Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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HINGE ASSEMBLY FOR FOLDING IMPLEMENT FRAME
TECHNICAL FIELD
This invention relates to apparatus for use
on mobile machines with outwardly extending
portions. The invention is especially well suited
for use on mobile agricultural machines which have
pivotally connected tool bars or frame sections
wherein one or more of the sections can be pivoted
upwardly away from the ground to an inactive,
transport position.
BACKGROUND OF THE INVENTION
AND
TECHNICAL PROBLEMS POSED BY THE PRIOR ART
Some conventional mobile agricultural
machines are provided with two or more frame sections
or tool bars that are pivotally connected together
with a conventional hinge assembly that permits one
frame section to pivot or "float" relative to the
other when the machine is baing operated with the
frame sections in a lowered, ground-engaging position
on uneven terrain. This accommodates vertical
variation in the terrain across the width of the
machine~
When a laterally extending frame section of
such a machine is raised away from the ground and
folded back toward the adjacent section beyond a
certain angle--as when the machine is being prepared
for transport along a highway--the conventional hinge
assembly permits the raised sec~ion to freely fall a
short distance toward the other frame section. This
"free fall" results in the machine being subjected to
undesired impact loading.
It would be desirable to provide a folding
implement frame section hinge assembly with an
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improved construction which, in addition to
accommodating frame section float when a frame
section is in the lowered, ground-engaging position,
would permit a frame section to be smoothly raised
and lowered. It would also be desirable if the
improved hinge assembly could prevent free fall of a
raised frame section during the folding and unfolding
operations so as to avoid subjecting the machine to
undesired impact loading.
SUMMARY OF THE INVENTION
An improved implement floating hinge
assembly is provided for accommodating the folding of
pivotally connected first and second frame sections.
The hinge assembly includes a first lever pivotally
connected to the first frame section, a second lever
connected between the second frame section and the
first lever, and an extendable and retractable
actuator pivotally connected between the first frame
section and the second lever. In the improved
assembly, the second lever is connected to the second
frame section about a pivot axis that is fixed
relative to the second frame section. A pin is
movable with the second lever at a fixed distance
from the pivot axis of the connection between the
~5 second frame section and the second lever. The first
lever defines an elongated slot means for receiving
the pin to accommodate relative movement between the
pin and the first lever. With this arrangement,
relative pivoting movement between the frame sections
can occur even after the frame sections have been
unfolded. Further, during the folding of the frame
sections, the pin remains at one end of the slot
means so that a free fall of one of the frame
sections relative to the other does not occur.
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Numerous other features and advantages of the present
invention will become readily apparent from the
foregoing detailed description of the invention, from
the claims, and from the accompanying drawings.
BRIEF DESCRIPTION OF TEIE DRAWINGS
In the accompanying drawings forming part of
the specification, in which like numerals are
employed to designate like parts ~hroughout the same,
Fig. 1 is a fragmentary, rear elevational
view of a mobile machine incorporating a conventional
prior art floating frame hinge assembly for
accomodating the folding of pivotally connected first
and second frame sections;
Fig. 2 is a greatly enlarged, fragmentary,
rear elevational view of the right-hand rear portion
of the machine illustrated in Fig. 1 showing the
hinge assembly with the frame sections in the
lowered, ground~engaging position,
Fig. 3 is a view similar to Fig. 2, but
showing the conventional hinge assembly moving toward
the folded position;
Fig. 4 is a view similar to Figs. 2 and 3,
but showing the novel hinge assembly of the present
invention in operation to pivot or "fold" one of the
frame sections toward a raised, inactive position;
and
Fig. 5 is a view similar to Fig. 4, but
showing the hinge assembly o~ the present invention
in a fully folded position.
DESCRIPTION OF THE PREFERRED EMBODIMENT
--Prior Art Design
Referring now to Fig. 1, a mobile machine is
designated generally therein by reference numeral
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10. The machine 10 includes a working implement
comprising a central or main -frame section 12 and
pairs of frame sections 14 and 16 which laterally
extend from either side of the central frame section
S 12. The frame sections typically carry working tools
such as those associated with a planter, seed drill,
etc. The machine 10 typically as a plurality of
s~heels 18, as well as wheels 20 associated with the
main frame section 12, wheels 22 associated with the
frame section 14, and wheels 24 associated with the
frame section 16~
In operation, the machine 10 is moved over
the ground 26 with the frame sections 14 and 16 in a
lowered, ground-engaging position as illustrated in
Fig. 1. To accommodate road transport of the machine
10, the frame sections are typically raised to an
elevated, inactive position. To this end, the frame
section 16 may be pivoted or folded over on top of
the frame section 14 by means hereinafter described
in detail so that the frame section 16 is generally
parallel to the first frame section 14. The first
frame section 14 can then be pivoted upwardly so that
it is approximately perpendicular to the main frame
section 12 but is preferably tilted a few degrees
from the vertical towards the frame section 12.
As best illustrated in FigO 2, each frame
section 16 is pivotally connected on an end of the
frame section 14 about a pin 32. Each frame section
16 is moveable between the raised, inactive position
and a lowered, ground-engaging position by an
extendable and retractable actuator 34~ In the
preferred embodiment illustrated, the actuator 34 is
a dual acting hydraulic cylinder-piston actuator. At
one end, the actuator 34 is pivotally connected to a
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portion of the frame 14, as at connection pin 36. At
the other end, the actuator 34 is pivotally connected
by means of a pin 38 to first and second levers 41
and 42, respectively.
The first lever 41 is pivotally connected by
means of a pin 46 to the frame section 14, and the
second lever 42 is a~tached to the frame section 16
by means o a pin 48 carried on the frame section 16
and which is received in a slot means or slot 50
defined in the second lever 42.
When the actuator 34 is in the extended
position as illustrated in Fig. 2, the frame section
16 is in the lowered, ground-engaging position, and
the pin 48 carried by the frame section 16 is
positioned intermediate the ends of the slot 50 in
the second lever 42. The arrangement of the pin 48
in the slot 50 permits the frame section 16 to pivot
or "float" relative to the frame section 14 when
uneven terrain is encountered by the machine 10.
Relative pivoting movement between the frame sections
is easily accommodated because of the relative
movement that is permitted between the second lever
42 and the pin 48 in the elongated slot 50 of the
lever 42.
When it is desired to raise the frame
section 16 to the elevated or inactive position, the
actuator 34 is retracted~ With reference to Fig. 2,
this causes the first lever 41 to pivot about pin 46
(counterclockwise as viewed in Fig. 2~. This also
moves the second lever 42 relative to the pin 480 As
the levers 41 and 42 are moved, the pin 38
necessarily first moves upwardly in an arc, and this
causes the lever 42 to be pulled upwardly so as to
cause the frame section 16 to be pivoted upwardly
with the pin 48 at the bottom end of the slot 50 in
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the second lever 42. The second lever 42 is under
tension loading as this occurs.
Eventually, the frame section 16 is pivoted
about pin 32 to the orientation wherein the center of
gravity of the frame section 16 is located on the
other side of the pin 32 (on the left side of the pin
32 as viewed in Fig. 3). At this point, the force of
gravity acts to pull the frame section 16 downwardly
in the counterclockwise direction around pin 32, and
the pin 48 moves with the frame section 16 away from
the end of the slot 50 (in the direction of the arrow
60 illustrated in Fig. 3). The frame section 16, and
the pin 48 carried thereon, thus undergo a "free
fall" until the pin 48 hits the other end of the slot
50. This causes an undesirable impact loading on the
machine 10.
It is to be noted that when the pin 48
initially slides away from the end of the second
lever slot 50, the tension loading on the lever 42
drops to zero, an~ when the pin 48 impacts at the
other end of the slot 50, the loading on the second
lever 42 becomes compressive. Continued retraction
of the actuator 34 effects continued movement of the
second lever 42 (toward the left as viewed in Fig.
3), and the pin 48, owing to the weight of the frame
section 16, then moves with the lever 42 at the end
of the slot 50 until the pivoting action has been
completed and the frame section 16 is substantially
parallel to the frame section 14.
To unfold the frame sections, the actuator
34 is extended, and the frame section 16 is pivoted
back to the lowered, ground-engaging position. As
the center of gravity of the frame section 16 passes
back to the other side of the pivot pin 32, the frame
section 16 again undergoes a "free fall" as the pin
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48 moves from one end of the second lever slot 50 to
the other end of the slot 50. This causes another
impact loading on the machine 10 as the loading on
the second lever 42 changes from compression to
tension.
The conventional frame hinge assembly
illstrated in Figs. 2 and 3 may also be employed with
respect to the connection between the frame section
12 and the frame section 14 illustrated in Fig. 1.
However, the frame section 14 would typically be
pivoted to an inactive, elevated position relative to
the frame section 12 only after the frame section 16
had been folded over relative to the frame section
14. Also, the frame section 14, with the folded over
frame section 16, would typically not be folded over
completely parallel to the frame section 12, but
rather, would be pivoted just slightly past the
vertical.
--The Improved Frame Hinge
Assembly Of The Present Invention
Figs. 4 and 5 illustrate the improved frame
hinge assembly of the present invention which is
shown connecting a first frame section 14' and a
second ~rame section 16'. The first frame section
14' is pivotally connected to the second frame
section 16' about a pin 32' in the same manner as the
frame sections 14 and 16 described above with
reference to Figs. 1-3.
A first lever 41' is pivotall~ connected by
means of a pin 46' to the first frame section 14l. A
second lever 42' is pivotally mounted about a ~ixed
axis by means of a pin 48' to the second frame
section 16~. An extendable and retractable actuator
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34', such as an hydraulic cylinder-piston actuator,
is pivotally connected by means of a pin 36' to the
first frame section 14'.
There is a common conne~tion of the first
lever 41', the second lever 42', and the actuator 34'
to accommodate relative pivoting movements during
extension and retraction of the actuator 34'. The
common connection includes a pin 38' which is mounted
for movement with the second lever 42' at a fixed
distance from the pivot axis defined by the pin 48'
which connects the second lever 42' to the second
frame section 16'.
The pin 38' is received within an elongated
slot 50' defined by the first lever 41'. The pin 38'
may be mounted to the assembly in a variety of waysO
~he pin 38' may be journaled within both the end of
the actuator 34' and the end of the second lever
42'. On the other hand, the pin 38' may be fixedly
attached to the end of the second lever 42' and
journaled within the end of the actuator 34'.
Alternatively, the pin 38l may be fixedly attached to
the end of the actuator 34' and journaled within the
second lever 42'. Also, the pin 38' may be separate
from the pivotal connection between ~he actuator 34'
and the second lever 42'. However, in the preferred
embodiment illustrated, the actuator 34' is pivotally
connected to the second lever 42' about a pivot axis
that is colinear with the longitudinal axis of the
pin 38'.
In the preferred embodiment illustrated in
Figs. 4 and 5, the elongated slot 50' is defined, in
part, by opposed straight side surfaces that are
parallel to, and equally distant from, a straight
line extending between the pin 38' and the connection
of the first lever 41' to the first frame section 14'
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at the pin 46'. Also, in the preferred embodiment,
the width of the elongated slot 50' is substantially
equal to the diameter of the pin 38' for
accommodating the pin 38' in sliding engagement.
With the novel hinge assembly of the present
invention, it is possible for the frame sections 14'
and 16' to be oriented in an un~olded, generall~
coplanar orientation (similar to the orientation of
the frame sections 14 and 16 of the prior art
assembly illustrated in Fig. 2). In such an
orientation, the first lever 41' and the second lever
42' define an acute included angle. In this unfolded
orientation, the pin 38' is positioned intermediate
the ends of the slot 50' when the machine is on level
ground. The slot 50' thus permits relative movement
between the pin 38' and the first lever 41'. This
accommodates relative pivoting movement or "~loat"
between the unfolded ~rame sections 14 and 16 when
uneven terrain is encountered.
When it is desired to raise the second frame
section 16' to an inactive position, the actuator 34'
is retracted as illustrated in Fig. 4. This results
in the first lever 41' pivoting about the pin 46'.
The pin 38' is engaged by the first lever 41' at the
bottom of the slot 50' and is carried in an arc with
the lever 41'. This subjects the second lever 42' to
tension and raises the lever 42' so as to pivot the
second ~rame section 16' about the main hinge pin
32'.
The novel hinge assembly of the present
invention does not subject the machine to impact
loading when the frame section 16' is folded or
raised to the inactive position. As the frame
section 16' is raised, the weight of the frame
section causes the pin 38' to exert a force on the
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first lever 41' at the bottom of the slot 50'. The
first lever 41' is thus compressively loaded between
the pin 38' and the pivot pin 46'. At the position
illustrated in Fig. 4, the center of gravity of the
frame section 16' is directly over the main hinge
pivot 32'. In Fig. 4, the center of gravity force
from the weight of the frame section 16' is
schematically illustrated by arrow 80'. Up to this
point, the second lever 42' is in tension, and beyond
this point (as the frame section 16' pivots further
in the counterclockwise direction as viewed in Fig.
4), the second lever 42' is in compression.
In Fig. 4, it is seen that the lines of
action of the actuator 34' and second lever 42'
intersect at an obtuse angle An As the frame section
16' pivots further (counterclockwise as viewed in
Fig. 4), the angle A increases as the lines of action
become colinear at an over center position, and then
the angle A becomes a reflex angle beyond the over
center position (Fig. 5).
Beyond the orientation illustrated in Fig. 4
but before the angle A becomes a reflex angle, the
pin 38' initially becomes subjected to a combined
force resulting from the compressive force in the
second lever ~2' and the actuator 34'. This combined
force on the pin 38' is directed toward the top end
of the elongated slot S0' in the first lever 41'.
However, the weight of the actuator 34' and the
weight of the second lever 42', along wi~h frictional
forces, maintain the pin 38' at the bottom of the
elongated slot 50'.
As the frame section 16' continues to pivot
to the folded position (counterclockwise as viewed in
Fig. 5) and the angle A becomes a reflex angle, the
resulting force on the pin 38' from the second lever
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42' and the actuator 34' changes direction from
toward the top of the slot 50' to toward the bottom
of the slot 50'. The pin 3~' thus remains at the
bottom of the slot 50' during the frame folding
sequence. The hinge assembly thus permits the frame
section 16' to be folded smoothly to the fully folded
position illustrated in Fig. 5 without any free fall
impact loading of the assembly.
The novel hinge assembly permits smooth
unfolding of the frame sections when actuator 34' is
extended to reverse the above-described sequence.
However, if the frame sections are unfolded on ground
that is not level, there may be some slight free fall
of the frame section 16' relative to the frame
lS section 14' around the mid-range position (such as
illustrated in Fig~ 4). However, in this mid-range
position, the elongated slot 50' in the first lever
~l' is almost perpendicular to the actuator 34' and
to the second lever 42'. Thus, any free fall will be
~0 minimal under such conditions.
It will be readily observed from the
foregoing detailed description of the invention and
from the illustrated embodiment thereof that numerous
variations and modifications may be effected without
departing from the spirit and scope of the novel
concepts or principles of this invention.
