Note: Descriptions are shown in the official language in which they were submitted.
TILLAGE APPARATUSES AND RELATED METHODS
BACKGROUND
1. Field
This invention relates to tilling, including methods, systems, and apparatuses
for
facilitating tilling.
2. Description of Related Art
Tillage apparatuses may be driven/pushed/pulled over a field to be tilled and
have
one, but typically a plurality of, engagement members that may engage with the
ground to dig, stir, or overturn the ground to a desired depth. The
performance of a
tillage apparatus in tilling the ground in a particular area is related at
least in part to
the precision at which engagement members such as for example disks or chisel
blades/plows, are positioned and held at a particular depth in the soil and/or
other
material forming the ground during the tilling process. This can be
particularly
challenging when the tilling process must be carried out over an area of
ground that
has an uneven surface and/or has sloped surface areas.
Tilling the ground accurately and relatively consistently to a desired tillage
depth is
important for several reasons. For example, when tilling to prepare the ground
for
seeding, it is important to till the ground to a relatively precise depth to
provide a
proper bed depth for placement of plant / crop seeds. This is particularly the
case
with so called "minimum till" farming which may currently be increasing in
popularity
in certain areas, and/or as a result of so called "organic farming". For
example, the
tilling of the ground may be desired at a depth of substantially 2 inches ¨
and the
seed may need to be planted for example at a depth of substantially 1 inch.
However, using conventional tilling apparatuses, there may be often
occurrences
during the tilling process of an area of ground, where the ground is only
tilled to 1.5
inches. The result may be that there is hard, untilled ground below the tilled
depth,
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such that planted seeds at 1 inch in depth may have their growth impeded
and/or
they may suffer root rot due to poor drainage. If, however, the ground is
tilled too
deeply, such as in this example notably more than 2 inches, then surface
moisture
may drain too deeply into the ground for the planted seeds to significantly
benefit
during initial growth, thus also impeding their growth. Excess tillage depth
may also
cause a seeding apparatus operable to place seeds into tilled ground, to place
the
seeds at a depth that is deeper than intended or desired. This may result due
to the
operation of a seeding depth gauge mechanism of the seeding apparatus, when
operating on excessively soft soil, causing the seeding apparatus to place the
seeds
lo more deeply in the soft soil than desired and/or intended. This may
result in poor
plant emergence and/or poor plant emergence.
Providing tillage apparatuses that can consistently and precisely till ground
surfaces
to a precise depth that may be uneven and/or includes slopes, has been
challenging.
Traditional tillage apparatuses typically include rigid frames which lack
flexibility and
may be unable to follow the terrain of a contoured ground surface. This is
particularly the case in large scale farming operations where to be able to
efficiently
till a very large surface area (eg. thousands of acres), it is desirable to
have
relatively wide tilling apparatuses that can till a wide area in one single
longitudinal
movement / in each pass through the surface area (eg. a tilling apparatus in
the
range of 10 feet to 70 feet or more in transverse width). The width of the
tillage
apparatus may normally be limited by factors that include the pulling power of
the
propulsion unit (eg. tractor); the strength of the tillage structure and its
components;
and the ability of the tillage apparatus to be oriented in a transportation
configuration
so it may be transported (eg. such being able to be transported on roadways).
Traditional tillage apparatuses may be unable to provide a consistent tillage
depth
across a wide tillage pathway.
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Some known tillage apparatuses may lack reliability and may require
significant
maintenance to keep them running. Some tillage apparatuses may not be able to
accurately control depths at which the ground engaging members engage with the
ground, especially in view of a contoured or sloped ground. In some cases,
inconsistent ground engagement may result in the tillage apparatuses moving
laterally or skewing as they travel across the ground.
Accordingly, improved tilling apparatuses are desirable.
SUMMARY
In one embodiment, the present disclosure relates to an apparatus operable for
supporting one or more agricultural tools. The apparatus comprises a frame and
the
frame comprises a transversely oriented open member having an upper flange and
a
lower flange and a web interconnecting the upper flange and the lower flange;
a
longitudinally oriented open member having an upper flange and a lower flange
and
a web interconnecting the upper flange and the lower flange; the
longitudinally
oriented open member having an opening through the web configured to receive
the
transversely oriented member there through; the lower flange of the
transversely
oriented member being fixedly connected to the lower flange of the
longitudinally
oriented member.
In another embodiment, the present disclosure relates to an apparatus operable
for
supporting one or more agricultural tools. The apparatus comprises a frame
that
includes a transversely oriented open member having an upper flange and a
lower
flange and a web interconnecting the upper flange and the lower flange; a
longitudinally oriented open member having an upper flange and a lower flange
and
a web interconnecting the upper flange and the lower flange; the
longitudinally
oriented open member having an opening through the web configured to receive
the
transversely oriented member there through; the upper flange of the
transversely
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oriented member being fixedly connected to the web of the longitudinally
oriented
member.
In another embodiment, the present disclosure relates to an apparatus operable
for
supporting one or more agricultural tools. The apparatus comprises a frame and
the
frame comprises at least one frame section. The at least one frame section
comprises a first transversely oriented open member having an upper flange and
a
lower flange and a web interconnecting the upper flange and the lower flange;
a
second transversely oriented open member having an upper flange and a lower
flange and a web interconnecting the upper flange and the lower flange; a
first
longitudinally oriented open member having an upper flange and a lower flange
and
a web interconnecting the upper flange and the lower flange; the first
longitudinally
oriented open member having a first opening through the web configured to
receive
the first transversely oriented member there through and a second opening
through
the web configured to receive the second transversely oriented member there
through; a second longitudinally oriented open member having an upper flange
and
a lower flange and a web interconnecting the upper flange and the lower
flange; the
second longitudinally oriented open member having a first opening through the
web
configured to receive the first transversely oriented member there through and
a
second opening through the web configured to receive the second transversely
oriented member there through; the lower flange of the first longitudinally
oriented
member being fixedly connected to the lower flange of the first transversely
oriented
member and being fixedly connected to the lower flange of the second
transversely
oriented member.
In another embodiment, the present disclosure relates to an apparatus operable
for
engaging a ground surface when moved in a direction of travel across the
ground
surface. The apparatus comprises a frame and the frame comprises a first
transversely oriented open member having an upper flange and a lower flange
and a
web interconnecting the upper flange and the lower flange; a second
transversely
oriented open member having an upper flange and a lower flange and a web
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interconnecting the upper flange and the lower flange; the first transversely
oriented
open member being transversely axially alignd with the second transversely
oriented
open member; a pivotal connector operable to provide a pivoting connection
between the first transversely oriented open member and the second
transversely
oriented open member.
In another embodiment, the present disclosure relates to an apparatus that
comprises a row of open members, each of the open members comprises at least
one flange defining at least one open recess along a length of the open
member;
and one or more pivotal connectors, each of the one or more pivotal connectors
coupled between an adjacent pair of open members in the row for facilitating a
pivotal connection between the adjacent open members such that the adjacent
open
members are operable to pivot to orientations generally parallel to a contour
of the
surface when the apparatus is moved across the surface; at least one ground
engager coupled to the at least one flange of each of the open members and
configured to engage the surface when the apparatus is moved across the
surface.
In another embodiment, the present disclosure relates to an apparatus that
comprises a first row of transversely oriented open members, each of the open
members in the first row comprising at least one flange defining at least one
open
recess along a length of the open member; a second row of transversely
oriented
open members, each of the open members in the second row comprising at least
one flange defining at least one open recess along a length of the open
member; a
first pivotal connection device between an adjacent pair of open members in
the first
row for facilitating a pivotal connection between the adjacent open members of
the
first row such that the adjacent open members are operable to pivot about a
first
longitudinal axis; a second pivotal connection device between an adjacent pair
of
open members in the second row for facilitating a pivotal connection between
the
adjacent open members of the second row such that the adjacent open members
are operable to pivot to orientations such that the adjacent open members are
operable to pivot about a second longitudinal axis that is generally parallel
to the first
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longitudinal axis; a plurality of ground engagers coupled to the at least one
flange of
each of the open members in the first and second rows and configured to engage
the surface when the apparatus is moved across the surface.
.. In another embodiment, the present disclosure relates to a mounting
apparatus for
mounting a ground engager to a member. The member comprises first and second
opposed flanges. The apparatus comprises a first flange coupler configured to
be
coupled to the first flange of the open member, the first flange coupler
comprising a
first flange receiving guide having one or more flange securing surfaces that
define a
first narrowing flange securing recess for receiving the first flange; a
second flange
coupler configured to be coupled to the second flange of the open member, the
second flange coupler comprising a second flange receiving guide having one or
more flange securing surfaces that define a second narrowing flange securing
recess for receiving the second flange; at least one mount tightening device
.. interconnecting the first and second flange couplers, the at least one
mount
tightening device; the ground engager being connected to one of the first
flange
coupler and the second flange coupler; the mount tightening device being
operable
to be adjusted to move said first and second flange couplers towards each
other so
that the first narrowing flange securing recess of the first flange receiving
guide is
moved onto the first flange and the second narrowing flange securing recess of
the
second flange receiving guide is moved onto the second flange to secure the
first
and second flange couplers on respective first and second flanges.
In another embodiment, the present disclosure relates to a mounting apparatus
for
.. mounting a ground engager to a member. The member comprising first and
second
opposed flanges. The apparatus comprises a first flange coupler comprising a
first
flange receiving guide having one or more flange securing surfaces that define
a first
narrowing flange securing recess for receiving the first flange and a second
laterally
spaced flange receiving guide having one or more flange securing surfaces that
.. define a second narrowing flange securing recess for receiving the first
flange; a
second flange coupler comprising a third flange receiving guide having one or
more
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flange securing surfaces that define a third narrowing flange securing recess
for
receiving the first flange and a fourth laterally spaced flange receiving
guide having
one or more flange securing surfaces that define fourth narrowing flange
securing
recess for receiving the first flange; a mount tightening apparatus
interconnecting the
first and second flange couplers. The ground engager being connected to one of
the
first flange coupler and the second flange coupler; the mount tightening being
operable to be adjusted to move the first and second flange couplers towards
each
other so that the first narrowing flange securing recess of the first flange
receiving
guide is moved onto the first flange and the second narrowing flange securing
recess of the second flange receiving guide is moved onto the second flange to
secure the first and second flange couplers on respective first and second
flanges.
In another embodiment, the present disclosure relates to an apparatus for
mounting
a component to an open member, the open member comprises at least two flanges
including a first flange and a second flange. The apparatus comprises a first
flange
coupler configured to be coupled to the first flange of the open member, the
first
flange coupler comprising a first flange receiving guide having one or more
flange
securing surfaces that define a first narrowing flange securing recess for
receiving
the first flange; a second flange coupler configured to be coupled to the
second
flange of the open member, the second flange coupler comprising a second
flange
receiving guide having one or more flange securing surfaces that define a
second
narrowing flange securing recess for receiving the second flange; at least one
mount
tightener linking the first and second flange couplers, the at least one mount
tightener having at least one variable length.
In another embodiment, the present disclosure relates to a disc for use with a
tillage
apparatus, the disc formed with a plurality of angularly spaced
circumferential gaps.
In another embodiment, the present disclosure relates to an apparatus operable
for
engaging a ground surface when moved across the ground surface, the apparatus
comprising a frame, the frame comprising at least one frame section, the at
least
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one frame section comprises a first transversely oriented member; a second
transversely oriented member; a first longitudinally oriented member; a second
longitudinally oriented member; the first and second transversely oriented
members
interconnected to the first and second longitudinally oriented member; the
first
.. transversely oriented member extending transversely further in a first
direction than
the second transversely oriented member to form a first transverse extension;
the
second transversely oriented member extending transversely further in a
direction
opposite to the first direction than the first transversely oriented member; a
first set
of ground engagers coupled to the first transversely oriented member and
configured to engage the surface when the apparatus is moved across the
surface;
the first set of ground engagers oriented at a first angle to the longitudinal
direction;
a second set of ground engagers coupled to the first transversely oriented
member
and configured to engage the surface when the apparatus is moved across the
surface; the second set of ground engagers oriented at a second angle to the
longitudinal direction that is in an opposite angular direction to the first
angle and
which is directed inwardly in relation to the frame section.
In another embodiment, the present disclosure relates to an apparatus for
releasing
pressure on a ground engager when the ground engager is engaged with a ground
surface. The apparatus comprises a support; a longitudinally oriented spring;
a rod
located and extending lengthwise within the spring; the rod having a first
distal end
portion inter-connected to the ground engager; the rod have a second opposite
end
portion supported by the support; a rotator cuff device mounted to the support
and
the rotator cuff operable to support the rod proximate the second end; the
rotator
cuff operable to permit the second end portion of the rod to pivot when the
spring is
subjected to a force above a threshold level; a distal spring support mounted
proximate the second end portion of the rod and interconnected to the ground
engager; the rotator cuff device and the distal spring support operable to
hold the
spring in compression there between, such that the spring is operable to exert
an
axial force on the distal spring support and on the interconnected ground
engager;
wherein in operation, when an external force is imparted on the ground engager
that
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creates a force on the spring that exceeds the threshold level, the rod, the
spring
and the rotator cuff will rotate causing the ground engager to rotated to
effect a
reduction in the force imparted on the ground engager.
In another embodiment, the present disclosure relates to an apparatus for
releasing
pressure on a ground engager when the ground engager is engaged with a ground
surface. The apparatus comprises a support; a spring device mounted on the
support and operable for pivoting movement between an engagement position and
a
tripped position; the spring device operable for releasbly exerting a biasing
force on
the ground engager; wherein in operation, when an external force is imparted
on the
ground engager that creates a force on the spring that exceeds a threshold
level, the
rod, the spring device will pivot causing the ground engager to pivot to
effect a
reduction in the force imparted on the ground engager.
In another embodiment, the present disclosure relates to an apparatus that
comprises a frame; a front wheel assembly mounted to the frame, the front
wheel
assembly having a front wheel and a front leg support assembly; the front leg
support assembly operable to provide variable height positioning of the front
wheel
relative to the frame; a rear wheel assembly mounted to the frame the rear
wheel
assembly having a rear wheel and a rear leg support assembly; the rear leg
support
assembly operable to provide variable height positioning of the rear wheel
relative to
the frame; a drive device connected to both the rear wheel assembly and the
frame,
the drive device operable to adjust and hold the height between rear wheel and
the
frame.
In another embodiment, the present disclosure relates to a method for
correcting a
direction of travel of a tillage apparatus moving across a ground surface, the
tillage
apparatus having a front row of ground engagers and a rear row of ground
engagers
engaging the ground surface, the front row of ground engagers being supported
by a
plurality of front wheeled support units each mounted for rotation, the method
comprises receiving at a controller, at least one rotation signal representing
a
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rotation of one of the front wheeled support units; causing the controller to
determine
whether the rotation of the front wheeled support unit is indicative of a
deviation in
the direction of travel of the tillage apparatus with respect to a desired
direction of
travel; and in response to a determination by the controller that there is a
deviation in
the direction of travel, causing the controller to generate control signals to
increase
or decrease engagement of the front row of ground engagers with respect to the
rear
row of ground engagers to produce a side force operable to counteract the
deviation
in the direction of travel.
In another embodiment, the present disclosure relates to an apparatus for
correcting
a direction of travel of a tillage apparatus moving across a ground surface,
the tillage
apparatus having a front row of ground engagers and a rear row of ground
engagers
engaging the ground surface, the front row of ground engagers being supported
by a
plurality of front wheeled support units each mounted for rotation, the
apparatus
comprises a controller; at least one rotation sensor operably configured to
produce a
rotation signal representing a rotation of one of the front wheeled support
units;
wherein the controller is operably configured to determine whether the
rotation of the
front wheeled support unit is indicative of a deviation in the direction of
travel of the
tillage apparatus with respect to a desired direction of travel; and wherein
the
controller is operably configured to, in response to a determination that
there is a
deviation in the direction of travel, generate control signals to increase or
decrease
engagement of the front row of ground engagers with respect to the rear row of
ground engagers to produce a side force operable to counteract the deviation
in the
direction of travel.
In another embodiment, the present disclosure relates to a tillage apparatus
the
comprises a front row of ground engagers and a rear row of ground engagers for
engaging the ground surface, the front and rear rows of ground engagers being
supported on a frame; a frame height control system for controlling a height
of the
frame to control engagement of the front and rear rows of ground engagers; and
a
rear hitch for towing an accessory behind the tillage apparatus, the rear
hitch being
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mounted on the frame and having a hitch point plate coupled to the frame via
an
actuator, the actuator being operable to cause a height of the hitch point
plate to be
raised or lowered in response to changes in height of the frame.
In another embodiment, the present disclosure relates to a method for
controlling a
height of a hitch point plate on a rear hitch for towing an accessory behind a
tillage
apparatus, the tillage apparatus having a front row of ground engagers and a
rear
row of ground engagers for engaging the ground surface, the front and rear
rows of
ground engagers being supported on a frame, the method comprises receiving a
control signal from a frame height control system for controlling a height of
the frame
to control engagement of the front and rear rows of ground engagers; and
causing
an actuator coupling between the hitch point plate and the frame to cause a
height of
the hitch point plate to be raised or lowered in response to the control
signal.
Other aspects and features of the present invention will become apparent to
those
ordinarily skilled in the art upon review of the following description of
specific
embodiments of the invention in conjunction with the accompanying figures.
BRIEF DESCRIPTION OF THE DRAWINGS
.. In drawings which illustrate embodiments of the invention,
Figure 1 is a perspective view of a tillage apparatus and propulsion apparatus
according to an embodiment;
.. Figure 1 A is an enlarged view of the tillage apparatus of Figure 1;
Figures 1 B to 1 E are enlarged views of portions of the tillage apparatus of
Figures 1
and 1A;
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Figure 2 is a side perspective view of a portion of the tillage apparatus
shown in
Figure 1;
Figure 2A is an enlarged side view of part of the apparatus of Figure 1;
Figure 2B is an enlarged end view of part of the apparatus of Figure 1;
Figure 3 is a rear perspective view of a portion of the tillage apparatus
shown in
Figure 1;
Figure 4 is a disassembled view of a portion similar to the portion of Figure
2 of the
tillage apparatus shown in Figure 1;
Figure 4A is a perspective view of some components of part of a mounting and
spring trip mechanism forming part of the apparatus of Figure 1;
Figure 4B is a top perspective view of some components of part of a mounting
and
spring trip mechanism forming part of the apparatus of Figure 1;
Figure 4C is a perspective view of some components of part of a mounting
mechanism forming part of the apparatus of Figure 1;
Figure 40 is a side view of some components of part of ground engager,
mounting
and spring trip mechanism in normal operating mode, which forms part of the
apparatus of Figure 1;
Figure 4E is a top perspective view of some components of a spring trip
mechanism
forming part of the apparatus of Figure 1;
Figure 4F is a side view of some components of part of a mounting and spring
trip
mechanism forming part of the apparatus of Figure 1;
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Figure 4G is a perspective view of some components of a spring trip mechanism
forming part of the apparatus of Figure 1;
Figure 4H is a perspective view of a component of a spring trip mechanism
forming
part of the apparatus of Figure 1;
Figure 41 is a perspective view of some other components of the spring trip
mechanism forming part of the apparatus of Figure 1;
Figure 4J is a side transparent view of some components of part of ground
engager,
mounting and spring trip mechanism in tripped operating mode, which forms part
of
the apparatus of Figure 1;
Figure 4K and 4L are perspective view of components of a spring trip mechanism
forming part of the apparatus of Figure 1;
Figure 4M and 4N are a perspective and front elevation view of a component of
mounting mechanism forming part of the apparatus of Figure 1;
Figure 5A is a front perspective view of an alternate left frame section shown
in
isolation, of the tillage apparatus of Figure 1;
Figure 5B is a view of a central frame section shown in isolation, of the
tillage
apparatus of Figure 1;
Figure 5C is a front perspective view of an alternate right frame section
shown in
isolation, of the tillage apparatus of Figure 1;
Figure 5D is a front plan view of the right frame section of Figure 5C shown
in
isolation;
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Figure 5E is an enlarged view of a portion of the right frame section of
Figure 5C,
marked as 5E;
Figure 5F is an enlarged view of a portion of the central frame section of
Figure 56,
marked as 5F;
Figure 5G is a top plan showing the path of two passes of the tillage
apparatus of
Figure 10 over a ground surface;
Figure 5H is an enlarged close up view of components of the frame of the
apparatus
of Figure 1;
Figure 6 is a top plan view of the tillage apparatus shown in Figure 1;
Figure 6A is a top plan view of the part of the tillage apparatus shown in
Figure 1;
Figures 6B to 6F are top perspective views of parts of the tillage apparatus
shown in
Figure 1;
Figure 6C is a top plan view of the part of the tillage apparatus shown in
Figure 1;
Figure 7 is a perspective view of an alternate tillage apparatus and
propulsion
apparatus;
Figure 7A is a side view of a portion of the tillage apparatus shown in Figure
7;
Figure 7B is a top perspective view of a portion of the tillage apparatus
shown in
Figure 7;
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Figure 7C is a rear perspective view of the tillage apparatus shown in Figure
7 in
isolation;
Figure 8 is a rear perspective view of a portion of the tillage apparatus
shown in
Figure 7;
Figure 8A is a rear perspective view of a portion of the tillage apparatus
shown in
Figure 7;
Figure 8B is a view of a portion of part of a trip mechanism forming part of
the tillage
apparatus shown in Figure 7;
Figures 8C and 8D are side views of a portion of the tillage apparatus shown
in
Figure 7 in un-tripped and tripped modes of operation;
Figure 9 is a side perspective view of a portion of the tillage apparatus
shown in
Figure 7; and
Figure 10 is a top view of a portion of the tillage apparatus shown in Figure
6.
Figure 11 is a top plan view of the tillage apparatus of Figure 1;
Figure 12 is a side view of a portion of the apparatus of Figure 1;
Figure 12A is an enlarged side view of a part of portion shown in Figure 12 of
the
apparatus of Figure 1;
Figure 12B is an enlarged perspective view of a part of the portion shown in
Figure 12 of the apparatus of Figure 1;
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Figure 12C is an enlarged perspective view of a portion shown in Figure 12 of
the
apparatus of Figure 1;
Figure 12D is an enlarged side view of a part of the portion shown in Figure
12 of the
apparatus of Figure 1;
Figure 12E is an enlarged perspective view of a part of the portion shown in
Figure 12 of the apparatus of Figure 1;
Figure 12F is an enlarged side view of a part of the portion shown in Figure
12 of the
apparatus of Figure 1;
Figure 12G is an enlarged side view of a part of the portion shown in Figure
12 of
the apparatus of Figure 1;
Figure 12H is an enlarged perspective view of a part of the portion shown in
Figure 12 of the apparatus of Figure 1;
Figure 121 is an enlarged side sectional view of the part of Figure 12H;
Figure 13 is a schematic view of a control system for the tillage apparatuses;
Figure 14 is a flowchart of a process for detecting and controlling skidding
of the
tillage apparatus during tilling operations;
Figures 14A, 14B, 14C, and 140 are schematic views of alternate control system
for
the tillage apparatuses;
Figure 15A is a rear elevation view of the tillage apparatus of Figure 1 in a
deployed
configuration;
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Figure 15B is a rear elevation view of the tillage apparatus of Figure 1 in a
transport
configuration;
Figures 16A, 16B and 16C are cross section views for example transverse and
longitudinal members of tillage apparatus 10;
Figures 17A, 17B and 17C are cross section views for example transverse and
longitudinal members tillage apparatus 510;
113 Figure 18 is a perspective view of an alternate engaging tool.
DETAILED DESCRIPTION
Referring to Figure 1, a tillage apparatus 10 in accordance with one
embodiment is
shown. In operation, tillage apparatus 10 may be pulled behind a propulsion
unit 12
in a direction of travel denoted by arrow 14 across a ground surface 16 and
the
tillage apparatus 10 may engage with and/or condition the surface 16 as it is
moved
in the direction of travel. In some embodiments, tillage apparatus 10 may
include a
plurality of ground engagers 140 which may have engagement tools such as for
example discs 144, 144A which may be configured to penetrate into and engage
with the material (eg. soil) defining the ground beneath the ground surface 16
and
are moved through and till the soil, preferably at a desired and consistent
depth
within the ground material. Such engagement and/or conditioning may be used to
prepare the ground material for planting and growing crops such as by
preparing a
seed bed as well as uprooting weeds and any cover crops to minimize
competition
for nutrients with the preferred crop.
Propulsion unit 12 may be a known type of tractor, which may be configured and
adapted to pull tillage apparatus 10 via a tow hitch 50 connected to towing
members
52 and 54 of tillage apparatus 10. Towing members 52, 54 may be closed or open
channeled beam members that may be made from a suitably hard and strong
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material such as a steel such as by way of example a suitable structural
steel. In
some application, A36 mild steel, which is considered a structural steel with
a yield
strength of about 60K psi, may be employed. Stronger structural steels with
higher
yield strengths (eg. 80-100K psi) may be employed in other embodiments,
depending upon expected operational and design loads.
In various embodiments, the propulsion unit 12 may be another vehicle capable
of
moving the tillage apparatus 10 and may include a propulsion unit operable to
move
tillage apparatus 10 from one operational location to another operational
location
may be a truck. In some embodiments, the propulsion unit 12 may be integrated
with
tillage apparatus 10.
Referring to both Figures 1 and 6, tillage apparatus 10 may include a frame 18
that
included a plurality of components. Frame 18 may be adapted to be supported
for
movement on the ground surface 16 by a plurality of front wheeled support
units
828, 830, 832, 834 and a plurality of rear wheeled support units 820, 822, 824
and
826, each having one, two or more wheels 197 mounted for rotation. It should
be
noted that given the level of weight carried by rear wheeled support units
820, 822,
824 and 826, and to provide enhanced lateral stability, such wheel support
units
may be double wheel units having two wheels 197 mounted transversely aligned
with each other.
Frame 18 may in turn, support a plurality of rows, such as front and rear rows
120,
122, of ground engagers 140. Ground engagers 140 may include discs and chisel
plows, both of which are described herein, as well as having other ground
engaging
tools or devices.
Frame 18 may include a plurality of transversely oriented (in direction Z in
Figure 1)
structural members interconnected to a plurality of longitudinally oriented
(direction X
in Figure 1) structural members. Frame 18 may be configured into a plurality
of
transversely positioned, frame sections, with a main, central section 18A, and
one or
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more sections positioned on each transverse side of the central section, such
as left
side section 18B and right side section 18C (see Figures 1A and 6).
The transversely oriented structural members may include a front row of
longitudinally axially aligned open members 20 and a rear row of
longitudinally
axially aligned open members 22. The structural open members in front and rear
rows 20, 22 of open members may be made from one or more suitable materials
such as a structural steel like A36 mild steel.
Front row open members 20 may include a center open member 28 in the central
frame section 18A, a left open member 30 in the left frame section 18B, and a
right
open member 32 in the right frame section 18C. Similarly the rear row members
22
include a central open member 38 in the central frame section 18A, a left open
member 40 in the left frame section 18B and a right open member 42 in the
right
frame section 18C. Open member 30 may be transversely axially aligned with
open
member 40; open member 28 may be transversely axially aligned with open member
38; and open member 32 may be transversely aligned with open member 42. With
reference to Figure 5A illustrating a slightly modified embodiment as
described
further below, front row transverse open member 30 and rear row open member
40'
are shown.
As will be described in further detail below, frame 18 may also include a
plurality of
spaced open members 800, 802, 804, 806, 808, 810, 812, 814, and 816 which are
generally oriented in a longitudinal direction (direction X in Figure 1) and
which
interconnect open members in each of the front and rear rows 20 and 22 in each
of
the frame sections 18A, 18B, and 18C. The structural open members 800, 802,
804, 806, 808, 810, 812, 814, and 816 may also be made from one or more
suitable
materials such as a structural steel such as A36 mild steel. With reference to
Figure
5A, note longitudinal open members 800, 802, 804, interconnecting transverse
open
members 40' and 30 in frame section 18B'. It should be noted the different
configuration of open member 800 compared to open members 802 and 804. Open
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member 800 is particularly configured to support wheel assemblies and
associated
frame lift mechanisms as described hereinafter.
Thus open members 800, 802, and 804 may interconnect open members 30 and 40
/ 40' and thereby form a generally rectangular shaped frame section 18B; (open
members 30 and 40 may be parallel or nominally or substantially parallel to
each
other) ; open members 806, 808 and 810 may interconnect open members 28 and
38 to form a generally rectangular shaped central frame section 18A (open
members
28 and 38 may be parallel or nominally or substantially parallel to each
other); and
open members 812, 814 and 816 may interconnect open members 32 and 42 and
thereby form a generally rectangular shaped side frame section 18C (open
members
30 and 40 may be parallel or nominally or substantially parallel to each
other).
With reference again to the front row 20 and rear row 22 of transversely
oriented
open members, each open member 28, 30, 32, 38, 40, 42 may be an open channel
member that has a substantial amount of flexibility (particularly as compared
to a
closed channel member of comparable wall thickness dimensions and made from a
comparable material) when, in operation, it is subjected to a twisting force
about an
axis in the X direction. Each of the open members 28, 30, 32, 38, 40, and 42
may
include a web portion and may have at least one flange defining at least one
open
recess / channel along a length of the open member.
By way of example, in the embodiment shown in Figure 1, each of the open
members 28, 30, 32, 38, 40, and 42 may be a generally I-beam member including
a
generally vertically oriented, longitudinally extending central web portion
inter-
connected or integrally formed with longitudinally extending, upper right and
left side
flanges, and lower left and right flanges. Such a member may be configured to
be
substantially equally flexible when subjected to twisting forces in both
rotational
directions about an axis in the Z direction along its length.
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Open members 28, 30, 32, 38, 40, and 42 may be "wide flange" members which
have flanges that have a greater thickness than the connecting central web.
For
example the flanges may have a thickness of about 1/2 inch which the central
web
may have a thickness of about 3/8 inch.
Referring now to Figure 2, representative open member 42 of rear row open
members 22 and front row open members 20 is shown in further detail. Open
member 42 may include a central web 68 and orthogonally oriented flanges 60,
62,
64, and 66 extending from web 68. Lower flange 60, upper flange 64 and web 68
may define a rearwardly directed channel extending along the length of open
member 42. Similarly, lower flange 62, upper flange 66 and web 68 may define a
forwardly directed channel extending along the length of open member 42. Each
of
the open members 28, 30, 32, 38, and 40 shown in Figure 1 may be configured to
include substantially the same features as open member 42.
Referring back to Figure 1, frame 18 may include a plurality of pivotal
connectors
between the transversely adjacent frame sections 18A/18B and the transversely
adjacent frame sections 18A/18C. For example, transversely positioned adjacent
frame sections, may each have a plurality of pivotal connectors that permit
the frame
sections 18A, 18B to be pivoted relative to each other about an axis oriented
in
direction X (Figure 1). Similarly, a plurality of pivotal connectors that
permit the
frame sections 18A, 18C to be pivoted relative to each other about an axis
oriented
in direction X (Figure 1). Thus, a frontal pivotal connector 80 may be
provided
between open members 28 and 30; a frontal pivotal connector 82 may be provided
between open members 28 and 32; a rearward pivotal connector 84 may be
provided between open members 38 and 40; and a rearward pivotal connector 86
may be provided between open members 38 and 42. Each of the pivotal connectors
80, 82, 84, and 86 may facilitate a pivotal connection between adjacent open
members such that the adjacent connected open members are operable to pivot
from a generally upright position (that may be a storage orientation of a side
section
18B, 18C) to an operational orientation which may typically be generally
supported
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on a contour of the surface 16 when the tillage apparatus 10 is positioned on
surface
16.
Referring to Figure 3, a detailed rear perspective view of representative
pivotal
connectors 82 and 86 is provided between open members 28 and 32 and between
open members 38 and 42 to pivotally interconnect frame section 18A and 18C.
Pivotal connector 82 may include first and second connector plate pair
portions
100a, 100b, and 102a, 102b which may be connected such as by welding, to the
open members 28 and 32 respectively. Pivotal connector 86 may be constructed
in
1() a similar manner an may include first and second connector plate pair
portions 100a,
100b and 102a, 102b which may be connected such as by welding, to the open
members 28 and 32 respectively.
With particular reference to Figures 5B to 5F (which relate to a modified
frame
section 18C' as described below) illustrated in detail are components of
representative connector like pivotal connectors 82 and 86.
As shown in Figures 5C and 5E, one part of a two part pivotal connector that
is part
of frame section 18C is illustrated. Connector plate 102a may be fixedly
attached
such as by welding in a vertical and transverse orientation to outer edges of
respective upper flange 64 and lower flange 60 of open member 42. Similarly
connector plate 102b may be fixedly attached such as by welding in a vertical
and
transverse orientation to outer edges of respective upper flange 66 and lower
flange
62 of open member 42. Connector plate 102a may have a lower cylindrical
opening
103a, and connector plate may have an axially aligned lower cylindrical
opening
103b. Connector plates 102a, 102b, may not be directly attached to the central
web
68 of member 42.
As shown in Figures 5A and 5F, the second part of the pivotal connector that
is part
of frame section 18C is illustrated. Connector plate 100 and connector flange
page
106a may be fixedly attached such as by welding in a vertical and transverse
22
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orientation to outer edges of respective upper flange 107a and lower flange
108a of
a transverse open member of a central frame section 18 such as and rear open
member 38. Similarly connector plate 100b and connector flange 106b may be
fixedly attached such as by welding in a vertical and transverse orientation
to outer
edges of respective upper flange 107b and lower flange 108b of open member 42.
Connector plates 100a, 100b, may not be directly attached to the central web
of
member 38.
A lower cylindrical tube 104 secured at lower ends to connector plates 100a,
100b.
Cylindrical tube 104 may have an axially extending opening. 105. When
cylindrical
tube 105 is received between cylindrical openings 103a, 103b, all the openings
may
be axially aligned and may permit the reception of a connecting pivot pin
member
(not shown) there though. This will provide a pivotal connection between
connector
plates 100a, 100b and connector plates 102a, 102b that ties together flanges
107a,
107b, 108a, 108b of member 38 with flanges 64, 66 and 60, 62 of member 42
without tying the respective webs of the open members.
This hinge mechanism fully ties the top and bottom flanges of open members 28
and
32, (and similarly the open members 38 and 42; members 28 and 30; and members
38 and 40) and permits the transmission of torsional forces between the open
members through the hinge mechanism. The hinge mechanism may be sufficiently
strong to be able to perform these functions reliably and over a significant
period of
use and repetitive cycles of loading. At the same time, the design is such
that it will
typically not significantly limit the torsional flexibility of the vertical
webs of open
members 28 and 32. It should be noted that the term I-Beam is intended not to
be
restricted to members where the thickness of the flange portions may be
similar to
the thickness of the web portions. In some desired embodiments, the thickness
of
the flange portions may be substantially greater than the thickness of the web
portion. This may allow greater design flexibility.
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Each of the pivotal connectors 80, 84, and 86 may include features generally
constructed in a manner substantially the same as pivotal connector 82 to
provide
pivotal connections between adjacent transversely oriented open members in the
front row of longitudinally axially aligned open members 20 and pivotal
connections
between adjacent transversely oriented open members in rear row of
longitudinally
axially aligned open members 22.
Referring again to Figure 1, tillage apparatus 10 may also include a first row
120 of
ground engagers 140 and a second row 122 of ground engagers 140. Each of the
ground engagers 140 of the first and second rows 120, 122 may be coupled to a
pair
of flanges of one of the open members 28, 30, 32, 38, 40, and 42 of the
respective
front row of open members 20 or rear row of open members 22. Ground engagers
of first and second rows 120, 122 may be configured to penetrate the ground
surface
16 and move through the material forming the ground to till the ground
material
when tillage apparatus 10 is moved across an area of ground surface 16.
With reference again to Figure 5A and to Figure 5H, it may be noted that each
of
open members 30 and 40' may each include a plurality of laterally spaced flex
reducing members 131 which fixedly connect an upper portion of the central web
portions on both sides, to their respective lower flanges. Flex reducing
members
may be made from any suitable material such as A36 mild steel and may be in
the
range of 3/16 inch to 1/2 inch thickness.
Such flex reducing members may be positioned and configured to prevent local
over-flexing of the lower flange portions when subjected to high ground
engagement
forces during operation of tillage appratus10. If flanges are over-flexed,
then the
flange may yield, work harden and then possibly crack leading to failure. Flex
reducing members 131 may substantially reduce the amount of over-flexing of
such
lower flanges in one particular location and may assist in spreading the loads
applied to a lower flange in a particular area.
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With reference to Figures 2-2B, a representative ground engager 140 of each
ground engager of the rows of ground engagers 120, 122 (Figure 1) is
illustrated in
further detail. Each ground engager 140 may include a mount 142 which is
coupled
to the lower opposed flanges 60 and 62 of the open structural members 30, 32,
34,
38, 40, 42, such as for example lower opposed flanges 60 and 62 of the open
structural member 42. Mount 142 may include a transversely and longitudinally
extending plate 176 fixedly interconnected (such as by welding) at side edges
to
side plates 158a and 158b (Figures 2A, 2B, 4 and 4B). Side plates 158a, 158b
may
have upwardly extending guide arms 172, 170 respectively which are configured
to
provide slots for engaging with flange 62 of open structural member 42. The
aforementioned components may be made from one or more suitable materials such
as structural steel with relatively big thickness (eg. about the same
thickness as the
web of open member 42).
Extending between side plates 158a, 158b and beneath plate 176 may be a
vertically extending support plate 159 (Figure 2B). Support plate 159 and the
undersurface of top plate 176 may be fixedly connected to and support hollow
cylindrical tubular members 71a, 71b (Figure 2A) each having axially extending
cylindrical passageways which may be used to interconnect mount 142 with
spaced
flange couplers 162, 164 (Figure 5) as described further below.
Ground engager 140 may also include a pair of freely rotatable disks 144 (ie.
freely
rotatable about a central axis oriented in Z direction), and each disk 144 of
the pair
of spaced disks may be pivotally coupled by at least one pivotable arm member
141
to a side plate 158a, 158b of mount 142. Arms 141 and discs 144 attached
thereto,
may pivot about a shaft 199 (Figure 2B) that passes through and is supported
by
spaced side plates 158a, 158b. Providing a transversely oriented rigid
connection
between each arm member 141 of an adjacent pair of discs 144, may be a
transversely oriented support brace member 156 (Figures 4 and 4A). Thus each
pair of disks 144 may pivot together about their common mount 142. It should
be
noted that while each disc 144 may be configured in the same manner and may
CA 2971616 2017-06-21
have generally smooth circular outer edge perimeter, in some embodiments, the
circular outer perimeter of discs 144 in the front row 120 and/or rear row 122
of
ground engagers 140 may be notched. Notched discs 144A may be used on the
front row 120 of ground engagers 140 to compensate for the fact that the discs
144A
on front row 120 of ground engagers 140 will typically have to penetrate
unbroken,
harder ground. By providing notches in the discs 144A in the front row 120
this may
reduce the forces in the Z direction imparted upon the discs in the front row
120 of
ground engagers 140, compared to the forces that would be imparted on un-
notched
discs of the same diameter. This will tend to compensate for the difference in
magnitude of the lateral forces acting on the rear row 122 (which would
otherwise be
lower than the front row for same size and configured discs). In some
embodiments,
front discs and rear discs may be substantially the same in configuration
including
having substantially the same diameter. It
should be noted that in some
embodiments / applications, it may be desirable to provide for a relatively
large disc
size. To increase or maximize the disc size by increasing the height lift
range of the
apparatus. However, providing for a relatively large height adjustment range
may be
limited by the wheel size. Therefore, it may be desirable to provide
relatively large
wheels and discs, such as where they have approximately the same wheel
diameter.
Each ground engager 140 is operable to engage with and penetrate the ground
material beneath surface 16 as tillage apparatus 10 is moved across surface
16.
With particular reference to Figures 2, 4, 4A-4L, a spring trip device 143 may
be
mounted between the pair of transversely spaced disks 144. Even though each
spring trip device 143 has a compressed spring 191, they may not include
suspension like functionality.
Instead, each spring trip device 143 may provide a trip mechanism that
normally
provides constant vertical positioning of the respective disc pairs 144 to
which it is
interconnected relative to the frame 18 to which each spring device 143 and
disc
pair 144 are attached. A pre-set force is exerted by each spring trip device
143 on
26
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support bracket 156 that interconnects pivot arms 141 which are fixedly
connected
to disc pairs 144. Until a force acting against the pre-loading force provided
by
spring trip device 143, exceeds the pre-load force imparted by spring trip
device 143,
then spring 191 of spring trip device 143 will not compress. This pre-load
force may
then assist in maintaining reasonably consistent depth engagement of the
respective
disc pairs 144 inter-connected to the frame 18. However, if one or both discs
of a
pair of discs 144 impact with a very strong, impenetrable item or material in
the
ground (eg. a large rock), the force Fg imparted by such impact on the discs
144
may exceed a maximum allowable threshold force - which corresponds with a
force
.. on the spring 191 greater than the pre-load force Fs. If the force Fg
imparted on
such discs 144 does exceed the threshold level associated with the pre-load
force
Fs, then the spring trip device 143 will "trip" by virtue of its spring 191
undergoing
compression. This compression of the spring 191 and the corresponding force
causing such compression, permits pivoting of the discs 144 on pivot arms 141
to
relieve the force on the discs, the pivot arms 141 and on the frame 18 to
which they
are interconnected. This will then relieve the contact forces being imparted
by the
ground (eg. the rock) on the discs 144 as the discs and their pivot arms 141
will pivot
away from the full engagement position.
.. Spring trip device 143 may be constructed to include a body portion having
longitudinally oriented support struts 151a, 151b. Support struts 151a, 151b
may
be fixedly and strongly connected to an underside surface of a transversely
and
longitudinally extending plate 176 (Figures 2A, 2B, 4 and 4B) of mount 142.
Pairs of
discs 144 may be mounted with their respective pivot arms 141 and side plates
158a, 158b to a separate support plate 176 dedicated to such pair of discs
144.
At a distal end of support struts 151a, 151b and secured there between, may be
a
rotator cuff unit 193 that may include a support bracket 152 and a rotatable
block
186. Spring trip device 143 that may be mounted between support struts 151a,
151b
by bolts 173 that pass through slots in support struts 151a, 151b and slots in
bracket
152. Support bracket 152 may have an inwardly directed generally hemi-
spherical
27
CA 2971616 2017-06-21
surface 152a which may engage with block 186 that may have a corresponding
semi-hemispherical surface 186a. Block 186 is operable to pivot within a range
of
angular movement on and relative to bracket 152 on respective facing sliding
surfaces 152a, 186a. One end of spring 191 may be supported for compression by
.. an annular groove of block 186.
Bracket 152 and block 186 may have axially aligned openings through which an
end
portion of rod 195 may be received through. Rod 195 may be supported by
bracket
152 and block 186 at one of rod 195 and the opening in bracket 152 may be
configured to allow rod 195 to pivot with block 186 and to move axially
relative to
bracket 152 and block 186 when spring 191 is compressed. Jam nuts 177 may be
provided at this outward end of rod 195 and engage with a top surface of
bracket
152. Jam nuts 177 hold and lock the entire assembly of spring trip device 143
together and are positioned the top and final end of the assembly.
Adjusting the position of jam nuts 177 on rod 195 can select the amount of
compression of spring 191 and thus the desired pre-load force of spring 191.
The
greater the compression of spring 191, then the greater the force. When spring
191
is compressed by adjusting jam nuts inwards, the rod 195 will move upwards in
bracket 152. This will shorten the distance between bracket 152 and plate 187,
thus
raising pivot arms 141 and discs 144 attached thereto to a relatively small
extent.
This allows all the discs 144 to be levelled for a consistent depth on all
ground
engagers 140.
The pre-load force can vary based on the particular springs that are selected
for
spring trip device 143. The jam nuts 177 allow the adjustment of the pre-load
to
ensure that all springs are set to the same and correct pre-load value. The
pre-load
determines the force level that will activate the trip mechanism which then
allows the
discs 144 and their pivot arms 141 to rotate about shaft 199. The selected pre-
load
force.
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CA 2971616 2017-06-21
In some embodiments such as is depicted in Figure 4F, there is not threaded
end to
rod 195 with corresponding jam nuts. Thus in this embodiment it is not easily
possible to adjust level of spring compression such that the pre-load force
may be
adjusted.
This preload of spring 191 may vary depending upon the particular springs that
are
selected for each spring trip device 143. Jam nuts 193 allow the adjustment of
this
pre-load force to ensure that all springs are set to the same and the correct
preload
value. The preload, determines the force at which spring trip device 143 will
be
"tripped" when the ground engagers 140 (eg. ground engagers having a pair of
discs
144) encounter a very hard obstacle, but ensure that the pairs of discs 144
remain
fully engaged in the ground until the trip threshold force is reached. This is
in
contrast to known compliant discs on tillage apparatuses that use a suspension
system that does not generally maintain a consistent depth penetration during
normal operation.
The inward end of rod spring 191 is connected to a fork member 154 with a
bottom
spring trip device connector assembly 185. This connector assembly 185 may
include a clevis and clevis pin stylefastener generally designated 155 (Figure
4A).
Fork member 154 may be engaged with support brace member 156 that is
connected to and positioned between arms members 141.
With particular reference to Figures 4E, 4F, 4H, and 41, connector assembly
185
may include a bottom pivot mount device 190 and a base support plate 187. Base
support plate may have an opening which may accept there through an upper
cylindrical portion 190a and body portion 190b of mount device 190. Base
support
plate 187 may rest upon and be supported by upward facing surfaces of hook
portions 190d. The hook portions 190d may prevent the base support plate 187
from
tilting ¨ which keeps spring 191 straight ¨ when the spring 191 and rod 195
rotate as
permitted by rotator cuff unit 193 when the spring trip device 143 is
"tripped". A top
cylindrical opening 190f of mount device 190 will receive an end of rod 195
there
29
CA 2971616 2017-06-21
through. Cylindrical opening 190f may be a threaded opening and may engage
with
a threaded end of rod 195. A nut may be held between hooks 190d.
With particular reference to Figure 4G, a washer 179 may be positioned on rod
195
between jam nuts 177 and the upper surface of bracket 152. In the normal
operating (un-tripped) position, washer 179 will be parallel to and seated
flat on the
top surface on bracket 152 of rotator cuff unit 193.
Spring device 143 may be operable to during normal operation, to provide a
generally downward force on and to bias the pair of arms 141 and the disks 144
mounted thereto, into a position whereby they engage with and penetrate the
ground
material beneath surface 16. However, spring device 143 may be configured and
adapted such that if one or both disks 144 associated with one or more mounts
142
engage with a substantially impenetrable material (eg. a large granite rock),
then to
avoid having the force of such impact transmitted throughout the rest of that
frame
section 18C of which those mounts 142 form a part, and beyond the rest of
frame
18, (potentially causing structural damage to the frame and/or ground engagers
140)
spring device 143 will release the biasing force exerted by spring 191 and
allow the
arms 141 and disks 144 attached thereto to pivot substantially freely away
from the
impenetrable material.
With reference to Figure 4D, each pivot arm 141 and disc 144 has an effective
arm
(shown in broken lines). If the pair of discs 144 of a ground engager 140 are
moving
in a direction of travel DT, and one or both of the discs encounter an
impenetrable
object, then an upward force Fg2 or perhaps a force Fg1 in the general
direction
upwards and slightly backwards may be applied to discs 144. The direction of
force
Fg1 or Fg2 will be such that is will create a rotational force around the
pivot location
at shaft 199.
If the force Fg imparted on such discs 144 does exceed the threshold level
associated with the pre-load force Fs, then the spring trip device 143 will
"trip" by
CA 2971616 2017-06-21
virtue of its spring 191 undergoing compression. By way of example, the force
required to be exerted upwards on spring 191 to compress the spring 191 to
activate
the trip mechanism may be 1242.96 lbs. This compression of the spring 191 and
the corresponding force causing such compression, permits pivoting of the
discs 144
on pivot arms 141 to relieve the force on the discs, the pivot arms 141 and on
the
frame 18 to which they are interconnected. The pivoting movement of arms 141
and
discs 144 can be observed from the position shown in Figure 40 to the position
shown in Figure 4J. It will be noted also the rotation of spring 191 and rod
195,
there is pivoting movement from the position shown in Figure 4E to the
positions
shown in Figures 4K and 4L. This pivoting movement relieves the contact forces
being imparted by the impenetrable material on the discs 144. The geometry of
spring 191 reduces the force in the upper area of the trip range. But never
goes to
over center lock, as it is mechanically stopped. But the forces are reduced at
top end
of the trip range.
Once the spring trip device 143 has been tripped, there is a downwards force
(eg.
539.52 lbs) that is still exerted on the pair of discs 144 (eg. the weight of
the pivot
arms, discs 144 etc.). This will then enable the pair of discs 144 to be
returned to an
operational position with a relatively easy amount of additional force.
Indeed, the
spring trip devices 143 and their respective ground engagers 140 may be
configured
such that the spring trip device 143 will automatically re-set itself once the
discs 144
have cleared the obstacle in the ground.
In other embodiments, instead of a single spring 191, a second spring (eg. a
corresponding axially aligned inner spring housed within spring 191) may be
provided to permit the ground force required to trip the spring trip device
143, to be
increased.
Mount 142 may be coupled to the lower flanges 60 and 62 of the open member 42
which may facilitate the mount rotationally flexing at least a portion of the
open
member 42 about a longitudinal axis 150 of the open member 42. Accordingly,
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when the ground engager 140 encounters a change in contour of surface 16, such
as, for example, a change in slope, a mound, or a hill, the ground engager 140
may
torque and flexibly rotate the open member 42 about the longitudinal axis 150.
As
the open member 42 rotates, this may facilitate raising the disk 144, such
that the
disk 144 stays at a generally constant depth below the surface 16. In some
embodiments, for example, the ground engager 140 may flex the open member 42
such that the ground engager 140 rotates at least about 20 degrees about the
longitudinal axis 150.
However, and as will be explained further elsewhere herein, the relative
position and
height of frame 18 relative to the wheels of wheel units 828, 830, 832, 834
and 820,
822, 824 and 826, and the elevation of the wheels relative to each other, will
typically provide a greater influence on the flexing of the open structural
members
such as open member 42. When tillage apparatus 10 is moving over level, and
horizontal ground, of consistent hardness, all members will in normal
operation
penetrate into the ground the same depth. This is because the overall weight
of
frame 18 and ground engagers 140 will be sufficient to override any upward
force
that may be imparted by the ground on the ground engagers. In such
circumstances
there will be no torsional flexing of the longitudinal structural members 800,
etc.
There may be some torsional forces exerted on the transverse structural
members
32, 42 etc. that may result from the forward movement of the ground engagers
140
through the penetrated ground. However, such torsional forces will typically
be
evenly spread out transversely across the frame 18.
However, when moving over uneven ground, at least some of the structural
members of frame 18 will flex due to the weight of the frame 18 and the ground
engagers 140 attached thereto as the tillage apparatus 10 moves over the
uneven
terrain/ground 16. The depth of penetration in the ground of each of the pairs
of
discs 144 may be primarily determined or influenced by the elevational
positon(s) of
the ground supporting the wheel or wheels that are near or adjacent to the
32
CA 2971616 2017-06-21
respective pair of discs 144. If there is a big depression in the ground
underneath a
particular wheel and wheel assembly that is close to a particular pair of
discs 144,
both the structural members interconnected to that wheel assembly, and the
discs in
the vicinity of those structural members, will also move downwards with that
wheel/wheel assembly relative to other wheel assemblies, structural members
and
discs elsewhere on frame 18. This may also result in torsional flexing of the
structural members in the vicinity thereof in response to the depression in
the terrain.
Similarly, if there is a big increase of elevation in the ground underneath a
particular
wheel(s) 147 and wheel assembly that is close to a particular pair of discs
144, both
the structural members interconnected to that wheel assembly, and the discs
144 in
the vicinity of those structural members, will also move upwards with that
wheel/wheel assembly relative to other wheel assemblies, structural members
and
discs elsewhere on frame 18. This may similarly also result in torsional
flexing of the
structural members in the vicinity thereof in response to the increase in the
terrain in
that locale supporting that wheel 147.
The discs 144 may be maintained at a fairly constant amount of penetration
into the
ground due to the position of the proximate wheel(s) and also due the flexing
of the
structural members of the frame in the vicinity/proximity of those respective
wheels.
The frame 18 may undergo torsional flexing when moving over contoured ground
surface 16 and this may assist in allowing the discs 144 in the vicinity of
those
wheels to move to a position that provides a relatively consistent depth of
penetration.
Also, as described herein, loads that may be imparted onto a particular pair
of discs
144 and structural member to which that particular discs are attached, may be
transmitted for example from a rear row structural member such as structural
member 42 through longitudinal members (such as member 814 ¨ as seen in Figure
5D) to a front row member (such as front row member 32). The shared carrying
of
torsional loads in such a manner can assist in avoiding one pair of discs 144
33
CA 2971616 2017-06-21
undergoing a significantly large movement as a result of a wheel(s) 147 in the
vicinity of such disc pair 144 undergoing a severe change in elevation
relative to
adjacent wheels. Thus the torsional flexing of a lower flange of a structural
member
such as member 42 may ensure that no vertical position of any pair of discs
144 is
too greatly exaggerated.
In overview, the height position of the wheels relative to each other across
the width
and length of the frame 18 may have the greatest influence on the flexing of
the
frame 18 and its open members. The effect of the ground engagers 140 and the
engagement tools thereof moving thorough the penetrated ground may be less
significant. The ground engagers 140 and their tools may be able to generally
maintain constant depth due to the flexibility of the frame, the frame
sections and the
open members forming the same. The tools form a "set" position based on the
terrain contours defined by the wheels. The flex in the frame gradients the
various
wheel heights above or below the set / flat position thus providing a smooth
and
generally consistent ground engagement depth. The torsional flex of the wide
flange
of the open members local to each disc mount forms part of the mechanism that
delivers the depth consistency. The sharing of the torsional loads between
rows of
transverse members minimizes the risk of, if not ensures that, no disc height
position
is overly exaggerated when compensating for vertical height changes in the
terrain.
If a tubular member of similar dimensions was employed instead of an open
member
such as open member 42, so that mount 142 were unable to substantially rotate
or
flex the open member 42, disks 144 may engage with the surface 16 at greater
and
possibly undesirable depths below surface 16 in a localized area, when the
disks
144 pass over or through a mound or elevated contour of the surface 16.
In some embodiments, a combination of the rotational flexibility of the
flanges of the
open members about the longitudinal axes when placed under torque (such as
changes in terrain encountered by a wheel assembly or by forces acting on
mounts
of the ground engagers 140) and the pivotal connections referenced above
between
34
CA 2971616 2017-06-21
the frame sections 18A/18B and 18A/18C and their adjacent open members, may
facilitate the ground engagers being held at generally constant depths across
all of
the open members in each of the rows 20 and 22.
As shown in Figure 1, each of the open members may have a plurality of ground
engagers 140 in front and rear rows 120, 122 coupled to lower opposed flanges
of
respective open structural members. For example, referring to the open member
42
in rear row 22 of frame section 18C, a plurality of pairs of ground engagers
140 are
coupled to the opposed lower flanges 60 and 62 of open member 42. In some
embodiments, ground engagers 140 coupled to the lower flanges 60 and 62 may,
when the ground engagers encounter a change in contour of the surface 16,
exert a
combined torque to the open member 42 about the longitudinal axis 150. This
combined torque applied by the ground engagers 140 on the open member 42 may
facilitate flexing of the open member 42 to facilitate the ground engagers 140
closely
follow contours in the surface 16.
Referring to Figures 2, 2A, 2B, and 4, mount 142 may include features which
may
facilitate a strong and stable connection to open member 42 and/or may
facilitate
flexing of open member 42. The components of mount 142 may be made from one
or more suitable materials such as A36 mild steel.
In addition to horizontally and longitudinally extending plate 176, side
plates 158a,
158b with respective guides 172 and 170, as well as vertical plate 159, mount
142
may include a first flange coupler 162 configured for engaging with flange 60
and a
second flange coupler 164 also configured for engaging with flange 60. Flange
couplers 162, 164 may be made of any suitable material such as for example A36
mild steel.
Referring in particular to Figures 2A, 2B and 4, flange coupler 162 includes
flange
receiving guide 180 having flange receiving surface 184a that defines a
narrowing
flange securing recess for receiving the flange 60. Flange coupler 162 may
also
CA 2971616 2017-06-21
include a tubular cylindrical portion 181a which may have an axially extending
cylindrical passageway and which may be interconnected (such as by welding) to
receiving guide 180.
Similarly, flange coupler 164 includes flange receiving guide 188 having
flange
receiving surface 184b that also defines a narrowing flange securing recess
for
receiving the flange 60. Flange coupler 164 may also include a tubular
cylindrical
portion 181b which may have an axially extending cylindrical passageway and
which
may be interconnected (such as by welding) to receiving guide 182.
Receiving guides 170 and 172 of side plates 158a, 158b also have flange
receiving
surfaces 174 175 that define a narrowing flange securing recess for receiving
the
flange 62. Upper flange receiving surfaces 174 and 175 and a portion of plate
surface 176a may together define narrowing flange securing recesses for
receiving
flange 62.
Referring particularly to Figures 4 and 4C, mount 142 is shown in a
disassembled
view, disconnected from open member 42 and flange couplers 162 and 164.
Associated with mount 142 there may also be nuts 166a, 166b and corresponding
threaded bolts 168a, 168b which may link the first flange coupler 162 and the
second flange coupler 164 to the main body of mount 142 by virtue of
cylindrical
members 71a, 71b. Bolts 168a, 168b may be received though respective axially
aligned passageways in cylindrical members 71a, 181a, and axially aligned
passageways 71b, 181b with respective nuts 166a, 166b secured to the ends of
the
respective bolts 168a, 168b. First and second flange couplers 162, 164 may be
drawn together when nuts 166a, 166b are tightened on respective bolts 168a,
168b.
Nuts 166a, 166b and corresponding bolts 168a, 168b may thus act as tighteners
for
mount 142 such that the distance between the heads of bolts 168a, 168b and
respective nuts 166a, 166b may be varied by loosening or tightening the nuts
166a,
166b on the respective bolts 168a, 168b. Bolts 168a, 168b may for example be
3/4
inch grade 8 bolts and be secured with C-lock nuts 166a, 166b.
36
CA 2971616 2017-06-21
Wedge devices 192 and 194 may also be provided and be operable to be disposed
between flange receiving guides 170 and 172 of mount 142, and flange 62, as
shown in Figure 2. Flange receiving guides 170 and 172 may be made from a high
strength material, such as, for example, heavy plate steel having a thickness
of
about 1/2 inch. Wedge devices 192, 194 may be high strength cast steel and may
be
designed of a shape and strength to bite into mild steel of which flange
receiving
guides 180, 182 maybe formed. This may provide for secure, non-shifting
connections.
With particular reference to Figures 2A and 5, flange receiving guides 180 and
182,
having recesses with respective flange receiving surfaces 184a and 184b for
receiving flange 60, may also include respective wedge devices 196 and 198
operable to be disposed between the flange receiving guides 180 and 182 and
.. flange 60, as shown in Figure 2. The flange receiving guides 180 and 182
and the
wedge devices 196 and 198 may have generally similar features to the flange
receiving guides 170 and 172 and the wedge devices 192 and 194.
In various embodiments, flange receiving guides 170, 172, 180, and 182 may
have a
high level of strength in the horizontal direction when the flange receiving
guides are
drawn together to urge the flanges 60, 62 of open member 42 into the flange
securing recesses. Wedge devices 192, 194, 196, and 198 may also provide a
significant vertical force which allows the mount 142 to act as a solid clamp
that
does not slide under load. Significant side loads may be exerted on the mount
142
when the disk 144 is engaged with the surface 16, for example, by engaging
with
soil defining the surface 16.
Referring now to Figure 4C, flange couplers 162 and 164 and respective wedge
devices 196 and 198 are shown in more detail. Wedge devices 196 and 198 of
flange couplers 162, 164 include respective guide engaging surfaces 220 and
222
which are angled outwardly in an X-direction toward flange 60 and which are
37
CA 2971616 2017-06-21
operable to be engaged with the flange receiving guides 180 and 182, as shown
in
Figure 2. Wedges devices 196 and 198 also include lower, flange engaging
surfaces 230 and 232 respectively which are operable to engage with the flange
60,
as shown in Figure 2.
In various embodiments, the guide engaging surfaces 220 and 222 may be angled
relative to the flange engaging surfaces 230 and 232. For example, in various
embodiments, the guide engaging surfaces 220 and 222 may be at an angle of
about 15 degrees relative to the flange engaging surfaces 230 and 232.
The angle between the flange engaging surfaces 230 and 232 and the guide
engaging surfaces 220 and 222 may facilitate the wedge devices adding vertical
forces to the faces of the flange 60 when the flange receiving guides 180 and
182
are urged towards the flange 60. In some embodiments, for example, the
vertical
force facilitated by wedges devices 196 and 198 may be about 4 times more
force
on the flange 60 than may be achieved without the wedges 196 and 198 and using
flange receiving guides alone.
Referring still to Figures 4C and 4M, wedge devices 220 and 222 may have a
width
greater than a width of the flange receiving guides 180 and 182. For example,
referring to the flange receiving guide 180 and wedge device 196, wedge 196
may
have a width Z1 that is greater than a width Z2 of the flange receiving guide
180.
By providing width Z1 of wedge device 196 being greater than width Z2 of
flange
receiving guide 180, this may facilitate a surface area defined by the flange
engaging surface 230 being greater than a surface area of the flange receiving
surface 184 of the flange receiving guide 180. This greater surface area may
facilitate a greater and more stable force being applied to the flange 60 by
the
wedge 196 relative to using the flange receiving guide 180 alone to engage
with the
flange 60. The angled guide surfaces 220, 222 provide the clamp in co-
operation
with the surfaces 184a, 184. The actual wedge devices 196, 198 may have a
width
that is about three times wider than the surfaces 220, 222.
38
CA 2971616 2017-06-21
In some embodiments, the width Z2 of the flange receiving guide 180 may be
about
1/2 inch, for example. In some embodiments, the width Z1 of the wedge 196 may
be
about 1 1/2 inches, for example.
Still referring to Figure 4C and 4M, in various embodiments, wedges devices
196
and 198 may include vertically and longitudinally extending grooves 260 and
262 for
receiving and holding the flange receiving guides 180 and 182, the grooves 260
and
262 including the angled guide engaging surfaces 220 and 222 of wedge devices
196 and 198. In various embodiments, the side walls forming grooves 260 and
262
may facilitate wedge devices 196, 198 being held between the respective flange
receiving guides 180 and 182 and flange 60, without sliding out from under the
flange receiving guides 180 and 182. Grooves 260 and 262 may be defined in
part
by side walls of wedge devices 196, 198 which retain the wedge devices between
flange receiving guides 180 and 182 and flange 60.
Wedge devices 196, 198 may include respective projections 270 and 272 which
may
act as stoppers to engage an edge of the flange 60. Projections 270, 272 may
restrict sliding movement of wedged devices 196, 198 towards web 68 of the
open
member 42 (Figure 2). This restriction of sliding movement may facilitate
wedge
devices 196, 198 being held in place while the flange receiving guides 170,
180 and
172, 182 are drawn together during tightening of mount 142 on flanges 60, 62
of
open member 42.
Referring to Figure 4, flange receiving guides 170 and 172 and the
corresponding
wedge devices 192 and 194 may include the same or substantially similar
features
to the flange receiving guides 180, 182 and the respective wedges 196, 198.
Wedge devices 196, 198 maybe made from high strength steel and may be
designed with such a configuration and strength that when used, their surfaces
which interface with guides 180, 182 with the lower flanges of the open
structural
39
CA 2971616 2017-06-21
members such as open member 42 (the latter being made from relatively softer
material such as mild steel), that the surfaces of the wedge devices 196, 198
will bite
/ provide a small impression into the surface of the softer material. This co-
operates
with the other features of the wedge devices 196, 198 to provide for an
enhanced,
secure and non-lateral shifting connection.
Referring to Figures 1, 1A and 6, as indicated above, frame 18 of tillage
apparatus
includes transversely oriented (Direction Z) open members 28, 30, and 32 in
front
row 20 and transversely oriented open members 38, 40, and 42 in the rear row
22.
10 Frame 18 of tillage apparatus 10 may also include longitudinally
oriented (direction X
in Figure 1) row open structural members 800, 802, 804, 806, 808, 810, 812,
814,
and 816 which inter-connect the open members of rows of open members 20 and
22. For example, in left side frame section 18B, open members 800, 802, and
804
are connected to front and rear open members 30 and 40; in central frame
section
18A, open members 806, 808, and 810 are connected to the open members 28 and
38; and in in right side frame section 18C, open members 812, 814, and 816 are
connected to open members 32 and 42. Open members 800, 806, 810, and 816
may have generally C-shaped cross sections; open members 802, 804, 812, 814
may be generally I-beam shaped members; and open member 808 may have a
generally inverted T shaped cross section which may be made for example by
joining two generally L-shaped channel members in back to back configuration
to
from a generally inverted T-shaped composite member.
Generally C-shaped open members 800, 806, that form part of left frame section
18B may have their channels directed outwardly from the central frame section
18A.
Similarly, generally C-shaped open members 810, 816 that form part of right
frame
section 18C may have their channels directed outwardly from the central frame
section 18A, in an opposite transverse direction to the channels of open
members
800, 806. Open channel members 800, 806, 810, and 816 are adapted for
supporting rear wheel supports 820, 822, 824 and 826 as described hereinafter.
CA 2971616 2017-06-21
The structural open members 800, 802, 804, 806, 808, 810, 812, 814, and 816
may
be made from one or more suitable materials such as A36 mild steel.
With reference now to Figures 1, 1A, 1B, lE and 6, representative examples of
how
the interconnection between the open channel members 800, 806, 810, and 816
may be made to the corresponding transversely oriented open members of front
row
of open members 20 and rear row of open members 22. In Figure 1A, a
representative example connection between open member 42 and open member
816 is illustrated. Open member 816 may have an upper flange 816c, a central
web
1() 816b and a lower flange 816a. Web 816b may have a cutout portion 816d
thorough
which open member 42 may be extend through. Open member 816 may also have
an end plate 816e oriented generally vertically and transversely (directions Y
and Z).
Open member 816 may also have a support plate 8161 that is also oriented
generally vertically and transversely and may extend between upper flange 816c
and lower flange 816a within the channel. Support plate 8161 and end plate
816e
may be connected to upper flange 816b, web 816b and lower flange 816a of open
member 816 by for example welding.
Extending within the channel of open member 816 between support plate 816f and
end plate 816e may be a generally L-shaped bracket 817 which may be bolted
with
nuts/bolts 839 through end plates to support plate 8161 and end plate 816e.
One leg
of bracket 817 may be bolted with bolts 819 to web portion 816b of open member
816. The bolts 819 may pass through web 816b and through a rear bracket 821
positioned against a rear surface of web 816b and be secured with nuts [See in
Figure 1C, corresponding bracket 821 and bolts 819 associated with connecting
open member 800 to open member 40 in the same manner; and see in Figure 1E
the corresponding connection between longitudinal open member 810 and
transverse open member 38].
The other, bottom leg of bracket 817 may be bolted with bolts/nuts 821 to the
upper
flanges 64 and 66 of open member 42.
41
CA 2971616 2017-06-21
Additionally, lower flanges 60, 62 of open member 42 may be bolted to lower
flange
816a of open member 816.
There are generally no fixed connections to the web portions of the transverse
open
members such as open members 42 such that the transverse. The top and bottom
flanges of each transverse structural member such as open member 42 is
connected at the top and bottom flanges of the longitudinal members such as
members 816. Additionally, the transverse open members such as open member 42
are generally located at the end region / area of each longitudinal members.
This
combination still allows the longitudinal members to twist as may be required,
because the web portions of the longitudinal members are not secured to other
members along their lengths and thus there are no such members along their
length
to impede such twisting.
With reference now to Figures 1, 6 and 1D, a representative example of how the
interconnection between the intermediate open channel members 802, 804, 812,
and 814 may be made to the corresponding transversely oriented open members of
front row of open members 20 and rear row of open members 22. In Figure 10, a
representative example connection between open member 32 and open member
814 is illustrated. Open member 814 may have upper flanges 814a, a central web
814b and lower flanges 814c. Web 814b may have a cutout portion 814d thorough
which open member 32 may be extend through. Bolts 823 may pass through upper
flanges 814a and through upper flanges 32a of open member 32 and may be
secured by nuts (not shown in Figure 1D). Bolts 825 may pass through lower
flanges 32c of open member 32 and lower flanges 814c of open member 814 and
may be secured by nuts (not shown in Figure 1D). In this way, open channel
members 802, 804, 812, and 814 may be connected to corresponding transversely
oriented open members of front row of open members 20 and rear row of open
members 22 with only upper and lower flange connections. By only providing for
flange to flange connections between these open members of each frame section,
42
CA 2971616 2017-06-21
the frame sections are able to twist and deflect more easily than if there
were
connections between web portions of the members. This construction can assist
in
maintaining a relatively high degree of flexibility in the frame sections 18A,
18B and
18C and avoids the creation of "boxed" sections with limited flexibility and
which may
encounter enhanced levels of stresses from loads of multiple sizes and
directions
making them prone to cracking and failure. The neutral axis webs are not
constrained.
Referring now particularly to Figures 1A, 6, 6A, and 6B, frame 18 may also
include
angled, open, load distribution members 840, 842, 844, and 846. Load
distribution
member 840 in left side frame section 18B may be fixedly connected to
transverse
open members 30 and 40, as well as to transverse open members 800, 802, 804.
Similarly, load distribution member 846 in right side frame section 18C may be
fixedly connected to transverse open members 32 and 42, as well as to
transverse
open members 812, 814, 816. The rigid connections may be made across and to
the flange members of the respective open members. Each of the open member
load distribution members 840 and 846 may extend at an angle relative to each
of
the open members to which they are connected. Referring to Figure 6, the open
member load distribution member 840 extends at an angle to the open members 30
and 40. By way of example, the angle may be between about 30 and 70 degrees,
such as about 40 degrees. The open member load distribution member 846 may be
generally similar to the member 840, but mirrored.
With particular reference to Figures 6A and 6B, a front end portion of load
distribution member 846 may be fixedly connected with bolts to a leg 831a of
an
angled connector plate 831. The other leg 831b of connector plate 831 may be
connected with blots 833 which pass through leg 831 b as well as flange 32a of
open
member 32 and flange 812a of open member 812.
A similar connection may be made between front end portion of load
distribution
member 846 and open member 816.
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CA 2971616 2017-06-21
Where load distribution member 846 crosses open member 814, it may be secured
with bolts 835 (Figure 6A) to the top flange of open member 814. Similarly
where
load distribution member 840 crosses open member 802, it may be secured with
bolts) to the top flange of open member 802.
With reference to Figure 1C, the rear end portion of load distribution member
840
may be secured with a bolt 843 that passes into top flange 40a of open member
40
and is secured with a nut (not shown). A rear end of load distribution member
840
may be received through an opening in bracket 821 and abut the rear surface of
web
portion of open member 800. This may reduce shear forces exerted on bolts 843
and reduce twisting at the bolt locations, thus assisting in maintaining tight
connections.
.. Similarly, the rear end portion of load distribution member 846 may be
secured with
a bolt that passes into top flange 42a of open member 402 and is secured with
a nut.
A rear end of load distribution member 846 may be received through an opening
in
bracket like bracket 821 and abut the rear surface of web portion of open
member
816.
Load distribution members 840 assists in distributing forces acting on the top
flanges
of each of the open members 32, 42 and particularly the longitudinal open
members
812, 814, 816 in right frame section 18C. Similarly, load distribution member
846
assists in distributing forces acting on the top flanges of each of the open
members
30, 40 and particularly the longitudinal open members 800, 802, 804 in left
frame
section 18B.
With reference to Figure 6D, 6E and 6F, the lower flanges 808b of central open
member 808 may be bolted at a forward end to top flange 28a of central
transverse
open member 28. The lower flanges 808b at a rearward end of open member 808
may be bolted to a top flange 38a of central transverse open member 38.
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CA 2971616 2017-06-21
Load distribution members 842 and 844, may function to provide a structure
that
may be fixedly connected at forward ends to a common, transverse plate 837
which
is itself bolted to the lower flange 28b of transverse open member 28a. Load
distribution members 842 and 844 extend at angles to open members 28 and 38.
By way of example, the angles that open members 842 and 844 extend at relative
to
open members 28 and 38 may be between about 30 and 70 degrees, such as for
example 60 degrees. In doing so open members 842 and 844 extend from corner to
corner (middle front to longitudinal rear at angle) to provide cross bracing
to keep
frame section 18A generally square/rectangular in shape.
The use of the upper diagonal load distribution members 840, 842, 844, and 846
(see Figure 1) prevents each of the frame sections 18A, 18B and 18C from
trapezoiding (ie. collapsing) under heavy loading, which at the same time
allowing
the frame sections to bow while the tillage apparatus 10 is operating over
uneven
ground surface 16. This configuration provides stability to the frame sections
18A,
18B and 18C when loaded, both in normal forward movement during operation (eg.
arrow 14 in Figure 1) and in a reverse direction (as moving the tillage
apparatus in
the opposite direction while the ground engagers 140 are penetrated in the
ground
may sometimes be required. This may result in a reduction in shear forces
acting on
the bolts connecting members.
It should be noted that many components of frame sections 18A, 18B and 18C as
described herein are configured to be bolted together. This allows the tillage
apparatus to be more easily transported/delivered as a kit to an at least an
initial
user/customer location where it can be assembled relatively easily, without
the need
for a large amount of on-site welding at the user/customer.
With reference again to Figures 1A and 6, tillage apparatus 10 may include
variable
height rear wheeled supports 820, 822, 824, and 826 and the C-shaped cross
CA 2971616 2017-06-21
sections of the open members 800, 806, 810, and 816 may facilitate wheeled
supports 820, 822, 824, and 826 being mounted to respective open members 800,
806, 810, and 816, through openings in upper and lower flanges of these open
members.
Tillage apparatus 10 also includes front variable height wheeled supports 828,
830,
832, and 834 connected to the open members 800, 806, 810, and 816 respectively
generally at forward ends of the open members.
Wheeled supports 820-834 may act as surface following supports and may
generally
control the relative height/distance of frame 18, and frame sections 18A, 18B
and
180 from ground surface 16. Some or all of wheeled supports 820-834 may each
be associated with one or more hydraulic cylinders which are configured to
vary the
height of the frame 18 and its frame sections 18A-C, as described in further
detail
below.
Referring back to Figure 1, in operation, tillage apparatus 10 may be moved
across
the surface 16 in the direction shown by the arrow 14 while supported by the
wheeled supports 820-834 (see Figure 6) with wheels 197 and the ground
engagers
140 may condition the surface 16 as they are pulled across the surface. In
various
embodiments, as described above, the pivotal connectors 80, 82, 84, and 86 may
facilitate differences in the orientation of adjacent open members such that
each of
the open members 28, 30, 32, 38, 40, and 42 of respective fame sections 18A-
180
extends generally parallel or tangential to a contour of the surface below the
open
member. The ground engagers 140 may, in response to engaging the surface 16,
flex one more of the open members 28, 30, and 32, and 38, 40, and 42 at least
rotationally to facilitate the ground engagers following specific contours of
the
surface 16. This flexibility may be provided at least in part by the open
member
construction of the open members 28, 30, 32, 38, 40, and 42, and of the open
members 800, 802, 804, 806, 808, 810, 812, 814 and 816, and the way in which
they are interconnected. The flexibility may also be provided at least in part
by the
46
CA 2971616 2017-06-21
way that mount 142 of the ground engagers 140 are coupled to the lower flanges
of
the open members 28, 30, 32, 38, 40, and 42.
In various embodiments, the pivotal connections between the open members
together with the flexibility of the open members in response to force or
torque
applied by the ground engagers may facilitate each ground engager maintaining
a
precise and consistent level or depth of engagement with the surface 16. In
various
applications, such a precise and consistent level of engagement with the
surface 16
may result in healthy crops and high yields for crops grown in soil defining
the
surface 16. Precise and consistent levels of engagement may reduce wear and
tear
on machines used during tillage.
Referring still to Figure 1, in various embodiments, the tillage apparatus 10
may
include actuators 860, 862, 864, and 866 which are configured to raise or
lower
outer portions of the tillage apparatus 10 to reduce a width of the tillage
apparatus
during transport, for example. In the embodiment shown, the actuator 860 is
coupled to the open members 30 and 28, the actuator 862 is coupled to the open
members 28 and 32, the actuator 864 is coupled to the open members 38 and 40,
and the actuator 866 is coupled to the open members 38 and 42. In operation,
the
actuators 860-866 may be retracted to raise the open members 30, 32, 40, and
42
such that the open members 30, 32, 40 and 42 pivot about the pivotal
connectors
80, 82, 84, and 86. In various embodiments, the actuators 860-866 may be
actuators which are configured to lift and hold substantial weight, such as,
for
example hydraulic actuators.
With reference to Figure 15A, apparatus 10 is shown in a deployed operational
orientation. In Figure 15B, apparatus 10 is shown in a raised orientation that
may be
suitable for storage and/or transportation.
The height of each of longitudinally oriented open members 800, 806, 810, and
816
above ground surface 16 may be controlled and thus the height of each of the
frame
47
CA 2971616 2017-06-21
sections 18A, 18B and 18C may be controlled. With reference to Figures 12 to
121,
a representative example of the rear wheeled supports, rear wheeled support
832, is
illustrated and may include a pair of transversely spaced apart rear wheels
197a
supported at one lower end of a leg member 853. The wheels 197a may be
attached to an axle/hub mechanism 857 (Figure 12C) that is connected to leg
member 853 in such a manner as to allow for free rotation of the wheels about
the
axis of the axle/hub 857. Leg member 853 may be generally rectangular in cross
section and tubular and may be receivable for axial movement relative to a
supporting hollow tubular support 854.
Axle/hub mechanism 157 may include a longitudinally oriented shaft 891 that
allows
wheels 197a to pivot transversely about the shaft. The main wheel axle may be
aligned with the center section 18A of tillage frame 18. This allow the mass
of the
frame to be distributed between (eg. equally shared on) both wheels 197a when
moving on uneven ground surface. This may be helpful or even necessary when
the
apparatus 10 is in the transport orientation (Figure 15B) and moving on non-
flat
surfaces such as crowned roads. This may avoid the maximum tire pressures for
wheels 197a being exceeded. It should be noted that the rotation is bi-
directional.
With additional reference to Figures 1B, 12D, 12E tubular support 854 may be
mounted so as to extend from a location above open member 816, through an
opening 865 in upper flange 816c of open member 816, within the channel of
open
member 816 next to web 816b, and through and opening 863 in lower flange 816a
to a location beneath lower flange 816a. Tubular support 854 may be fully
welded to
lower flange 816a to provide for a rigid connection at that location. However,
the
connection between the upper flange 816c and the tubular support 854 may be
floating, such that there is a limited degree/amount of horizontal movement of
tubular support 854 relative to upper flange 816c, although vertical movement
is
substantially prevented (eg. through the fixed connection at the lower flange
816a).
A control ring 861 (Figure 12E) may be positioned over opening 863 of upper
flange
816c may be fixedly attached (such as by welding) to tubular support 864.
Tubular
48
CA 2971616 2017-06-21
support 854 may be received through the generally square opening 867 in
control
ring 861. Control ring 861 may be held within a support plate 869 (Figure
12D).
Support plate 869 may be secured such as by welding, to the upper surface of
upper
flange 816c and lay flat thereon. Control ring 861 may be configured to guide
and
support tubular support 854. The control ring 861 may guide tubular support
854 at
the required angle. Another opening 878 in lower flange 816a is provided to
permit
a hydraulic cylinder 855 (Figure 12) to be received there through.
Still with particular reference to Figure 120, a bracket 852 may be mounted
such as
by welding to tubular support 854. Bracket 852 may have a pair of spaced arms
851
which may be secured such as by welding to outer surfaces of tubular support
854.
Tubular support 854 may be only secured such as by welding to lower flange
816a.
Tubular support 854 may thus be constrained in its movement horizontally and
rotationally, to move with control ring 861. But upper flange 816c can twist
to some
extent relative to tubular support 854.
A two way acting hydraulic cylinder 855 may be interposed between open member
816 and axle/hub 857. Hydraulic cylinder 855 may have an upper end
interconnected to bracket 852 which has describe above is also secured to
tubular
support 854. Hydraulic cylinder 855 may have an extendible piston rod 856. The
end of piston rod 856 may be connected to axle/hub 857. The operation of
hydraulic
cylinder 855 may be controlled by an actuator and/or controller (as described
further
hereinafter), which may control valves in a hydraulic fluid circuit to control
the flow of
pressurized hydraulic fluid to and from hydraulic cylinder 855. By extending
piston
rod 856, the distance between wheel 197a and the open member 816 may be
increased, and by retracting piston rod 856, the distance between wheel 197a
and
the open member 816 may be decreased.
.. Secured to opposed sides of web portion 816b of open member 816 may be a
pair
of pulley devices 858 (only one of which is visible in Figure 12). One or more
cables
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CA 2971616 2017-06-21
(such as a single continuous cable 859) may be secured around an arcuate guide
893 which may be fixedly mounted to axle/hub 857 associated with wheels 197a.
Cable 859 may extend around arcuate guide 893 of axle/hub 857 (see Figure 12C)
upwards on both sides to transversely opposed rearward pulley devices 858 and
then follow curved paths around pulley devices 858 on opposite sides of web
816b
of open member 816 and extend to a pair of corresponding opposed forward
pulley
devices 874 associated with front wheeled support 834 (see Figure 12B).
With reference to Figures 12, 12A, 12B, 12F and 12G, a representative example
of
the front wheeled supports, front wheeled support 834 is also illustrated and
may
include a single caster wheel 197b supported at one end of a leg member 871
which
may be attached to an axle/hub mechanism 872 in such a manner as to allow for
free rotation of the wheel about the axis of the axle/ hub 872. In
other
embodimentsõ where for example loading may be of a magnitude to require it,
front
wheeled support 834 may include two, side by side, caster wheels. Leg member
873 may be generally rectangular in cross section and tubular and may be
connected at a top end portion to a cylindrical rotatable support post 873.
Post 873
may be receivable for axial movement relative to a supporting hollow
cylindrical
tubular support 877. Post 873 may also be rotatable about a longitudinal axis
of
tubular support 877. Tubular support 877 may be mounted to a forward end
portion
of a mount 878.
Pulley devices 874 have a common transverse axle for rotation and may be
mounted on a common shaft 899 (Figure 12F). Shaft 899 may be mounted to a
lever
arm device 875. Lever arm device 875 maybe mounted to mounting block 878 for
pivoting movement about a pivot location 898. An end arm portion of lever arm
device 875 may be pivotally connected to an end of a piston rod of a two way
acting
hydraulic cylinder 876 that is also mounted to mounting block 878. Hydraulic
cylinder
876 may have an extendible piston rod 997. The operation of hydraulic cylinder
876
may be controlled by an actuator and/or controller which may control valves in
a
hydraulic fluid circuit to control the flow of pressurized hydraulic fluid to
and from
CA 2971616 2017-06-21
hydraulic cylinder 876. By extending or retracting piston rod 997 of hydraulic
cylinder 876, lever arm 875 may be pivoted about pivot location 898. The shaft
899
connecting pulley device 874 may move within a slot 999 in mounting block 878.
By
this movement, the position of pulley devices 874 can be altered. By moving
the
position of pulley devices 874, the path distance for cable 859 between the
pulley
devices 874 and trunnion device 879 can be increased or decreased. An increase
in
this distance will cause the front wheel 197b to be moved closer to frame 18 -
thus
lowering the frame and causing the front row of ground engagers 140 to
penetrate
into the ground more. A decrease in this distance between the pulley devices
874
and trunnion device 879 will cause the front wheel 197b to be moved further
away
from frame 18 - thus raising the frame 18 relative to the wheel and the ground
surface 16 and causing the front row of ground engagers 140 to penetrate into
the
ground to a lesser extent.
The result is that each of the front castor wheels 197a of front wheel
assemblies
828, 830, 832 and 834 can be independently adjusted independently of the main
frame height setting that is controlled by operation of each of the main
hydraulic
cylinders 855 (Figure 12).
As noted above, continuous cable 859 may extend from axle/hub 857 upwards to
pulley devices 858 and then follow a curved path around pulley devices 858 and
extend to forward pulley devices 874. The opposite sides of cable 859 may
follow a
path upwards and are affixed to cable trunnion 879 located at the upper end of
post
873. Opposed sides of cable 859 pass over and meet at the cable trunnion 879.
Thus the continuous path of cable 859 is completed.
Isolated views of cable trunnion 879 are shown in Figures 12H and 121. Cable
trunnion 879 includes an upper arcuate guide member 896 which will be held at
a
fixed angle (ie. top down rotational angle) by the tension in cable 859 that
passes
over arcuate guide member 896 has runs vertically down each side thereof. This
arrangement will keep cable trunnion 879 from rotating angular about a
vertical
51
CA 2971616 2017-06-21
axisY1 (Figure 12H). Trunnion 879 will be mounted on a thrust bearing device
895
(Figure 121) the inner race 897 of which is attached to a bolt 894. Bolt 894
is fixedly
attached to the top of rotatable wheel post 873. Bolt 894 will thus be capable
of
rotating with post 873 about a generally vertical / upwardly directed axis
within thrust
bearing 895. This allows post 873, leg member 871 and castor wheel 197b to
rotate
about a generally vertical axis, without interfering with the positioning of
cable 859.
By extending piston rod 876 of hydraulic cylinder 876, the distance between
pulley
devices 874 and cap device 879 can be altered. Post 873 may be rotatable
relative
to end cap device 859 such that post 873 rotates about a longitudinal axis.
But when
post 873 rotates, the cables 879 attached to end cap device 879 are not
rotated.
It should be noted that for sensing the castor angle, a sensor may be attached
to
arcuate cable guide 896 so that the sensors rotational centerline will be in
line with
the rotational centerline of bolt 894. A rotating part of the sensor (eg.
sensor arm)
may be keyed / attached to the centerline of bolt 894 for rotation with bolt
894, wheel
post 873 and front castor wheel 197b.
Mounting block 878 may have a rear portion connected to an end of open member
816 at a three point connection, with a pair of transversely spaced lower
connection
locations 892 and s single upper connection location 891. This three point
connection assists in ensuring that the castor wheels 197b remain
substantially
vertical even when main frame 18 and its members such as open members like
member 816 are twisting during operation.
In operation of tillage device 10, for example when tillage device is about to
commence tilling of the ground material beneath ground surface 16, it may be
desirable to lower frame 18 and including the front row of open members 20 and
rear row of open members 22 an equal amount relative to the ground surface 16.
This may cause front row 120 and rear row 122 of discs 122 to penetrate into
the
ground material beneath surface 16 an equal distance. It may be appreciated
that in
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many typical operating environments, the overall weight of the frame 18,
mounts 142
and discs 144 will be considerable and will typically cause the discs 144 to
penetrate
into the ground to a desired depth if the frame 18 is lowered relative to
wheel
supports 820 to 834. In other words, within typically operating depths, the
contact
surface areas of the discs 144 with the ground material beneath surface 16
will not
provide sufficient upward forces to alone counteract the force of gravity
acting on
frame 18, mounts 142 and discs 144. The front wheel supports 828, 830, 832 and
834, and rear wheeled supports 820, 822, 824 and 826, are required to support
the
weight of these components above surface 16.
Assuming the frame 18 starts from a generally horizontally level manner, both
longitudinally and transversely to lower the frame 18 and the mounts 142 and
discs
144 attached thereto, in a level manner, piston rod 856 of hydraulic cylinder
855 of
each of rear wheel supports 820, 822, 824 and 826 may be retracted. This will
cause corresponding pairs of wheels 197a to move up relative to the frame 18
including respective open members 816, 810, 806 and 800. This movement will
cause in respect of each rear wheel supports 820, 822, 824 and 826, the
distance
of the respective cables 859 between their respective axles/hubs 857 to
shorten,
with the result is that the distance between pulleys 874 on mounts 878 and
trunnions
879 for each of front wheel supports 828, 830, 832 and 834 will extend. This
will
create a corresponding shortening of the distance between caster wheels 197b
and
mounting blocks 878 for each front wheel support 828, 830, 832 and 834 and
respective open members such as open member 816, 810, 806 and 800. The result
is that the open members 816, 810, 806 and 800 will move towards their
respective
front wheels 197a and rear wheels 197b a substantially equal amount resulting
in a
level movement downwards and an equal movement of front row 120 of ground
engagers and rear row 122 of ground engagers (eg. discs 144) across the
entirety of
frame 18.
To raise frame 18 and discs 144 attached thereto in a level manner, piston rod
856
of hydraulic cylinder 855 of each of rear wheel supports 820, 822, 824 and
826, may
53
CA 2971616 2017-06-21
be extended. This will cause corresponding rear pair of wheels 197a to move
down
relative to frame 18 including open members 816, 810, 806 and 800. This
movement will cause the distance of cables 859 between respective axles/hubs
857
of each rear wheel supports 820, 822, 824 and 826 to lengthen, with the result
is
that the distance between pulleys 874 on mounting blocks 878 and trunnions 879
of
each front wheel supports 828, 830, 832 and 834 will be reduced. This will
create a
corresponding lengthening of the distance between wheel 197b and mount 878 for
each front wheel supports 828, 830, 832 and 834 and respective open members
816, 810, 806 and 800. The result is that such as open members 816, 810, 806
and
800 will move towards respective rear wheels 197a and front caster wheels 197b
a
substantially equal amount resulting in a level movement upwards and an equal
movement of front row 120 of ground engagers and rear row 122 of ground
engagers (eg. discs 144).
Referring to Figures 1, 1A and 6, the forward row of ground engagers 140 may
be
disposed at an angle such that when the first row of ground engagers 140
engage
with the ground material beneath surface 16, a force acting in a direction
transversely (direction Z) right to the direction of travel 14 of tillage
apparatus 10 is
exerted on the ground engagers which is transmitted to frame 18. Conversely,
the
rear row of ground engagers 140 may be disposed at an angle such that when the
ground engagers engage the ground material beneath surface 16, a force acting
in
a direction transversely (direction Z) left to the direction of travel 14 of
tillage
apparatus 10 is exerted on the ground engagers which is transmitted to frame
18.
In some situations, when the forward and rearward set of ground engagers 140
and
122 engage with the surface 16 at generally the same depth, transverse forces
exerted by the surface 16 on the forward and rear sets of ground engagers 140
and
122 may offset each other, and the transverse forces may in some circumstances
be
substantially the same magnitude and opposite in direction, such that the
tillage
apparatus 10 keeps the generally square orientation relative to the propulsion
unit
54
CA 2971616 2017-06-21
12 shown in Figure 1 and travels substantially in the direction 14 with
propulsion unit
12 across the surface 16.
However, there may be situations where the ground engagers 140 penetrating the
ground material may not provide transverse forces that are equal in the
opposite
transverse directions, which may rotate tillage apparatus 10 into a skewed or
skidding orientation, relative to the direction of travel 14 and propulsion
unit 12.
For example, even if the surface 16 is substantially level, and the front row
20 of
ground engagers 140 and the rear row 22 of ground engagers 140 penetrate to
substantially the same depth, the front row of ground engagers 140 may have a
more difficult task in breaking up the ground material as they engage the
ground
material before the rear row of ground engagers 140. The result may be that
the
front row of ground engagers 140 have a greater transverse force exerted on
them
in a right transverse direction, than the transverse force exerted on the rear
row of
ground engagers 140 exerted on them in a left transverse direction. This force
imbalance may rotate tillage apparatus 10 into a skewed or skidding
orientation,
relative to the direction of travel 14 and propulsion unit 12.
In another type of situation, if and when some or all of ground engagers of
the
forward and rear set of ground engagers 140 and 122 engage with the ground
material beneath surface 16 at different depths, the transverse forces acting
on
tillage apparatus 10 as a result of the ground engagers penetrating the ground
material may not be equal in the opposite transverse directions, which may
rotate
tillage apparatus 10 into a skewed or skidding orientation, relative to the
direction of
travel 14 and propulsion unit 12.
Referring back to Figure 1, as tillage apparatus 10 is pulled across the
surface 16,
the contours of the surface 16 may cause the forward set of ground engagers
140 to
engage the surface 16 more deeply than the rear set of ground engagers 140, or
vice versa.
CA 2971616 2017-06-21
With reference to Figure 5A, a modified left frame section 18B' is shown. For
simplicity, no ground engagers 140 are shown schematically in this Figure 5A,
but it
should be understood that frame section 18B' would also generally have the
features of frame section 18B, including rows 120, 122 of ground engagers 140
including their mounts 142, as shown in Figure 6. A main difference between
frame
section 18B illustrated in for example Figure 6, and frame section 18B' is
that
transverse open member 40' in frame section 18B' is extended laterally
outwards
beyond the furthest lateral extension of open member 30. This permits
additional
ground engagers 140 to be mounted in the extended region of open member 40.
Similarly with reference to Figures 5C and 50, a modified right frame section
18C' is
shown. For simplicity, only a few of ground engagers 140 are shown
schematically in
Figure 50, but it should be understood that frame section 18C' would also
generally
have the same features of frame section 18C, including 120, 122 rows of ground
engagers 140 and their mounts 142, as shown in Figure 6. A main difference
between frame section 18C illustrated in for example Figure 6, and frame
section
18C' is that transverse open member 32' in frame section 18C' has been
extended
laterally outwards beyond the furthest lateral extension of open member 42.
This
permits additional ground engagers 140 to be mounted in the extended region of
open member 32'.
With reference to Figure 5G, the additional ground engagers 144 on the
extensions
of frame sections 18B' and 18C' will assist in maintaining the surface 16 over
which
tillage apparatus 10 passes to remain relatively flat and reduce the
likelihood or
amount of any berm of ground material forming at the intersection of passes in
opposite longitudinal directions of tillage apparatus 10.
With reference to Figures 1, 15B and 18, it an alternate form of disc 244
(which may
be referred to as a "flower" disc due to its resemblance to a flower shape).
Disc 244,
while having the same diameter as discs 144, 144A, may have a gaps or spaces
in
56
CA 2971616 2017-06-21
its radial body that may result in a reduction of in the range of about 40 to
60% of
the body (eg. about 50% reduction). The result is that this disc will only
"throw" /
move about half as much dirt to the side and thus will be less prone to
forming
berms of tilled material after tillage apparatus makes a pass over surface
area. A
disc 244 may be provided at the very end of the rear row of 122 of ground
engagers
140.
Tillage apparatus 10 may be adapted as partly described further below, to
adjust the
relative heights of the front row of ground engagers 140 relative to the rear
row of
ground engagers 140 and thereby modify the relative transverse forces that are
acting upon the frame in opposite directions. The apparatus that facilitates
this
adjustment will now be described.
With reference again to Figures 12, 12A and 12B, as noted above, pulley
devices
874 may be mounted to mounting blocks 878 and may be connected to a lever
device 875. The operation of hydraulic cylinder 876 may be controlled by an
actuator
and/or controller which may control valves in a hydraulic fluid circuit to
control the
flow of pressurized hydraulic fluid to and from hydraulic cylinder 876. By
extending
or retracting piston rod of hydraulic cylinder 876, the position of pulley
devices 874
on each mounting block of each front wheel assembly 820, 822, 824 and 826 can
be
altered. By altering the position of pulley device 874, the path length of
each
respective cable 859 between pulley device 874 and trunnion 879 may be
lengthened or shortened independently of the main height control of the frame
provided by operation of hydraulic cylinders 855. By lengthening the path
length
between pulley devices 874 and trunnions 879, resultant axial movement of post
873
will cause the distance between caster wheels 197b and the respective open
members such as open member 816, will be shortened, thus lowering the open
members and the front side of frame 18, relative to the surface 16. This will
cause
front row of ground engagers 140 to penetrate the ground material to a greater
depth, thus increasing the transverse force in a right transverse direction.
57
CA 2971616 2017-06-21
Similarly, by shortening the path length between pulley devices 874 and
trunnion
879, axial movement of post 873 will cause the distance between caster wheels
197b and the respective open members such as open member 816, will be
lengthened, thus raising the open members and the front side of frame 18,
relative
to the surface 16. This will cause front row of ground engagers 140 to
penetrate the
ground material to a lesser depth, thus decreasing the transverse force in a
right
transverse direction.
The upward and downward movement of the front of the frame 1,8 relative to the
rear
of the frame 18, may be controlled by actuation of hydraulic cylinders 876.
This may
be controlled manually by an operator or by a control system with a suitable
sensing
system that interfaces with a system controller.
With reference now to Figure 13, an embodiment of a control system for tillage
apparatus 10 is shown generally at 1000. The control system 1000 includes a
front
row control system 1002 for controlling a height of the front row of
longitudinally
axially aligned open members 20. The control system 1000 also includes a frame
height control system 1004 for controlling an overall height of the frame 18.
The
front row control system 1002 includes the hydraulic cylinder 876 of the front
wheeled support unit 834 (shown in Figure 12). The front row control system
1002
also includes respective hydraulic cylinders 1006, 1008, and 1010 associated
with
each of the front wheeled support units 828, 830, and 832. The hydraulic
cylinders
876, 1006, 1008, and 1010 are disposed on respective mounts (such as the mount
878 shown in Figure 12) for raising or lowering the respective wheeled support
units
834, 832, 830, and 828 to cause the open members 816, 812, 806, and 800 of the
frame 18 to be raised or lowered to counteract skidding of the tillage
apparatus 10
as described above. Each cylinder has an actuator rod connected to a moveable
piston (for the hydraulic cylinder 1010, the rod is shown at 1012 and the
piston at
1014). The moveable piston 1014 divides the cylinder 1010 into a cap end
chamber
having a cap end hydraulic fluid port 1016 and rod end chamber having a rod
end
hydraulic fluid port 1018. The hydraulic cylinders 876, 1006, 1008 are
similarly
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CA 2971616 2017-06-21
configured in the embodiment shown and are hydraulically connected in series
via a
hydraulic fluid line 1020, which is in fluid communication with the cap end
port 1016.
The line 1020 also couples between the rod end port 1018 and a cap end port of
the
cylinder 1008 and between respective rod end and cap end ports of the
successive
downstream cylinders 1006 and 876. A rod end port 1017 of the cylinder 876 is
coupled to a hydraulic fluid line 1022.
The hydraulic fluid lines 1020 and 1022 are selectively connected to a
pressurized
hydraulic fluid supply line 1024 and a return line 1026 through a
proportionally
controlled directional valve 1028 (shown schematically in Figure 13). The
lines 1024
and 1026 may be coupled via respective quick connect fittings 1034 and 1036 to
a
pressurized hydraulic fluid supply (not shown) on the host propulsion unit 12.
The
directional valve 1028 includes an internal control spool that may be actuated
for
straight-through flow via solenoids 1030 and 1032 to selectively permit fluid
flow
from the supply line 1024 and through the line 1020 to the cap end port 1016
of the
cylinder 1010 and to permit fluid to flow back from the rod end port of the
cylinder
876 via the line 1020 to the return line 1026. Alternatively, the directional
control
valve 1028 may be actuated for cross-flow to selectively permit fluid flow
from the
supply line 1024 and through the line 1022 to the rod end hydraulic fluid port
1017 of
the cylinder 876 and to permit fluid to flow back from the cap end port 1016
of the
cylinder 1010 and via the line 1020 to the fluid return line 1026. The
solenoids 1028
and 1030 are responsive to electrical control signals provided at inputs 1038
and
1040 to cause the internal control spool to move between the straight-through
flow
and cross-flow configurations. For example, the control signal may be a DC
current
that varies over a range between amperages of --/o, 0, and +10, where the
positive /0
current causes the valve 1028 to be completely open in the straight-through
flow
configuration and a negative /0 current causes the valve 1028 to be completely
open
in the cross-flow configuration. A current of OA causes the valve to be
substantially
closed. A DC current of less than positive or negative /0 supplied to the
solenoids
causes the valve to be proportionally opened for flow in the respective
directions.
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CA 2971616 2017-06-21
The front row control system 1002 also includes a rotation sensor 1042
associated
with the front wheeled support unit 834 and a rotation sensor 1044 associated
with
the front wheeled support unit 828. The rotation sensor 1042 and rotation
sensor
1044 have respective outputs 1050 and 1052 for generating rotation signals
representing the rotation of the respective front wheeled support units 834
and 828.
Referring back to Figure 12B, in one embodiment the rotational sensor 1042 may
be
disposed within the end cap device 879 and configured to generate rotation
signals
at the output 1050 representing an angle of rotation of the leg member 873
with
respect to the end cap. As described above, in operation, engagement of the
end
cap device 879 by the cable 859 effectively prevents rotation of the end cap
when
the leg member 873 rotates within the cylindrical tubular support 877. The
rotation
sensors 1042 and 1044 each produce rotation signals representing the
respective
rotation of the front wheeled support units 834 and 828. In one embodiment the
rotation sensors 1042 and 1044 may be configured to each produce rotation
signals
representing a zero angular rotation when the respective front wheeled support
units
834 and 828 are oriented straight ahead in the direction of travel as shown in
Figure
6. An angular deviation of the wheeled support unit 834 to one side would
result in a
positive angle signal and an angular deviation to the other side would result
in a
negative angular signal. Rotation sensors may include an element (such as a
magnet in the case of a Hall effect sensor) that moves relative to a base of
the
sensor and generates a rotational displacement signal and this element may be
mounted on or coupled to the leg member 873. Various other rotation sensors
may
be used such as inductive sensors, resistive sensors, or optical rotary
encoders.
The frame height control system 1004 includes the hydraulic cylinder 855
associated
with the rear wheeled support 826, which includes the extendible piston rod
856.
The frame height control system 1004 also includes respective hydraulic
cylinders
1060, 1062, and 1064 associated with each of the rear wheeled support units
824,
822, and 820. The cylinders 855, 1060, 1062, and 1064 are connected in series
via
.. hydraulic fluid lines 1070 and 1072. As described above, by extending or
retracting
the piston rods of the cylinders 855, 1060, 1062, and 1064, the front row 120
of
CA 2971616 2017-06-21
ground engagers and rear row 122 of ground engagers across the entirety of
frame
18 are both raised or lowered by substantially equal amounts resulting in a
level
movement. In the embodiment shown in Figure 13, the frame height control
system
1004 also includes a linear sensor 1066 having an output 1068 for producing a
frame height signal representative of a height of the frame 18.
In this embodiment, the frame height control system 1004 is hydraulically
actuated
by hydraulic fluid pressure provided via hydraulic the fluid lines 1070 and
1072,
which is generated and controlled at the host propulsion unit 12. The lines
1070 and
1() 1072 may be coupled via respective quick connect fittings 1074 and 1076
to a
pressurized hydraulic fluid supply on the host propulsion unit 12. In
other
embodiments, a directional control valve similar to the proportionally
controlled
directional valve 1028 of the front row control system 1002 may be provided on
the
tillage apparatus 10 for controlling frame height.
The hydraulic cylinders 876, 1006, 1008, and 1010 of the front row control
system
1002 and the hydraulic cylinders 855, 1060, 1062, and 1064 of the frame height
control system 1004 are thus driven in unison by fluid pressure received via
the
respective lines 1020, 1022, 1070 and 1072. In operation, leakage around the
pistons of the cylinders may cause a phasing difference between motion of the
respective piston rods over time. In one embodiment the cylinders 876, 1006,
1008,
1010, 855, 1060, 1062, and 1064 may be implemented using phased cylinders.
Phased cylinders are configured to permit hydraulic fluid to bypass the piston
and
flow through the cylinder when the piston is in a re-phasing position. Re-
phasing
may be required from time to time to prevent one of the cylinders in series
(typically
the downstream cylinder) from reaching a fully extended or fully retracted
position
before the upstream cylinders and thus blocking further extension or
retraction of
these upstream cylinders.
The control system 1000 also includes a tillage apparatus controller 1080,
which in
the embodiment shown receives sensor signals and produces control signals for
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CA 2971616 2017-06-21
controlling the front row control system 1002 to counteract skidding and thus
correct
a direction of travel of a tillage apparatus moving across a ground surface
with
respect to a desired direction of travel (the desired direction of travel
would generally
be a straight-ahead condition). In this embodiment, the controller 1080 has an
input
1084 for receiving the frame height signal from the output 1068 of the frame
height
linear sensor 1066. The controller 1080 may process the signal and transmit
data at
the communications port 1082 to the host propulsion unit controller to
facilitate
display of frame height information to an operator of the host. In embodiments
where the frame height signal at the output 1068 is an analog signal, the
controller
1080 may include analog to digital converters for converting the signal into a
digital
representation for transmission to the host controller on the CAN bus.
The controller 1080 also includes inputs 1086 and 1088 for receiving the
rotation
signals from the respective outputs 1050 and 1052 of the rotation sensors 1042
and
1044. The controller 1080 further includes an output 1090 for producing a
valve
control signal for driving the solenoids 1030 and 1032 to control the
directional valve
1028.
The controller may be implemented using a low-cost microprocessor based
controller
such as the Eaton HFX Family of programmable controllers (available from Eaton
Corporation plc, Dublin, Ireland) or the JCA electronics Oriole controller
(available from
JCA Electronics Manitoba, Canada). These controllers implement a Controller
Area
Network bus (CAN bus) that may act as a communications port 1082 for receiving
commands from a host controller and also provide inputs and outputs that may
be
configured to act as the output 1090 and inputs 1084, 1086 and 1088.
In this embodiment the communications port 1082 of the controller 1080
facilitates
connection to a control bus of the host propulsion unit 12 for receiving and
sending
control signals between the host and the tillage apparatus. The host
propulsion unit
12 will generally include a host controller (not shown) that operates via a
data bus
(such as a CAN bus) for controlling the propulsion unit and connected farm
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implements such as the tillage apparatus 10. Command signals may be received
from the host controller at the communications port 1082 for controlling
operations of
the front row control system 1002 and frame height control system 1004.
Referring to Figure 14, a process for detecting skidding of the tillage
apparatus 10
during tilling operations and correcting a direction of travel is shown as a
process
flowchart at 1100. The process starts at block 1102, when the controller 1080
receives a command via the communications port 1082 to commence controlling
skidding of the tillage apparatus 10. At block 1104, a rotational signal is
received at
the controller 1080 from the output 1050 of the rotation sensor 1042
representing the
current angle of rotation a1 of the leg member 873 with respect to the end
cap. A
rotational signal is also received at the controller 1080 from the output 1052
of the
rotation sensor 1044 representing the current angle of rotation a2 of a leg
member of
the front wheeled support unit 828 with respect to its end cap. In one
embodiment
the signals representing angles a1 and a2 are received as analog signals at
the
inputs 1086 and 1088 and converted into digital signals using analog-digital
converter circuitry in the controller 1080. In
other embodiments the signals
representing angles a1 and a2 may already be in digital format as provided by
the
rotation sensors 1042 and 1044. When the wheeled support units 828 and 834 are
aligned in a straight ahead condition (i.e. at an angle of 0 as shown in
Figure 6) the
sensors 1042 and 1044 may be configured to each produce angles al and a2
having
a zero value. Alternatively, the controller 1080 may be configured to offset
the
received angle signals to produce zero values for processing at block 1106.
At block 1106, the controller determines the difference between the angles and
determines whether an absolute value of the difference is greater than a
threshold Td.
If the condition in block 1106 is met, then the front wheeled support units
834 and 828
are determined to be at different angles, which is indicative of the
propulsion unit 12
towing the tillage apparatus 10 through a turn to the left or right. Since the
front
wheeled support units 834 and 828 are spaced apart by a relatively large
distance,
when turning the inner wheeled support unit will oriented at a greater angular
deviation
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from the straight ahead condition than the outer wheeled support unit. The
threshold
Td may be set to a small angular difference value that prevents the front row
control
system 1002 from reacting to very small disturbances due to normal angular
movements by the wheeled support units when the frame 18 is moving straight
ahead
over the ground surface 16. If the condition in block 1106 is met, then the
tillage
apparatus controller 1080 determines that the propulsion unit 12 is executing
a turn
and the blocks 1102 ¨ 1106 are simply repeated. Accordingly, when the
controller
1080 determines that the angles al and a2 are indicative of the tillage
apparatus going
through a turn the controller inhibits generation of the control signals at
the output 1090
lo and no corrections to the direction of travel are made during the turn.
If the condition in block 1106 is not met then the wheeled support units 834
and 828
are at generally similar angular deviations from the straight ahead condition,
as
shown in Figure 11. In Figure 11, the wheeled support units 834 and 828 are at
approximately equal small negative angles a1 and a2 with respect to the
straight
ahead 0 reference lines. Under these conditions the tillage apparatus 10 is
determined to be skidding with respect to the direction of travel denoted by
arrow 14.
The skidding may be caused by several factors including a side force F
generated
by the plurality of ground engagers 140 of the front row 20.
At block 1108 the controller 1080 generates a valve control signal at the
output 1090
to activate the front row control system 1002. The valve control signal is
generated
in proportion to the deviation of the wheeled support units 834 and 828 from
the
straight ahead condition. In the embodiment shown the valve control signal is
generated based on an average of the signals representing the respective a1
and a2
deviations of the wheeled support units 834 and 828 and includes an
amplification
factor K that may be selected to provide an appropriate response for
counteracting
skidding of the frame 18.
Referring back to Figure 6, when the tillage apparatus 10 is moving in the
direction
of travel denoted by arrow 14, the a1 and a2 angles will be near zero or very
small.
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The front row control system 1002 will be activated since the threshold Td
should be
greater than the small angles al and a2. The valve control signal generated by
the
controller 1080 and received from the at the valve inputs 1038 and 1040 will
cause
the valve 1028 to remain substantially closed thus maintaining the front row
height
and the degree of engagement of the plurality of surface engagement devices
120
with the ground surface 16.
Referring now to Figure 11, when the al and a2 angles have non-zero negative
values as shown, the valve control signal generated at the output 1090 by the
1080
will have a negative value proportional to the angular deviation of the
wheeled
support units 834 and 828. The negative valve control signal will thus cause
the
valve 1028 to be configured for cross-flow and increased hydraulic fluid
pressure will
be supplied to the rod end port 1017 of the cylinder 876 via the hydraulic
fluid line
1022 causing the rod of the cylinder to retract. This causes a shortening of
the cable
859 and results in the front of the frame 18 being raised. Each of the
hydraulic
cylinders 1006, 1008, and 1010 are similarly actuated to raise the respective
frame
portions thus raising the front row of open members 20 and the plurality of
ground
engagers 140. Reduced engagement of the plurality of ground engagers 140 with
the ground causes the side force F to be reduced thus reducing the skidding
force
toward the right in Figure 11.
The process 1108 then returns to block 1104 and the al and a2 angles are again
evaluated to determine whether the propulsion unit 12 is going through a turn.
If the
frame 18 is still skidding, at block 1108 the controller continues the attempt
to correct
by further raising the front row of open members 20 and the plurality of
ground
engagers 140.
Should the side or transverse force F be in a direction opposite to that shown
in
Figure 11, the skidding will be to the left and the al and a2 angles will have
positive
values. A positive valve control signal will be generated and will cause the
valve
1028 to be configured for straight-through flow and increased hydraulic fluid
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pressure will be supplied to the port 1016 of the cylinder 1010 via the
hydraulic fluid
line 1020 causing the rod 1012 of the cylinder to extend. This causes a
lengthening
of the cable 859 and results in the front of the frame 18 being lowered. Each
of the
hydraulic cylinders 1006, 1008, and 1010 are similarly actuated to lower the
respective frame portions thus lowering the front row of open members 20 and
the
plurality of ground engagers 140. Increased engagement of the plurality of
ground
engagers 140 with the ground causes the side force F to be increased thus
reducing
the skidding force toward the left.
Blocks 1104 ¨ 1108 effectively implement a closed loop feedback control system
that will react to any deviation of the wheeled support units 834 and 828 that
produce al and a2 angles of similar non-zero magnitude. The magnitude of the
amplification factor K represents a loop gain that may be selected to provide
a
sufficiently quick response for counteracting skidding without overcorrecting.
If K is
too large the front row control system 1002 may cause oscillating
overcorrection and
unstable control of the frame height.
While the tillage apparatus controller 1080 has been described above for a
digital
control system, the same functions may be implemented using an analog feedback
.. control system that receives analog signals from the rotation sensors 1042
and 1044
and uses analog amplifies to generate the valve control signal.
Referring back to Figure 13, in one embodiment operation of the controller
1080 for
controlling the valve 1028 to correct the direction of travel of the tillage
apparatus 10 is
inhibited when the frame 18 is lifted to cause the ground engagers to clear
the ground
surface for transport. In this embodiment the frame height signal produced by
the
frame height linear sensor 1066 may be used to detect that the frame has been
fully
lifted and the controller 1080 may inhibit further control of direction of
travel of the
tillage apparatus.
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Additional details of various embodiment of the control system 1000 are shown
in
Figures 14A to 14D. In the embodiments shown in Figures 14A to 14D the control
system further includes wing stow/deploy hydraulic cylinders for causing the
left side
section 18B and right side section 180 (shown in Figures 1A and 6) to be
raised with
.. respect to the central section 18A for transport.
Referring back to Figure 1, the tillage device 10 further includes a rear
hitch shown
generally at 870. The rear hitch 870 is provided to facilitate coupling and
towing
additional tools or accessories (not shown) behind the tillage device 10. In
some
embodiments the tillage device 10 may not provide a satisfactory soil finish
for some
applications and the additional tool may be used in conjunction with the
tillage device
to further condition the soil. The rear hitch 870 is centrally located on a
rear portion of
the tillage device 10 and is mounted to the rear row 22. In this embodiment
further
open members 872 and 874 are welded to the open members 38, 40, and 42 and the
rear hitch 870 is attached to a transverse open member 876 extending between
the
open members 872 and 874.
Referring again to Figure 12, the rear hitch 870 of the tillage device 10 is
shown in
elevational view and includes a collar 878 mounted to the transverse open
member
876 for slidingly receiving a jack leg 880. The jack leg 880 has a plate 882
for
attaching a hitch point for coupling to the additional tool. The collar 878
has a flange
884 and the jack leg 880 has a corresponding flange 886. The rear hitch 870
also
includes a cylinder 888, which is connected to the flange 884 on the collar
878 and has
an extendible piston rod 890 coupled to the flange 886 on the jack leg 880.
In some embodiments the cylinder 888 is driven in tandem with the hydraulic
cylinder
855 associated with the frame height control system 1004 shown in Figure 13.
As
such, when the frame height 18 is raised or lowered by operating the cylinders
855,
1060, 1062, and 1064, the jack leg 880 is raised or lowered through a
corresponding
.. distance so that the plate 882 on the jack leg remains at a substantially
constant height
with respect to the wheels 197a and 197b of the tillage device 10. For
example, if the
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cylinder 855 is operated to extend the piton rod 856, thus raising the height
of the
frame 18, the extendible piston rod 890 of the cylinder 888 is also extended
to move
the jack leg 880 and plate 882 downwardly by a distance corresponding to the
change
in frame height. Similarly, when the cylinder 855 is operated to retract the
piton rod
856, thus lowering the height of the frame 18, the extendible piston rod 890
of the
cylinder 888 is also retracted to move the jack leg 880 and plate 882 upwardly
by a
distance corresponding to the change in frame height. In one embodiment the
cylinder
888 may be fed in series with the cylinders 855, 1060, 1062, and 1064 via the
hydraulic
fluid lines 1070 and 1072, as generally shown in Figure 13.
With reference to Figures 14A to 14D various alternate hydraulic fluid
circuits for
providing hydraulic fluid power to components of tillage apparatus 10 are
disclosed.
Referring now to Figure 7, a tillage apparatus 510 is which may include
generally the
same features to those described above having regard to the tillage apparatus
10
shown in Figure 1 and may be operated generally similarly to the tillage
apparatus
10. The main functional difference between tillage apparatus 510 and tillage
apparatus 10 is that because tillage apparatus 510 utilizes chisel plows in
its ground
engagers 600, there is not the same need to provide for the anti-slide and
anti-skew
system as described above in relation to tillage apparatus 10.
In operation, the tillage apparatus 510 is pulled behind a propulsion unit 512
in a
direction of travel denoted by arrow 514 across a field surface 516 and
engages with
and/or conditions the surface 516 as it is moved in the direction of travel.
The tillage apparatus 510 includes a frame 518 including rows 522, 524, 526,
and
528 of transversely oriented open members. The frame 518 includes a central
section 530, left and right inner sections 532 and 534, and left and right
outer
sections 536 and 538. The open members of the frame 518 may be generally
similar to the open members of the frame 18 shown in Figure 1.
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Referring to Figure 7, the frame 518 includes pivotal connectors in each row
between the central section 530 and the left and right inner sections 532 and
534,
and between the left and right inner sections 532 and 534 and the left and
right outer
sections 536 and 538. Each of the pivotal connectors may facilitate a pivotal
connection between adjacent open members such that the adjacent open members
are operable to pivot to orientations generally parallel to a contour of the
surface 516
when the tillage apparatus 510 is moved across the surface 516. The pivotal
connections between transverse open members may be substantially the same as
the pivotal connections described above.
Referring now to Figure 8, a rear perspective view of a portion of the central
section
530 and a portion of the left inner section 532 of the frame 518 is shown. The
central section 530 includes open members 550, 552, 554, and 556. The left
inner
section 532 includes open members 560, 562, 564, and 566 which are pivotally
connected to the open members 550, 552, 554, and 556 via pivotal connectors
570,
572, 574, and 576. By way of example, the pivotal connector 576 includes first
and
second connector portions 580 and 582 which are welded to the open members 556
and 566 respectively, to facilitate a pivotal connection between the open
members.
Each of the pivotal connectors 570, 572, and 574 may each include generally
similar
features to that of the pivotal connector 576. This allows rotational torsion
of the
members to be transferred across the pivot connection as described above.
Referring back to Figure 7, the tillage apparatus 510 also includes one or
more
ground engagers coupled to each of the open members. One of the ground
engagers is denoted at 600 in Figure 1 for exemplary purposes. In the
embodiment
shown, the ground engagers 600 include chisel plows. Each of the ground
engagers
is coupled to at least one flange of one of the open members in the rows 522,
524,
526, and 528 and configured to engage the surface 516 when the tillage
apparatus
510 is moved across the surface 516. Referring to Figure 7, the ground engager
600 is coupled to an open member 602 included in the row of open members 528.
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Referring now to Figure 9, the ground engager 600 and the open member 602 are
shown in further detail. The open member 602 includes flanges 610, 612, 614,
and
616 and a web 618. The ground engager 600 includes a mount 630 which is
coupled to the flanges 610, 612, 614, and 616 of the open member 602. The
ground
engager 600 also includes a chisel shank member 640 which is coupled to the
mount 630 and which is operable to engage with the surface 516 as the tillage
apparatus 510 shown in Figure 7 is moved across the surface 516.
Referring still to Figure 9, the tillage apparatus 510 includes a ground
engager 650
having generally similar features to the ground engager 630, which includes a
mount
652 coupled to an open member 604 in the row 526 of open members. In the
embodiment shown in Figure 9, the tillage apparatus 510 further includes a
mount
load distributor 660 coupled to the mount 652 of the ground engager 650 and to
the
open member 602 such that the mount load distributor 660 links the mount 652
and
the open member 602. The mount load distributor 652 may facilitate load
distribution from the ground engager 650 to the open member 602 instead of to
just
the open member 604. In some embodiments, this may facilitate limiting or
reducing
the application of torque to the open member 604 by the mount 652 and reduce
the
likelihood of the ground engager damaging the open member 604. The mount load
distributors 660 shown in Figure 9 are configured and designed to share the
twisting
load that may arise between open members 602 and 604. In difficult tilling
conditions, impact with an obstacle could cause and over-twisting of the
mount. The
use of mount load distributors 660 helps to alleviate the risk of this type of
over
loading occurring, which may also otherwise result in bent flanges due to
overloading.
With particular reference to Figures 8A to 8D, a spring trip device 1143 may
be
provided which may function and be constructed in substantially the same
manner
as spring device 143 as described above and each may operate to provide a trip
mechanism for a single chisel shank member 640.
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Each spring trip device 1143 may provide a trip mechanism that normally
provides
constant vertical positioning of the respective chisel shank member 640 to
which it is
interconnected relative to the frame 618. A pre-set force is exerted by each
spring
trip device 1143 on pivotable support plate 1156 fixedly connected to chisel
shank
member 640. Until a force acting against the pre-loading force provided by
spring
trip device 1143, exceeds the pre-load force imparted by spring trip device
1143,
then spring 1191 of spring trip device 1143 will not compress. This pre-load
force
may then assist in maintaining reasonably consistent depth engagement of the
respective chisel shank member 640 inter-connected to the frame 18 by struts
1151a, 1151b. However if chisel shank member 640 of impacts with a very
strong,
impenetrable item or material in the ground (eg. a large rock), the force
imparted by
such impact on may exceed a maximum allowable threshold force - which
corresponds with a force on the spring 1191 greater than the pre-load force
Fs. If
the force Fg imparted on such chisel shank member 640 does exceed the
threshold
level associated with the pre-load force Fs, then the spring trip device 1143
will "trip"
by virtue of its spring 1191 undergoing compression. This compression of the
spring 1191 and the corresponding force causing such compression, permits
pivoting of chisel shank member 640 on bracket 1156 to relieve the force on
chisel
shank member 640 and on the frame 18 to which to which it is interconnected.
This
will then relieve the contact forces being imparted by the ground (eg. the
rock) on
the chisel shank member 640 as the chisel shank member 640 will pivot away
from
the full engagement position.
Like spring device 143, spring trip device 1143 may be constructed to include
a body
portion having longitudinally oriented support struts 1151a, 1151b. Support
struts
1151a, 1151b may be fixedly and strongly connected to a transverse member of
tillage apparatus 510.
A rotator cuff unit 1193 that may be provided like rotator cuff unit 193 and
also a rod
may also be provided as described above.
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Spring device 1143 may be operable to during normal operation, to provide a
generally downward force on and to bias the chisel shank member 640 into a
position whereby it engages with and penetrate the ground material beneath
surface
516. However, spring device 143 may be configured and adapted such that if
chisel
shank members 640 associated with one or more mounts 142 engage with a
substantially impenetrable material (eg. a large granite rock), then to avoid
having
the force of such impact transmitted throughout the rest of that frame section
of
which those mounts form a part, and beyond the rest of frame 18, (potentially
causing structural damage to the frame and/or ground engagers 140) spring
device
1143 will release the biasing force exerted by spring 1191 and allow the
chisel shank
member 640 attached thereto to pivot substantially freely away from the
impenetrable material.
Once the spring trip device 1143 has been tripped, there is a downwards force
that
is still exerted on chisel shank member 640 (eg. the weight of chisel.). This
will then
enable the chisel shank member 640 to be returned to an operational position
with a
relatively easy amount of additional force. Indeed, the spring trip devices
1143 and
their respective ground engagers may be configured such that the spring trip
device
1143 will automatically re-set itself once the chisel shank member 640 has
cleared
the obstacle in the ground.
In other embodiments, instead of a single spring 191, a second spring (eg. a
corresponding axially aligned inner spring housed within spring 191) may be
provided to permit the ground force required to trip the spring trip device
143, to be
increased.
Referring now to Figure 10, a top view of the tillage apparatus 510 shown in
Figure 7
is provided. The frame 518 of the tillage apparatus 510 includes open members
702, 712, 722, 732, and 742 in the row 522, open members 704, 714, 724, 734,
and
744 in the row 524, open members 706, 716, 726, 736, and 746 in the row 526,
and
open members 708, 718, 728, 738, and 748 in the row 528.
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The frame 518 of the tillage apparatus 10 also includes row supporting open
members 760, 762, 764, 766, and 768 which connect the rows 522, 524, 526, and
528 of open members. For example, the open member 760 is connected to the
open members 732-738, the open member 72 is connected to the open members
712-718, the open members 764 and 766 are connected to the open members 702-
708, the open member 768 is connected to the open members 722-728, and the
open member 770 is connected to the open members 742-748. In the embodiment
shown, the open members 760-768 have C-shaped cross sections.
The inter-connection between the transverse members and the longitudinal
members may generally be done in the same way as described above.
In various embodiments, the tillage apparatus 510 may include variable height
wheeled supports 920, 922, 924, 926, 928, and 930 and the C-shaped cross
sections of the open members 760-770 may facilitate the wheeled supports being
mounted to the open members through openings in flanges of the open members.
The tillage apparatus 510 also includes variable height wheeled supports 900,
902,
904, 906, 908, and 910 connected to the open members 760-770 respectively
generally at forward ends of the open members. In various embodiments, the
wheeled supports 900-910 and 920-930 may act as surface following supports and
may keep the frame 518 at a relative height from the surface 16. In various
embodiments, the wheeled supports 900-910 and 920-930 may each include a
hydraulic cylinder which is configured to vary the height of the support, as
described
in further detail below.
Referring still to Figure 10, the frame 518 also includes open member load
distribution members 940, 942, 944, 946, and 948. The open member load
distribution member 940 is connected to the open members 732, 734, 736, and
738,
the open member load distribution member 942 is connected to the open members
712, 714, 716, and 718, the open member load distribution members 944 and 946
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are connected to the open members 702, 704, 706, and 708, the open member load
distribution member 948 is connected to the open members 722, 724, 726, and
728,
and the open member load distribution member 950 is connected to the open
members 742, 744, 746, and 748. In various embodiments, each of the open
member load distribution members 940, 942, 944, 946, 948, and 950 may extend
at
an angle to the open members to which they are connected.
Referring to Figure 10, each of the open member load distribution members 940,
942, 948, and 950, and 948 extends at an angle of between about 30 and 70
degrees relative to the open member to which they are connected. In the
embodiment shown, the angle may be about 45 degrees. The open member load
distribution members 944 and 946 extend at angles of between about 30 and 70
degrees and in the embodiment shown, the angles that the open members 944 and
946 extend are each about 60 degrees. In various embodiments, the load
distribution members extending at angles to the open members in the rows 522,
524, 526, and 528 may facilitate rigidity in the frame 518.
Referring still to Figure 10, in various embodiments, the tillage apparatus 10
may
include actuators 960, 962, 964, 966, 968, and 970 which are configured to
raise
and lower portions of the tillage apparatus 510 to reduce a width of the
tillage
apparatus during transport, for example. In the embodiment shown, the actuator
960 is coupled to the open members 732 and 712 and configured to retract to
pivot
the outer left portion 536 of the frame 518 about the pivotal connectors
between the
outer left portion 536 and the inner left portion 532. The actuator 962 is
coupled to
the open members 704 and 714 and the actuator 964 is coupled to the open
members 708 and 718. In operation, the actuators 962 and 964 may be retracted
from the configuration shown in Figure 10 to rotate the left inner portion 532
upwards
relative to the center portion 530 of the frame 518. The actuators 966, 968,
and 970
may be generally similar to the actuators 962, 964, and 960.
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In various embodiments, the actuators 966, 968, and 970 may be retracted
generally
simultaneously with the actuators 960, 962, and 964, to rotate the right inner
and
outer portions 534 and 538 inwards as the left inner and outer portions 532
and 536
are rotated inwards. In various embodiments, the actuators 960-966 may be
actuators which are configured to lift and hold substantial weight, such as,
for
example hydraulic actuators.
As will be evident from Figures 7A and 7B, a system like that described above
for
raising and lowering the frame 518 relative to the wheels, may be provided,
including
a pulley and cable mechanism, along with a hydraulic cylinder that may be
supplied
with fluid from a supply system and controlled by a controller.
Figures 16A, 16B and 160 depict some examples of cross sectional dimensions
for
the transverse and longitudinal member of tillage apparatus 10.
Figures 17A, 17B and 17C depict some examples of cross sectional dimensions
for
the transverse and longitudinal member of tillage apparatus 510.
While specific embodiments of the invention have been described and
illustrated, such
embodiments should be considered illustrative of the invention only and not as
limiting
the invention as construed in accordance with the accompanying claims.
The above described embodiments are intended to be illustrative only and in no
way
limiting. The described embodiments of carrying out the invention are
susceptible to
many modifications of form, arrangement of parts, details and order of
operation.
Other variations are possible.
When introducing elements of the present invention or the embodiments thereof,
the
articles "a," "an," "the," and "said" are intended to mean that there are one
or more of
the elements. The terms "comprising," "including," and "having" are intended
to be
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inclusive and mean that there may be additional elements other than the listed
elements.
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