection 50. Feed conveyor 48 preferably includes an endless conveyor belt
48c.
Feed conveyor 48 is powered by feed conveyor hydraulic drive 56. Preferably
feed
conveyor hydraulic drive 56 is reversible and operable at variable speeds.
Feed
conveyor 48 is aligned longitudinally to receive rocky soil at its forward
inlet 48a and
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discharge rocky soil at its aft discharge end 48b to drum separator 70. Feed
conveyor 48 preferably includes front roller 52 mounted forward of feed
conveyor inlet
48a at a selected gap distance D. Preferably gap distance D is at least 1/4
inch (6mm)
to allow adequate clearance. Front roller 52 is preferably power-rotated
through
parasitic drive 54 receiving power through feed conveyor idler 48d. Front
roller 52
preferably is approximately as wide as feed conveyor 48, and includes
longitudinal
ridges similar to windrow roller ridges 33.
Feed wheel 140 is dynamically mounted above feed conveyor front roller 52 and
feed
conveyor inlet 48a to create variable gap height H between feed conveyor front
roller
52 and feed wheel 140. "Dynamically mounted" means that feed wheel 140 is able
to
move vertically as different sized rocks or chunks of soil are fed in between
feed
conveyor front roller 52 and feed wheel 140. Feed wheel 140 is supported by
feed
wheel arm 142. Feed wheel arm 142 is connected to forward support frame 14 by
feed wheel hinge connector 144, such that feed wheel 140 is cantilevered
forward
and is free to rotate up and down about hinge connector 144 like a jaw. Feed
wheel
arm 142 rests on blocks 146 when down, to ensure the desired minimum gap
height
H is maintained. Blocks 146 are mounted to feed conveyor 48 and so move up or
down with feed conveyor 48. Preferably the minimum gap height H is between 1.5
to
2 inches (37-50mm), or approximately the size of the rocks desired to be
removed
such that the material will be gripped between feed wheel 140 and front roller
52 to
help it onto feed conveyor 48. Blocks 146 may be adjustable to vary the
minimum
gap height H, such as by using threaded posts, set screws, dowels or other
means.
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Preferably the maximum gap height is approximately 2 feet (60cm), to provide
sufficient space for feed wheel 140 to "bounce up" without jamming if it
encounters a
large rock or obstacle, and to allow sufficient clearance to raise feed
conveyor 48
clear of the ground when desired. Feed wheel 140 preferably consists of one or
more
pneumatic tires with heavy treads on a common axle. Alternatively, feed wheel
140
may consist of a steel roller with protruding teeth or other suitable roller,
where added
weight is desired to assist in breaking up chunks of soil and rock.
Feed wheel 140 is power rotated by feed wheel hydraulic drive 148. Feed wheel
hydraulic drive 148 is coupled to feed wheel 140, preferably using a chain
drive to
allow for misalignments and movement. Feed wheel drive 148 is mounted to feed
wheel arm 142 and feed wheel 140, so as to move with feed wheel 140.
Preferably
feed wheel hydraulic drive 148 is variable speed and reversible.
Collector 42 includes height adjustment means to lift collector 42 up and
clear of the
ground or to allow collector 42 to dig into the soil. Height adjustment means
is
provided by hydraulically actuated collector lift cylinders 60 and 62. Each of
lift
cylinders 60 and 62 are connected at first ends 60a and 62a, respectively, to
forward
support frame 14 and connected at second ends 60b and 62b, respectively, to
collector lift connection means 66. Collector lift connection means 66 provide
flexible
connections to feed conveyor inlet end 48a. Raising or lowering feed conveyor
inlet
48a relative to the ground also raises and lowers feed wheel 140 as blocks 146
will
maintain feed wheel 140 at the selected gap height H. Preferably collector
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connection means 66 are flexible connectors such as chain, cable, or rope,
which will
allow feed conveyor 48 to "bounce up" as it encounters large rocks being fed
into
collector 42.
Referring to Figs. 1-3, 6 and 10, a drum separator 70 is shown. Drum separator
70
preferably includes a drum separator inlet end 70a, drum separator discharge
end
70b, a plurality of longitudinal slats 72, and a plurality of scoop blades 74.
Drum
separator 70 is aligned axially, and sloped downward from forward to aft, to
urge
separated material aft to transfer conveyor 80. Slats 72 are distributed
evenly around
the perimeter of drum separator 70, with the gap between slats 72 selected
based on
the minimum size of rock desired to be removed from the soil. Preferably slats
72 are
spaced with approximately 2 inches (50 mm) between adjacent slats.
Scoop blades 74 are mounted to the inside surface of drum separator 70 and
extend
radially inward. Scoop blades 74 are arranged in circumferential rows,
preferably two
or three circumferential rows or rings, with multiple blades in each row,
which rows
are distributed along the axial length of drum separator 70. In the disclosed
embodiment scoop blades 74 are arranged in two rows of 2 to 3 blades each.
Scoop
blades 74 are preferably mounted at an angle of attack relative to the
longitudinal axis
of drum separator 70 so as to urge rocks aft.
As shown in Figs. 1-3 and 6, a transfer conveyor 80 receives rock discharged
from
separator drum 70 at transfer conveyor inlet end 80a and discharges rock at
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discharge end 80b to dump trailer 90. Transfer conveyor hydraulic drive 88
drives
transfer conveyor 80. Preferably transfer conveyor 80 includes a transfer
conveyor
belt 80c with lifting plates 80d to facilitate lifting rocks at steeper angles
to shorten the
overall length of rock picker system 10. Transfer conveyor 80 connects to
prime
mover 12 via hinge joint 82. Preferably hinge joint 82 is separable to ease
disassembly and transport.
Transfer conveyor pivoting means, f or moving transfer conveyor 80 between an
aft/transfer position and a forward/dumping position, preferably consists of
hydraulic
cylinders 84 and 86 connected at respective first ends 84a and 86a to prime
mover 12
and at respective second ends 84b and 86b to transfer conveyor 80. Preferably
first
and second connections 84a and b and 86a and b are flexible joints, such as
universal joints, to prevent damage to the cylinder or jamming if rock box 94
is
inadvertently lifted while transfer conveyor 80 is in the aft/transfer
position.
As shown in Figs. 1 - 4c and 7-8a, dump trailer 90 receives rocks from
transfer
conveyor 80 for storage during operations and dumping. Dump trailer 90
includes
large-capacity articulated rock box 94, preferably able to retain 10-12 cubic
yards of
material, mounted to trailer frame 110. Trailer frame 110 preferably includes
towing
hitch 112 for connecting to prime mover towing hitch 92. Rock box 94 is
articulated in
that it can be raised and tilted for dumping its contents. Rock box 94 is
connected to
lift frame 106 via hinge connectors 120. Lift frame 106 fits within forward
and aft lift
guide rails 102 and 104, respectively, such that lift frame 106 slides up and
down
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CA 02688935 2009-12-21
within guide rails 102 and 104 when raised and lowered. "Guide rails" includes
traditional rails, as well as open and closed channels or sleeves. Guide rails
102 and
104 preferably cant outward to provide clearance past the side of dump trailer
frame
110 during dumping. Forward lift cylinder 98 connects at first end 98a to
forward
guide rail 102 and a second end 98b to the forward part of lift frame 106.
Likewise,
aft lift cylinder 100 connects at a first end 100a to aft guide rail 104 and a
second end
100b to the aft part of lift frame 106. Preferably first and second
connections 98a and
b and 100a and b consist of flexible connectors, such as universal joints, to
allow for
movement or slight misalignments. Lift frame 106 or guide rails 102 and 104
may
incorporate friction reducing bearings such as track wheels, runners made from
self-
lubricating plastic, or other means known in the art to reduce loads on lift
cylinders 98
and 100.
Tilting means includes forward and aft tilt cylinders 116 and 118,
respectively.
Forward and aft tilt cylinders 116 and 118, respectively, are connected at
first ends
116a and 118a to lift frame 106 and second ends 116b and 118b to rock box 94.
Aft
tilt cylinder 118 is not visible in the views but is identical to forward tilt
cylinder 116.
Preferably 116a and b and 118a and b are connected using rotating connectors
to
allow for the change in orientation as rock box 94 is tilted during dumping,
but other
methods such as sliders operating in tracks could also be used.
As shown in Fig. 4 - 4c, an embodiment includes first and second alignment
cables
122 and 124. First alignment cable 122 is connected at a first end 122a to the
upper
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CA 02688935 2009-12-21
end of forward guide rail 102 and at a second end 122b to the aft bottom end
of aft
guide rail 104. First alignment cable 122 is routed under forward double
pulley 126
and over aft double pulley 128 under tension. Second alignment cable 124 is
arranged in an opposing manner: connected at a first end 124a to the upper end
of aft
guide rail 104 and at a second end 124b to the bottom end of forward guide
rail 102.
Second alignment cable 124 is routed under forward double pulley 126 and over
aft
double pulley 128. Double pulleys 126 and 128, each include a pair of stacked
coaxially mounted outer and inner pulleys, which can rotate independently and
are
mounted to lifting frame 106 level with each other, moving up and down with
rock box
94. In this embodiment, "outer pulley" refers to the pulley distal from frame
106, and
"inner pulley" refers to the pulley proximal to frame 106. Each of alignment
cables
122 and 124 are routed through the inner or outer set of pulleys,
respectively.
Therefore, first alignment cable 122 is routed under inner pulley 126a, and
over inner
pulley 128a. Second alignment cable 124 is routed over outer pulley 126b, and
under
outer pulley 128b. In this way, if lifting frame 106 begins to misalign during
lifting, e.g.
due to one lift cylinder sticking, the counteracting tension of alignment
cables 122 and
124 acting on pulleys 126 and 128 will balance and maintain lifting frame 106
in
proper alignment with guide rails 102 and 104.
Hydraulic connectors 108 are provided to connect lift cylinders 98 and 100 and
tilt
cylinders 116 and 118 to hydraulic power supply 20. Preferably hydraulic
connectors
108 are quick disconnects, and corresponding quick disconnects 109 are
provided on
prime mover 12.
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CA 02688935 2009-12-21
Individually operated and adjustable hydraulic drives and hydraulic lift
mechanisms
permit great improvements in efficiency and safety. Additionally, individually
operated
hydraulic components allow maintenance and modification to individual
components
without effect on other components and the system as a whole, because system
components are not mechanically linked together in fixed gearing ratios. An
embodiment including simple control means is shown schematically in Figs. 7-
8a.
Hydraulic power supply 20 is in fluid communication with hydraulic loads: left
windrow
height adjustment 28a, right windrow roller height adjustment 28b, collector
height
adjustment cylinders 60 and 62 (collectively), left and right transfer
conveyor pivot
cylinders 84 and 86 (collectively), left windrow roller drive 36a, right
windrow roller
drive 36b, feed wheel drive 148, feed conveyor drive 56, drum separator drive
76,
transfer conveyor drive 88, rock box lift cylinders 98 and 100 (collectively),
and rock
box tilt cylinders 116 and 118 (collectively).
Control of individual hydraulic loads is provided by remotely operated
hydraulic
control valves 160 through 182, to provide remote start/stop control of
corresponding
hydraulic loads as shown: control valve 160 controls left windrow height
adjustment
28a; control valve 162 controls right windrow roller height adjustment 28b;
control
valve 164 controls collector height adjustment cylinders 60 and 62
(collectively);
control valve 166 controls left and right transfer conveyor pivot cylinders 84
and 86
(collectively); control valve 168 controls left windrow roller drive 36a;
control valve 170
controls right windrow roller drive 36b; control valve 172 controls feed wheel
drive
148; control valve 174 controls feed conveyor drive 56; control valve 176
controls
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CA 02688935 2009-12-21
drum separator drive 76; control valve 178 controls transfer conveyor drive
88; control
valve 180 controls rock box lift cylinders 98 and 100 (collectively); and,
control valve
182 controls rock box tilt cylinders 116 and 118 (collectively). As shown
schematically in Fig. 7, remotely operated hydraulic control valves 160
through 182
may be mounted and plumbed through valve manifold blocks 150a-e, with several
similarly-sized valves mounted to each valve manifold block 150a-e.
Alternatively,
valves could be mounted individually or plumbed on a single manifold block,
depending on preference.
Referring to Figs. 7-8a, in an embodiment control valves 160 through 182 are
four-
way three-position double solenoid valves, in order to provide compact
mounting,
simple control wiring, and adequate directional control. Figure 7a provides a
generic
schematic for each hydraulic load. SA and SB refer to the solenoids for
positioning the
hydraulic control valves 160 through 182. A person of ordinary skill in the
art will
understand that other equivalent valving combinations could be used, e.g.
using
separate supply and return solenoid valves rather than a combined four way
valve, or
other equivalent valving arrangements. Manual isolation valves could also be
provided to isolate individual hydraulic loads or manifolds.
Again referring to Figs. 7-8a, in an embodiment, remotely operated control
valves 160
through 182 are in electrical communication with control panel 152, located in
operator's cab 12a. A simple control schematic is provided in Figs. 8 and 8a.
Figure
8a provides a generic circuit schematic for simple switch controls
corresponding to
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CA 02688935 2009-12-21
control switches 220 through 242, using relays L1 and L2 controlling normally
open
and normally closed contacts in series with solenoids SA and SB of control
valves 160
through 182. Normally open contacts from emergency stop switch 156 are also
included in the circuit as a typical safety measure. Three-position selector
switches
220 through 242 are provided on control panel 152 to operate hydraulic control
valves
- and thereby their corresponding hydraulic loads - as shown: selector switch
220
corresponds to control valve 160 controlling left windrow height adjustment
28a;
selector switch 222 corresponds to control valve 162 controlling right windrow
roller
height adjustment 28b; selector switch 224 corresponds to control valve 164
controlling collector height adjustment cylinders 60 and 62 (collectively);
selector
switch 226 corresponds to control valve 166 controlling left and right
transfer
conveyor pivot cylinders 84 and 86 (collectively); selector switch 228
corresponds to
control valve 168 controlling left windrow roller drive 36a; selector switch
230
corresponds to control valve 170 controlling right windrow roller drive 36b;
selector
switch 232 corresponds to control valve 172 controlling feed wheel drive 148;
selector
switch 234 corresponds to control valve 174 controlling feed conveyor drive
56;
selector switch 236 corresponds to control valve 176 controlling drum
separator drive
76; selector switch 238 corresponds to control valve 178 controlling transfer
conveyor
drive 88; selector switch 240 corresponds to control valve 180 controlling
rock box lift
cylinders 98 and 100 (collectively); and, selector switch 242 corresponds to
control
valve 182 controlling rock box tilt cylinders 116 and 118 (collectively).
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CA 02688935 2009-12-21
Selector switches controlling rotating hydraulic loads (i.e. windrow roller
drives 36a
and b, feed wheel drive 148, feed conveyor drive 56, drum separator drive 76,
and
transfer conveyor drive 88) thereby control direction of operation: the
neutral position
"N" corresponds to 0 rpm; position "A" corresponds to normal rotation
direction; and,
position "B" corresponds to reverse rotation direction. Selector switches
controlling
hydraulic cylinders (i.e. windrow height adjustment means 28a and b, collector
height
adjustment cylinders 60 and 62, transfer conveyor pivot cylinders 84 and 86,
rock box
lift cylinders 98 and 100, and rock box tilt cylinders 116 and 118) similarly
control
direction of movement: the neutral position "N" corresponds to locking the
cylinder in
place; position "A" corresponds to extending the cylinder; and, position "B"
corresponds to retracting the cylinder.
Voltage supply 154, shown schematically in Fig. 8a, provides 12vdc power to
operate
control valves 160 through 182 and other dc loads. Voltage supply 154 may
simply
be the alternator/battery circuit of engine 16 or a separate power supply. Any
suitable
voltage source compatible with the solenoid operated control valves 160
through 182
can be used, including ac voltage sources, but 12vdc components are commonly
used and available. Emergency stop switch 156 may be incorporated to de-
energize
all solenoid valves and thereby immediately stop all hydraulic loads. Control
panel
152, including selector switches 220 through 242, is in electrical
communication with
control valves 160 through 182.
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CA 02688935 2009-12-21
Referring again to Figs. 7 and 7a, in an embodiment speed control for
hydraulic loads
is provided by throttle valves 190 through 212, corresponding to hydraulic
loads as
shown: control valve 190 controls left windrow height adjustment 28a; control
valve
192 controls right windrow roller height adjustment 28b; control valve 194
controls
collector height adjustment cylinders 60 and 62 (collectively); control valve
196
controls left and right transfer conveyor pivot cylinders 84 and 86
(collectively); control
valve 198 controls left windrow roller drive 36a; control valve 200 controls
right
windrow roller drive 36b; control valve 202 controls feed wheel drive 148;
control
valve 204 controls feed conveyor drive 56; control valve 206 controls drum
separator
drive 76; control valve 208 controls transfer conveyor drive 88; control valve
210
controls rock box lift cylinders 98 and 100 (collectively); and, control valve
212
controls rock box tilt cylinders 112 and 118 (collectively). In an embodiment
shown in
Fig. 7, speed control valves 190 through 212 are manually operated needle
valves
installed on the return side of the hydraulic load to provide fine control.
Alternative
configurations could also be used, including the incorporation of the speed
control
adjustment mechanism into the hydraulic drives themselves.
Referring to Figs. 1-10, the operation of an embodiment is now described for
illustration. The entire system may be operated from the cab 12a of prime
mover 12.
The operator maneuvers prime mover 12 to the start location. Windrow assembly
22
may be unfolded prior to maneuvering to the start location, or may be left
folded and
locked until prime mover 12 arrives at the start location and then deployed.
Hydraulic
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CA 02688935 2009-12-21
power supply 20 is coupled directly to the output of engine 16, so the
hydraulic
system is pressurized when engine 16 is running.
The operator, using selector switches 220 through 242 on control panel 152
(located
inside operator's cab 12a) activates hydraulically driven components - windrow
rollers
34a and b, feed wheel 140, feed conveyor 48, separator drum 70, and transfer
conveyor 80 - and sets the heights of windrow rollers 34a and b and collector
42 as
desired based on anticipated soil conditions. During normal operation windrow
rollers
34a and b rotate such that the bottom is traveling forward relative to prime
mover 12
and the top travels backward relative to prime mover 12. This counter-rotation
agitates the soil and will tend to allow loose soil to flow over the top of
the rollers but
cause heavier rocks to remain in front of the rollers and be urged steadily
toward
collector 42 located centrally aft of left and right windrow assemblies 22a
and b.
The operator may adjust the rotation speed of windrow rollers 34a and b
independently of the speed of prime mover 12, and independently of other
components, to suit the soil conditions and the density and sizes of the rocks
in the
soil to be removed. Referring to Fig. 7, in an embodiment an operator may
adjust
speeds by operating manual throttle valves 190 through 212. The operator
preferably
conducts a test run over a short distance, monitoring the equipment operation
and the
volume and efficiency of rocks collected, and then adjusts operating speeds
and
heights/depths accordingly.
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Center support frame 40 connects to forward support frame 14 by hinge
connector
41. This allows center support frame 40 and windrow assembly 22 to flex up and
down while following the undulations of the ground, thereby preventing jams
and
ensuring optimal performance by maintaining constant height in relation to the
ground.
The rocky soil mixture urged to the center contacts collector 42. Feed
conveyor front
roller 52 rotates in the same direction as windrow rollers 34a and b,
receiving power
from parasitic drive 54 running off of idler 48d. Front roller 52 performs
dual
functions: it absorbs the shock from rocks and obstacles rather than feed
conveyor
48, and it assists rocks onto feed conveyor 48. Feed wheel 140 normally
rotates in
the opposite direction of feed conveyor front roller 52, so as rocks and large
chunks of
soil are urged over top of feed conveyor front roller 52 they are grabbed
between feed
wheel 140 and front roller 52 and accelerated to feed conveyor inlet 48a. Feed
wheel
140 is necessary for two reasons. First, frequently rocks are encountered
which are
too heavy for front roller 52, by itself, to move onto feed conveyor 48. Feed
wheel
140 will grip large heavy rocks on their tops and roll them over front roller
52.
Second, large chunks of soil, and occasionally large chunks of aggregated
rocks, will
be fed to collector 42. The pressure created between feed wheel 140 and front
roller
52, from the weight of feed wheel 140, will tend to break these aggregations
apart for
more efficient separation, and reduces the amount of soil that must be removed
by
drum separator 70. Feed wheel 140 is dynamically mounted above front roller 52
and
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CA 02688935 2009-12-21
feed conveyor inlet end 48a, so it will automatically rise to accommodate
large rocks
as feed wheel arm 142 rotates around hinge connection 144.
Blocks 146 maintain a minimum gap height H between feed wheel 140 and front
roller
52. This minimum gap height H is preferably approximately equal to or slightly
smaller than the minimum average rock size desired to be removed so that the
rocks
will be positively gripped between feed wheel 140 and front roller 52 and
moved to
feed conveyor 48. Generally, rocks equal to or greater than approximately 2
inches
(50mm) across can damage plows and so should be removed. Preferably some
loose soil will fall out in the gap between front roller 52 and feed conveyor
48, but
there will still be a significant amount of soil received by feed conveyor 48
and
discharged into drum separator 70.
Feed wheel 140 and feed conveyor 48 incorporate independent hydraulic drives
148
and 56, respectively, so their speeds can be adjusted independently as well,
to
optimize them for the conditions encountered.
Feed wheel drive 148 and feed conveyor drive 56, which also drives front
roller 52,
are preferably reversible so that if an object becomes jammed between feed
wheel
140 and front roller 52 it can be dislodged by reversing their respective
directions of
rotation. Likewise, if a dangerous object was ingested onto feed conveyor 48
which
could jam drum separator 70 the operator could immediately stop feed conveyor
48,
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CA 02688935 2009-12-21
and then reverse feed conveyor 48 and/or feed wheel 140 to eject the object
forward,
at which point it could be disposed of or maneuvered around.
Feed conveyor 48 is connected to prime mover 12 by hinge connection 50,
allowing
the height of collector 42 to be adjusted by raising or lowering collector
height
adjustment cylinders 60 and 62. This way the operator can adjust the depth of
front
roller 52 in the soil, independently of windrow rollers 34a and b, or raise
collector 42
completely to avoid an obstacle.
Rock-soil mixture is received at feed conveyor inlet end 48a and discharged at
feed
conveyor outlet 48b into drum separator 70. Drum separator 70 separates rocks
from
soil by mechanically beating the rocks against slats 72 and scoop blades 74 to
remove adhered soil, and allowing loose soil to fall out through the gaps
between
slats 72. The spacing between slats 72 determines the minimum size of rocks
removed from the ground. The speed of drum separator hydraulic drive 76 may be
varied independently of other components. The slight slope of drum separator
70 to
aft urges separated rocks aft as drum separator 70 rotates. Scoop blades 74
also act
to urge separated rocks aft due to their angle of attack - similar to the
operation of an
auger, and assist in separation by lifting and dropping aggregate chunks as
the
separator drum 70 rotates.
Drum separator discharge end 70b discharges separated rocks to transfer
conveyor
inlet end 80a. Lifting plates 80d, projecting outward from transfer conveyor
belt 80c,
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assist in moving rocks up transfer conveyor 80 and allow a steeper slope for
transfer
conveyor 80 in order to clear rock box 94 with a shorter overall length. When
rock
box 94 is to be dumped the operator may pivot transfer conveyor 80 forward by
operating transfer conveyor pivot cylinders 84 and 86.
Dump trailer 90 receives separated rock into rock box 94 from transfer
conveyor 80.
The large capacity of rock box 94, preferably holding 10-12 cubic yards of
material,
significantly increases the efficiency of the improved rock picker system over
prior
systems. An operator may dump accumulated rocks either into a collection
container
or directly onto the ground as desired. To dump rocks into a container, the
operator
can simply raise windrow rollers 34a and b from the ground, raise collector 42
from
the ground, stop rotation of windrow rollers 34a and b, feed wheel 140, front
roller 52,
feed conveyor 48, drum separator 70, and transfer conveyor 80, and tow dump
trailer
94 to a position side-by-side to the container. The operator then pivots
transfer
conveyor 80 forward by operating transfer conveyor pivot cylinder 84 and 86 in
order
to provide clearance for rock box 94. Rock box 94 is raised to the desired
height to
clear the sides of the receiving container by extending dump trailer lift
cylinders 98
and 100, causing lift frame 106 to raise upward and outward along guide rails
102 and
104. The outward slant of guide rails 102 and 104 causes rock box 94 to move
sideways as well, to ensure rock box 94 is clear of dump trailer frame 110 and
over
the receiving container when it dumps. When rock box 94 is raised to the
desired
height and side distance the operator extends rock box tilt cylinders 116 and
118,
causing rock box 94 to rotate about hinge connectors 120, thereby dumping its
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contents. In order to make maneuvering close to a receiving container easier,
the
operator can simply raise windrow rollers 34a and b, disconnect hinge pins 24a
and b,
and push windrow rollers 22a and b back into the folded, locked position. An
operator
could also tow dump trailer 56 to a location requiring rock fill, such as a
road
depression or retaining wall area, and discharge rocks directly to that point,
thereby
eliminating a requirement for intermediate transfer to a dump truck.
After the rock is dumped the operator simply lowers the rock box 94 back into
its
normal position, pivots transfer conveyor 80 back to its normal position, and
returns to
the field being cleared. To resume operation the operator simply restarts the
components, lowers the windrow rollers 34a and b and collector 42 to the
desired
height/depth, and continues operation.
When clearing operations are complete an operator can easily fold the improved
rock
picker system for transport on a flatbed truck or storage in a shed. After the
operator
has stopped the individual components and raised windrow rollers 34a and b and
collector 42, the operator simply disconnects left and right windrow support
frames
26a and b by removing hinge pins 24a and b and pushes left and right windrows
22a
and b back, causing them to pivot around pivot joints 38a and b, until they
are close
enough to engage locking hasps 14a and b and 23a and b. Road wheels 30 on
windrow support frames 26a and b swivel 360 degrees so it is easy for a single
person to push windrows 22a and b back to their folded, locked position. The
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operator can then drive the prime mover onto a flatbed truck for transport to
another
location or into a storage shed.
Those skilled in the art will recognize that numerous modifications and
changes may
be made to the preferred embodiment without departing from the scope of the
claimed invention. It will, of course, be understood that modifications of the
invention,
in its various aspects, will be apparent to those skilled in the art, some
being apparent
only after study, others being matters of routine mechanical, chemical and
electronic
design. No single feature, function or property of the preferred embodiment is
essential. Other embodiments are possible, their specific designs depending
upon
the particular application. As such, the scope of the invention should not be
limited by
the particular embodiments herein described but should be defined only by the
appended claims and equivalents thereof.
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