U.S. patent application number 09/929630 was filed with the patent office on 2002-03-07 for direct drive vibratory shaker.
Invention is credited to Orlando, Franklin P..
Application Number | 20020026780 09/929630 |
Document ID | / |
Family ID | 23643918 |
Filed Date | 2002-03-07 |
United States Patent
Application |
20020026780 |
Kind Code |
A1 |
Orlando, Franklin P. |
March 7, 2002 |
Direct drive vibratory shaker
Abstract
A vibratory shaker for mounting on a crop harvester framework
for removing crops from vines, bushes, and trees has a crop foliage
engaging brush that is driven directly about a brush rotation axis
by a brush driving motor. The crop foliage engaging brush and the
brush driving motor are supported for rotation on the crop
harvester framework. The power for driving the brush driving motor
is controlled to provide oscillatory motion subject to operator
controlled frequency, amplitude and oscillatory wave shape.
Inventors: |
Orlando, Franklin P.;
(Morgan Hill, CA) |
Correspondence
Address: |
Henry M. Stanley
165 E. Hilton Drive
Boulder Creek
CA
95006
US
|
Family ID: |
23643918 |
Appl. No.: |
09/929630 |
Filed: |
August 13, 2001 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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09929630 |
Aug 13, 2001 |
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09414997 |
Oct 7, 1999 |
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Current U.S.
Class: |
56/328.1 ;
56/340.1 |
Current CPC
Class: |
A01D 46/26 20130101 |
Class at
Publication: |
56/328.1 ;
56/340.1 |
International
Class: |
A01D 046/00 |
Claims
What is claimed:
1. A directly driven shaker for mounting on a mobile crop harvester
framework for harvesting bush, tree and vine grown crops,
comprising a crop foliage engaging brush having a brush axis of
rotation, a drive motor connected to said crop foliage engaging
brush for providing a motor output for directly driving said crop
foliage engaging brush about said brush axis of rotation, means for
journalling said crop foliage engaging brush and said drive motor
on the mobile crop harvester framework, a power source on the
mobile crop harvester framework providing a power output connected
to said drive motor, and means mounted between said power source
and said motor for controlling said power output connected to said
drive motor.
2. The directly driven shaker of claim 1 wherein said power source
comprises a hydraulic pump, a hydraulic fluid supply connected to
said hydraulic pump, said power output comprising a hydraulic fluid
flow, and wherein said drive motor comprises a hydraulic motor.
3. The directly driven shaker of claim 2 wherein said means for
controlling comprises a hydraulic valve receiving said hydraulic
flow, and a valve controller for controlling quantity, sense and
time rate of change of said quantity of said hydraulic fluid
flow.
4. The directly driven shaker of claim 3 wherein said valve
controller comprises means for controlling a shape of said time
rate of change.
5. The directly driven shaker of claim 1 wherein said power source
comprises an electric power source having an electric power output,
and wherein said drive motor comprises an electric motor.
6. The directly driven shaker of claim 5 wherein said means for
controlling comprises an electric power output controller for
controlling magnitude, polarity and time rate of change of
magnitude of said electric power output.
7. The directly driven shaker of claim 1 wherein said power source
comprises a pneumatic power supply, said power output comprising a
pneumatic fluid flow, and wherein said drive motor comprises a
pneumatic motor.
8. The directly driven shaker of claim 7 wherein said means for
controlling comprises a pneumatic valve receiving said pneumatic
fluid flow, and a valve controller for controlling quantity, sense,
and time rate of change of said quantity of said pneumatic fluid
flow.
9. The directly driven shaker of claim 1 wherein said crop foliage
engaging brush comprises first and second brush segments having
substantially coaxial brush axes of rotation, said drive motor
comprising motor case, and a motor shaft, said motor case connected
to said first brush segment, and said motor shaft connected to said
second brush segment.
10. The directly driven shaker of claim 9 wherein said first and
second brush segments have inside dimensions and said motor case
has an outside dimension, said brush segment inside dimensions
being sufficient to accept said motor case outside dimension,
whereby said motor case is positioned within said brush segment
inside dimensions.
11. The directly driven shaker of claim 1 wherein said drive motor
comprises a motor case, and a motor shaft, and wherein said means
for journalling comprises a first bearing for supporting one end of
said crop foliage engaging brush in the crop harvester framework,
and a second bearing for supporting said motor case in the crop
harvester framework, further comprising means for connecting an
opposing end of said crop foliage engaging brush to said motor
shaft.
12. The directly driven shaker of claim 11 comprising an inertial
member attached to said motor case.
13. The directly driven shaker of claim 12 comprising resilient
centering means attached between said inertial member and the crop
harvester framework.
14. The directly driven shaker of claim 1 wherein said crop foliage
engaging brush comprises first and second brush segments having
substantially coaxial brush axes of rotation, and wherein said
drive motor comprises first and second drive motors having a first
motor case and first motor shaft and a second motor ease and second
motor shaft respectively, and a torsion member connected between
said first and second motor cases, said means for controlling
providing substantially simultaneous and opposite motor output at
said first and second motor shafts.
15. The directly driven shaker of claim 14, said means for
journalling comprising a first bearing on the mobile crop harvester
framework for supporting said first motor case therein, and a
second bearing on the mobile crop harvester framework for
supporting said second motor case therein further comprising means
for connecting said first motor shaft to one end of said first
brush segment, means for connecting said second motor shaft to one
end of said second brush segment, and means for connecting opposing
ends of said first and second brush segments for rotation
therebetween.
16. The directly driven shaker of claim 14, said means for
journalling comprising a first bearing on the mobile crop harvester
framework for supporting one end of said first brush segment, a
second bearing on the mobile crop harvester framework for
supporting one end of said second brush segment, further comprising
means for connecting said first motor shaft to an opposing end of
said first brush segment, means for connecting said second motor
shaft to an opposing end of said second brush segment.
17. The directly driven shaker of claim 14 wherein said first and
second motor cases comprise first and second cylinders and wherein
said first and second motor shafts comprise first and second
pistons and first and second piston rods extending therefrom
respectively, said torsion member comprising a first lever having
opposing ends, a second lever having opposing ends, means for
connecting said first and second levers at intermediate points
thereon for relative rotational motion therebetween, means for
pivotally connecting said first and second piston rods to said
opposing ends on said second lever, and means for pivotally
connecting said first and second cylinders to said opposing ends on
said first lever.
18. The directly driven shaker of claim 1 wherein said means for
controlling provides real time control of frequency and amplitude
of said motor output.
19. The directly driven shaker of claim 18 wherein said means for
controlling provides control of said motor output frequency wave
shape.
20. The directly driven shaker of claim 1 comprising means for
transferring said power output from the mobile crop harvester
framework to said drive motor.
21. A direct drive shaker head mounted for rotating motion on a
framework of a mobile crop harvester used for harvesting above
ground grown crops, comprising a crop engaging brush having an
axial length and an axis of rotation, a motor, said motor providing
a motor output connected to directly drive said crop engaging brush
about said axis of rotation, and means for controlling said motor
output to provide oscillatory motion of said crop engaging brush
about said axis of rotation.
22. The direct drive shaker head of claim 21 wherein said means for
controlling comprises means for controlling frequency and amplitude
of said motor output.
23. The direct drive shaker head of claim 21 wherein said motor
comprises a hydraulic motor.
24. The direct drive shaker head of claim 21 wherein said motor
comprises a pneumatic motor.
25. The direct drive shaker head of claim 21 wherein said motor
comprises an electric motor.
26. The direct drive shaker head of claim 23 wherein said means for
controlling comprises a hydraulic valve having an output in
communication with said hydraulic motor, and means for controlling
frequency and amplitude of said hydraulic valve output.
27. The direct drive shaker head of claim 24 wherein said means for
controlling comprises a pneumatic valve having an output in
communication with said pneumatic motor, and means for controlling
frequency and amplitude of said pneumatic valve output.
28. The direct drive shaker head of claim 25 wherein said means for
controlling comprises an electrical control circuit having an
output connected to said electric motor, and means for controlling
frequency and amplitude of said electrical control circuit
output.
29. The direct drive shaker head of claim 22 wherein said means for
controlling comprises means for controlling wave shape of said
amplitude.
30. The direct drive shaker head of claim 21 wherein said crop
engaging brush comprises first and second crop engaging brushes,
and wherein said motor comprises first and second motors providing
first and second motor outputs respectively, further comprising
means for directly connecting said first motor output to one end of
said first crop engaging brush, means for directly connecting said
second motor output to one end of said second crop engaging brush,
and a mechanical connection member extending between said first and
second motors.
31. The direct drive shaker head of claim 21, comprising an
inertial member attached to said motor.
32. The direct drive shaker head of claim 31, comprising spring
means for extending between said inertial member and the framework
of the mobile crop harvester.
33. The direct drive shaker head of claim 21, wherein said crop
engaging brush comprises a hub having an internal chamber and
radially outward extending tines, said motor being positioned
within said internal chamber, whereby shaker head axial length is
minimized.
34. The direct drive shaker head of claim 21 wherein said crop
engaging brush comprises first and second crop engaging brushes
having an internal chamber extending along said axial length, said
motor being positioned within said internal chamber, whereby shaker
head axial length is minimized.
35. A crop harvester for separating a crop from plants growing from
an underlying surface, comprising a harvester framework, harvester
propulsion means mounted in said harvester framework, means
attached to said harvester framework and connected to said
harvester propulsion means for engaging the underlying surface for
supporting said harvester framework for movement over the
underlying surface, a crop foliage engaging brush having a brush
axis of rotation and an axial length, a brush drive motor providing
a motor output connected directly to and for driving said crop
foliage engaging brush about said brush axis of rotation, means for
journalling said crop foliage engaging brush and said brush drive
motor on said harvester framework, a power source for providing
power to said brush drive motor, and control means mounted between
and connected to said power source and said brush drive motor for
controlling said motor output to provide oscillatory motion of said
crop foliage engaging brush about said brush axis of rotation.
36. The crop harvester of claim 35 wherein said control means
comprises means for controlling frequency and amplitude of said
motor output.
37 The crop harvester of claim 36 wherein said means for
controlling comprises means for controlling wave shape of said
amplitude.
38. The crop harvester of claim 35 wherein said crop foliage
engaging brush comprises first and second foliage engaging brushes,
and wherein said brush drive motor comprises first and second drive
motors providing first and second motor outputs respectively,
further comprising means for connecting said second motor output to
one end of said second foliage engaging brush, and a connecting
member attached to and extending between said first and second
motors.
39. The crop harvester of claim 35 comprising an inertial member
attached to said brush drive motor.
40. The crop harvester of claim 39 comprising spring means attached
to and extending between said inertial member and said harvester
framework.
41. The crop harvester of claim 35 wherein said crop foliage
engaging brush comprises a hub having an internal chamber and
radially outward extending tines, said brush drive motor being
positioned within said internal chamber, whereby said brush drive
motor is contained substantially within said crop foliage engaging
brush axial length.
42. The crop harvester of claim 35 wherein said crop foliage
engaging brush comprises first and second crop engaging brushes
having an internal chamber extending along said axial length, said
brush drive motor being positioned within said internal chamber,
whereby said crop foliage engaging brush is contained substantially
within said first and second crop engaging brushes' axial
lengths.
43. The crop harvester of claim 35 wherein said brush drive motor
comprises a hydraulic motor.
44. The crop harvester of claim 43 wherein said control means
comprises a hydraulic valve having an output in communication with
said hydraulic motor, and means for controlling frequency and
amplitude of said hydraulic valve output.
45. The crop harvester of claim 35 wherein said brush drive motor
comprises a pneumatic motor.
46. The crop harvester of claim 45 wherein said control means
comprises a pneumatic valve having an output in communication with
said pneumatic motor, and means for controlling frequency and
amplitude of said pneumatic valve output.
47. The crop harvester of claim 35 wherein said brush drive motor
comprises an electric motor.
48. The crop harvester of claim 47 wherein said control means
comprises an electrical control circuit having an output connected
to said electric motor, and means for controlling frequency and
amplitude of electrical control circuit output.
49. The crop harvester of claim 35, comprising means for
transferring power from said power source to said brush drive
motor.
50. A shaker for harvesting crops from plants and for mounting on a
framework of a crop harvester, comprising a harvesting brush for
contacting plants, said harvesting brush having a brush axis, a
brush drive motor connected to drive said harvesting brush about
said brush axis, said brush driving motor having a motor shaft and
a motor case, means for providing a predetermined ratio of inertias
about said brush axis between said motor shaft and said motor case,
and means for supporting said harvesting brush, brush drive motor
and means for providing a predetermined ratio of inertias on the
framework for rotation about said brush axis.
51. The shaker of claim 50 wherein said means for providing a
predetermined ratio of inertias comprises a predetermined inertial
member attached to said motor case.
52. The shaker of claim 51 further comprising resilient centering
means attached between said inertial member and the crop harvester
framework.
53. The shaker of claim 50 wherein said means for providing a
predetermined ratio of inertias comprises an additional harvesting
brush connected to said motor case.
54. The shaker of claim 50, wherein means for providing a
predetermined ratio of inertias comprises an additional harvesting
brush, and wherein said brush drive motor comprises first and
second brush drive motors having first and second motor shafts and
first and second motor cases respectively, means for connecting
said first motor shaft to said harvesting brush, means for
connecting said second motor shaft to said additional harvesting
brush, and means for connecting said first motor case to said
second motor case.
55. The shaker of claim 54, wherein said means for supporting
comprises means for journalling said first and second motor cases
in the crop harvester framework, further comprising means for
connecting one end of said harvesting brush to one end of said
additional harvesting brush in rotating relationship.
56. The shaker of claim 54, wherein said means for supporting
comprises means for journalling one end of said harvesting brush in
the crop harvester framework, and means for journalling one end of
said additional harvesting brush in the crop harvester
framework.
57. The shaker of claim 50, wherein said means for providing a
predetermined ratio of inertias comprises an additional harvesting
brush, and wherein said brush drive motor comprises a piston motor
having a cylinder, a piston enclosed within said cylinder, and a
piston rod attached to said piston at one end and having an
opposing end extending from said cylinder, further comprising means
for connecting said harvesting brush and additional harvesting
brush at adjacent ends for rotational movement therebetween, means
for pivotally mounting said cylinder to said adjacent end of said
harvesting brush at a position displaced from said brush axis, and
means for pivotally mounting said opposing end of said piston rod
to said adjacent end of said additional harvesting brush at a
position displaced from said brush axis.
58. The shaker of claim 57, wherein said piston motor comprises
first and second piston motors.
59. The shaker of claim 50, further comprising resilient centering
means attached between said means for providing a predetermined
ratio of inertias and the crop harvester framework.
60. The shaker of claim 50, wherein said means for providing a
predetermined ratio of inertias comprises means for providing
substantially equivalent inertias.
Description
SUMMARY OF THE INVENTION
[0001] A directly driven shaker is disclosed herein for mounting on
a mobile crop harvester framework used for harvesting bush, tree
and vine grown crops. A crop foliage engaging brush has a brush
axis of rotation. A drive motor is connected to the crop foliage
engaging brush for providing a motor output that directly drives
the crop foliage engaging brush about the brush axis of rotation.
Means is provided for journalling the crop foliage engaging brush
and the drive motor on the mobile crop harvester framework. A power
source is provided on the mobile crop harvester framework, which
produces a power output connected to the drive motor. Means is
mounted between the power source and the motor for controlling the
power output connected to the drive motor.
[0002] A direct drive shaker head is disclosed that is mounted for
rotation on a framework of a mobile crop harvester used for
harvesting above ground grown crops. A crop engaging brush has an
axial length and an axis of rotation. A motor is provided which
produces a motor output connected to directly drive the crop
engaging brush about the axis of rotation. Means is connected to
the motor for controlling the motor output to provide oscillatory
motion of the crop engaging brush about the axis of rotation.
[0003] A crop harvester is disclosed for separating a crop from
plants growing from an underlying surface. The crop harvester
includes a harvester framework and harvester propulsion means that
is mounted in the harvester framework. Means is attached to the
harvester framework and connected to the harvester propulsion means
for engaging the underlying surface for supporting the harvester
framework and for producing harvester movement over the underlying
surface. A crop foliage engaging brush has a brush axis of rotation
and an axial length. A brush drive motor provides a motor output,
which is connected directly to and drives the crop foliage engaging
brush about the brush axis of rotation. Further, means is provided
for journalling the crop foliage engaging brush and the brush drive
motor on the harvester framework. A power source is present for
providing power to the brush drive motor. Control means is mounted
between and connected to the power source and the brush drive motor
for controlling the motor output to provide oscillatory motion of
the crop foliage engaging brush about the brush axis of
rotation.
[0004] The invention relates to a shaker for harvesting crops from
plants wherein the shaker is configured to be mounted on a
framework of a crop harvester. A harvesting brush is provided for
contacting the plants, the brush having a brush axis. A brush drive
motor is connected to drive the brush about the brush axis. The
drive motor has a motor shaft and a motor case. Means is present
for providing a predetermined ratio of inertia about the brush axis
between the motor shaft and the motor case. Further, means is
present for supporting the combination of the harvesting brush, the
brush drive motor and the means for providing a predetermined ratio
on the framework for rotation about the brush axis.
BRIEF DESCRIPTION OF THE DRAWINGS
[0005] FIG. 1 is a mechanical diagram of one embodiment of the
present invention.
[0006] FIG. 2 is a block diagram generally depicting the power
source, power distribution and distribution control utilized in the
present invention.
[0007] FIG. 3 is a mechanical diagram of another embodiment of the
present invention.
[0008] FIG. 3A is a view along the line 3A-3A of FIG. 3.
[0009] FIG. 4 is a mechanical diagram of yet another embodiment of
the present invention.
[0010] FIG. 5 is a mechanical diagram of still another embodiment
of the present invention.
[0011] FIG. 6 shows an additional embodiment of the present
invention.
[0012] FIG. 7 is a partial section along the lines 7-7 of FIG.
6.
[0013] FIG. 8 is a section of a piston motor used in the embodiment
of FIG. 6.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0014] Currently, shakers that are used for harvesting vegetables
and fruits, such as tomatoes, cucumbers, grapes, raisins, and
olives use a brush element having brush tines that enter the
foliage of the crop and are then driven in an oscillatory manner to
disengage the crop from the vines or bushes. The oscillation of the
brush, however, is obtained currently by using eccentric masses
that are timed to rotate in such as fashion as to produce a rocking
couple. A motor drives the eccentric masses. Devices producing the
rocking couples are called force-balanced shaker heads and contain
two or more heavy eccentric masses. The oscillatory output from the
force-balanced shaker heads is connected directly to the brush,
which causes the tines engaging the crop foliage to oscillate. As
may be imagined, the force-balanced shaker heads are heavy, due to
the large eccentric masses, often weighing four to six hundred
pounds. The brush and force-balanced shaker head together with a
motor for driving the shaker head are often required to be raised
or lowered as well as to be moved from side to side to accommodate
contact with the crop foliage. When the motor, shaker head and
brush assembly are positioned high on or laterally of the
harvesting machine, the center of gravity of the harvesting machine
can assume a position which causes instability in the harvesting
machine as it travels over an underlying surface. Additionally, in
such force-balance shaker head driven harvesting machines it is not
easy to adjust shaker displacement. To do so the harvesting
operation must be stopped and the mass of the eccentric weights
must be altered by adding or removing mechanical components from
the eccentric masses. Many configurations of force-balanced shaker
heads are known, clear descriptions of which may be found in U.S.
Pat. No. 4,341,062, Scudder, and U.S. Pat. No. 4,432,190,
Orlando.
[0015] In the invention to be described herein, the force-balanced
shaker head is eliminated as well as a net rotation retarder or
rotation brake. Three to four hundred pounds of weight are
eliminated by elimination of the eccentric masses. The reduction in
weight further reduces the potential for harvesting machine
instability due to high or laterally shifted centers of gravity
when the shaker head is elevated or extended to contact foliage in
an olive tree, for example. Axial length of a shaker head
previously occupied by an eccentric mass assembly and a drive motor
therefor is eliminated and the entire length of the novel shaker
head described herein is the axial length of the brush as the
direct drive motor may be placed internally within the brush.
Further, the frequency of oscillation of the brush and the
amplitude of oscillation can be independently controlled by
controlling the output of the direct drive motor. In addition, the
form of the oscillation wave is also readily modified by
controlling the output of the direct drive motor for the brush.
[0016] A brief review of some equations of motion for a harvesting
brush will be undertaken. For simplification purposes, a simple
harmonic sine/cosine motion will be used in the analysis.
Typically, a harvesting brush is constructed of a series of rings
having an inside diameter, wherein a number of shaker tines are
mounted in each ring, the tines extending outwardly around the
entire periphery of the ring. A plurality of rings are mounted side
by side to form a cylinder having an inside diameter. A plurality
of radially extending tines project from the cylinder. The inside
diameter of the cylinder formed by the plurality of rings is left
free of other structure to accept a direct drive motor as will be
hereinafter explained.
[0017] A typical dimension for tine extension from the center of
the cylinder or axis of rotation of the harvesting brush is
approximately 27 inches. A typical oscillatory amplitude at the tip
of the tines is .+-.4 inches. The angular displacement of the tips
of the tines in radians then computes to 0.149 radians. In terms of
a hydraulic motor, for purposes of this explanation, a motor size
which exhibits 2.pi. radians of shaft rotation for 24 cubic inches
of hydraulic flow is selected. With such a motor size for the
desired tine tip amplitude of .+-.4 inches, a hydraulic flow of
0.57 cubic inches is required. It remains to find a maximum flow
rate for the hydraulic motor in cubic inches per second for a
selected maximum operating frequency, .omega.. The equations of
motion, where G is flow displacement in cubic inches and Q is flow
rate, G=A cos(.omega.t) and Q=-A.omega.sin(.omega.t). Since the
negative sign in the expression for Q merely keeps track of phase
angle between displacement and velocity it is of no interest and is
dropped resulting in the expression Q=A.omega.sin(.omega.t) cubic
inches per second. For displacement A of 0.57 cubic inches and an
operating frequency .omega. of 400 cycles per minute, Qmax [when
sin(.omega.t)=1] computes to 6.2 gallons per minute. It may be seen
in a hydraulic system conforming to this example that the
displacement of the tine tips A on the shaker brush may be
adjusted, hydraulic fluid flow rate Q through the hydraulic motor
may be adjusted, and the frequency of oscillation .omega.of the
harvester brush may be adjusted. Components chosen for the
hydraulic system to function as hereinbefore described include a
hydraulic valve (Parker D1FHE50MCNBJ00), hydraulic motor (Parker
NE0395-BS-03-0-AAAB), and valve controller (Parker PMC-10E). It is
envisioned that the foregoing hydraulic components could be
replaced by appropriate pneumatic components or appropriate
electrical components to obtain control of the characteristics of a
shaker brush similar to those recited herein for the hydraulic
system.
[0018] With reference now to FIG. 1, a system constructed in
conformance with the foregoing analysis is pictured. A crop
harvester 10 is shown in FIG. 1 having a framework 11 on which is
mounted a harvester propulsion unit 12. Harvester 10 is supported
on an underlying surface 13 by a plurality of wheels 14. The wheels
14 are connected to and driven by the propulsion unit 12 so that
the harvester 10 is moveable over the underlying surface. A split
crop harvesting brush having a left harvesting brush half 16 and a
right harvesting half 17 is shown in FIG. 1, wherein an axial shaft
18 is shown on brush 16 and an axial shaft 19 is shown on brush 17.
One end of the axial shaft 18 is journalled in the frame 11 by
means of a bearing 21. One end of axial shaft 19 is also journalled
in the framework 11 by means of a bearing 22. The brushes are
therefore free to rotate in the framework about substantially
co-linear axes. A hydraulic motor 23 is shown situated between the
left and right brush halves 16 and 17 having a motor case 23a and a
motor output shaft 23b. A coupling 24 is shown fixing the output
shaft 23b to an opposing end of the left brush half shaft 18.
Another coupling 26 is shown coupling the motor case 23a to an
opposing end of the right brush half axial shaft 19. The motor 23
is shown in FIG. 1 externally of the brush halves 16 and 17,
whereas the brush halves in practice could be moved together and
the motor 23 placed within the aforementioned inner diameter within
the brush halves formed by the side by side rings which hold the
radially outward extending tines, as previously described
herein.
[0019] FIG. 1 further includes a hydraulic power source 27 shown in
dashed lines, a hydraulic fluid reservoir 28 and a hydraulic pump
29. As shown, hydraulic flow is directed to a valve 31 and return
flow is conducted from the valve to the fluid reservoir. Valve
controller 32 is connected to the valve 31 that operates to control
the fluid flow from the valve 31 to the hydraulic motor 23. Valve
controller 32 provides for operator adjustable parameters for the
valve 31 so that aspects of the hydraulic motor 23 are controllable
thereby. An operator controllable speed or frequency input 33,
displacement or amplitude input 34 and time rate of change of
amplitude or wave shape 36 are provided. In this fashion, the
frequency of the oscillation brush halves 16 and 17, the amplitude
of the oscillation and the shape of the amplitude as a function of
time are controllable by an operator of the harvesting machine.
Power transfer device or swivel 37 is shown situated between the
valve 31 and the hydraulic motor 23 to transfer power between the
valve and the hydraulic motor while accommodating rotation of the
hydraulic motor relative to the frame mounted valve 31. FIG. 1
therefore depicts schematically a crop harvester which has a
harvester brush assembly driven directly by a motor, wherein the
motor output shaft characteristics, i.e., frequency, displacement
and wave shape, are controllable by an operator "on-the-fly" as the
harvesting machine travels along the underlying surface 13
accomplishing its harvesting mission.
[0020] It should be noted that neither the shaft 23b nor the motor
case 23a is fixed rotationally. The combined inertia about the
brush axis of the motor case 23a and the brush 17 fixed to the
motor case will likely be substantially the same as the combined
inertia of the shaft 23b and the brush 16 fixed to the shaft. This
results when the brush inertias are similar because they are
considerably larger than the shaft and motor case inertias. In this
instance, when the motor 23 is powered by hydraulic flow, the shaft
will rotate through an angle in one direction and the motor case,
in reaction, will rotate through a similar angle in an opposing
direction. In an instance where it is desirable to have unequal
angles of departure (oscillation) from an at rest position in the
brush, a predetermined ratio of inertias is imposed between the
shaft and motor case loads. The larger inertial element, whether it
is on the shaft or the case, will dictate a smaller angle of
departure from the neutral or at rest position than the smaller
inertial element. This invention envisions control of the relative
angles of oscillation from neutral for the brush or brushes through
predetermination of the inertial loads carried by the motor shaft
and the motor case.
[0021] As seen in FIG. 2, a block diagram of a power source 38
connected to a power distribution device 39 is shown. A control 41
is connected to the power distribution device and output from the
power distribution device is shown at A and B in FIG. 2. FIG. 2
shows a general combination of power source, power distribution and
controller, whereas FIG. 1 is hydraulic specific. Power source
27,valve 31 and valve controller 32 of FIG. 1 correspond to power
source 38, power distribution device 39 and control 41 of FIG. 2
respectively. Power source 38 could be pneumatic or electrical in
FIG. 2 and power distribution element 39 could be a pneumatic valve
or an electrical distribution circuit respectively. Controller 41
would then take the form of a controller for the pneumatic valve or
a controller for the electrical distribution circuit, whichever
appropriate. The controller 41 in a hydraulically powered
embodiment of the invention dictates flow quantity, flow direction
or sense and the time rate of change of the flow quantity or cyclic
wave shape. In the instance where the power source 38 is a
pneumatic source, the motor 23 of FIG. 1 would then be a
pneumatically driven motor. In the event where the power source 38
is an electrical power source, the motor 23 of FIG. 1 would take
the form of an electrical motor. The arrangement of FIG. 2 is
intended to show power distribution and distribution control
without regard for the character of the power source. Any power
source and power distribution control system falling within this
category is useful in the embodiment of FIG. 1 or in any of the
embodiments to be hereinafter described. In the following
embodiment descriptions the power source and power distribution
control is represented by the input A and B with an appropriate
direct drive motor responsive to the power source elected whether
it be hydraulic, pneumatic, electrical, or otherwise. It should be
noted again that with the power source and power distribution
control of FIG. 2 there is no need to halt harvesting operations to
change harvesting brush characteristics as is the case when
changing harvester brush characteristics in other currently known
harvesting machines.
[0022] With regard to FIG. 3, the framework 11 is shown having
bearings 21 and 22 mounted therein for supporting (or, as used
herein, journalling) opposing ends of a brush and a direct drive
motor assembly. The harvester brush 42 has one end supported in the
bearing 21 and an opposing end joined by a coupler 43 to an output
shaft 44 on a motor 46. An extension 47 of the case of the motor 46
is supported in the bearing 22. The motor 46 is actuated by
distributed power at the points A and B obtained as previously
explained in conjunction with the description of the diagram of
FIG. 2. An inertial member 48 is fixed to the case of the motor 46,
serving as a reaction force to rotation of the motor output shaft
44. Inertial member 48 is shown in section in FIG. 3 for clarity. A
connection point 49 is formed on the inertial member 48, serving as
an anchor for a pair of coil springs 51 and 52 as seen in FIG. 3A.
Opposing ends of the springs 51 and 52 are attached to points on
the frame 11 as shown. Coil springs 51 and 52 shown in FIG. 3A
operate as centering springs and could as readily be leaf springs,
etc. The centering springs allow the case of motor 46 to oscillate
in response to the motion of the output shaft 44, but not to
rotate. The oscillation amplitude of the motor case 46 is designed
to be significantly less than the oscillation amplitude of the
motor shaft 44 and brush 42 combination by appropriate selection of
inertial member 48. Therefore, in the embodiment of FIG. 3 no
swivel is necessary for transferring the distributed power to the
motor 46. Flexible hoses accomplish the transfer because the motor
46 does not continuously rotate relative to the framework 11.
[0023] FIG. 4 shows the framework 11 and the bearings 21 and 22
functioning to support opposing ends of the shaker brush and drive
motor assembly of FIG. 4. The embodiment of FIG. 4 shows a left
motor 53 and a right motor 54. The left motor 53 has its case
mounted on a plate 56 and right motor 54 has its case mounted on a
plate 57. A connecting member or torsion member 58 is shown
connected between the plates 56 and 57. The connecting member 58
prevents the cases of motors 53 and 54 from rotating relative to
one another. An extension 59 from the case of motor 53 is supported
within the bearing 21. An extension 61 of the case of motor 54 is
supported within the bearing 22. A left crop foliage engaging brush
62 is shown together with a right crop foliage engaging brush 63.
Left motor 53 has an output shaft 64 and right motor 54 has an
output shaft 66. A coupling 67 connects output shalt 64 to one end
of crop foliage engaging brush 62 and another coupling 68 connects
output shaft 66 to one end of right crop foliage engaging brush 63.
The opposing ends of the left and right crop foliage engaging
brushes 62 and 63 are connected in rotating relationship by a
bearing 69 as seen in FIG. 4. The motors 53 and 54 are connected to
the points A and B at the output of the controlled and distributed
power system of FIG. 2 so that the output shafts 64 and 66 will
rotate in opposite directions about the shaft axis. The torques at
the cases of the motors 53 and 54 will cancel through the
connecting member 58. The connecting or torsion member 58 is shown
in FIG. 4 as passing outside the diameter of the brush tines for
clarity only. It could as well pass along the inside diameter
passage inside the tine holding rings as discussed in the
description of the harvesting brush structure hereinbefore. In the
event the embodiment of FIG. 4 is caused to rotate relative to the
framework 11, a power transfer device or swivel 71 is used to
accommodate rotation between the cases of motors 53 and 54 and the
framework 11 of the crop harvester 10.
[0024] Yet another embodiment of the present invention is seen in
FIG. 5 wherein the harvester framework 11 has bearings 21 and 22
mounted therein for supporting one end of a left harvester brush
assembly 72 and one end of a right harvester brush 73. Left direct
drive motor 74 is mounted to a plate 76 and a right direct drive
motor 77 is mounted to a plate 78. Left direct drive motor 74 has
an output shaft 79 which is connected by a coupling 81 to an
opposing end of the left harvester brush 72. Right direct drive
motor 77 has an output shaft 82 which is connected by means of a
coupling 83 to an opposing end of the right harvester brush 73. A
connecting member 84 is joined to the peripheral regions of both
plates 76 and 78. The connecting member 84 may take the form of a
tube enclosing the motor cases. In this fashion the cases of the
direct drive motors 74 and 77 are prevented from rotating relative
to each other. Direct drive motors 74 and 77 are connected to the
controlled and distributed power outputs A and B in such a fashion
as to cause rotation of their respective output shafts 79 and 82 in
opposite directions about the axis of the assembly of FIG. 5. In
most cases it will be preferred that the motors 74 and 77 are
identical in characteristics, but unequal motors could also be
used. Motors of dissimilar size will result in dissimilar torques
at shafts 79 and 82. In the event that the embodiment of FIG. 5 is
configured to rotate about the axis of the harvester brushes 72 and
73 as it passes through the foliage of a crop being harvested, a
device for transferring power from the framework 11 to the direct
drive motors 74 and 77 such as swivel 86 will be required.
Conversely, if it is not necessary to allow the harvester brushes
72 and 73 to rotate through the plant foliage, no swivel 86 is
required.
[0025] Turning now to FIG. 6 of the drawings, an embodiment using
piston motors is displayed. The embodiment is disclosed in
conjunction with hydraulically driven piston motors. A first lever
corresponding to some degree to the connecting members 58 and 84 in
FIGS. 4 and 5, respectively, is shown as item 87. Lever 87,
vertically disposed in FIG. 6, has an upper pivot point 88 and a
lower pivot point 89. An upper cylinder 91 is pivotally attached at
pivot point 88 and a lower cylinder 92 is pivotally attached at
lower pivot point 89. An additional lever 93, horizontally disposed
in the depiction of FIG. 6, has a left pivot point 94 thereon and a
right pivot point 96. Cylinder 91 has a piston 97 contained therein
(FIG. 8) to which is attached a piston rod 98 extending outwardly
therefrom through a sealed aperture. The piston motor shown in FIG.
8 has equal piston area on opposing sides of the piston so that
similar flow into either cylinder chamber provides similar force in
opposing directions along the piston rod 98. A free end of the
piston rod 98 is pivotally attached at the pivot point 94. Cylinder
92 contains a piston similar to piston 97, having a piston rod 99
extending therefrom through a sealed aperture. Free end of piston
rod 99 is pivotally attached at pivot point 96 on the lever 93.
FIG. 7 is a partial section taken from FIG. 6 showing the levers 87
and 93 positioned with a thrust bearing 101 therebetween so that
they may freely rotate relative to one another about an axis 102. A
fastening member 103 extends along the axis 102 between the levers
87 and 93 having a bearing 104 at one end thereof to preserve
independent rotation between the levers. A left harvesting brush
106 and a right harvesting brush 107 are shown in FIG. 7 connected
by fastening means 108 to the lever 93 and the lever 87,
respectively. Opposing ends of brush 106 and 107 are supported in
the harvester framework 11 by bearings 21 and 22, respectively. As
in the other embodiments disclosed herein having more than one
actuator or motor directly connected to the harvester brushes,
power to points A and B in FIG. 6 from the controlled and
distributed power at points A and B of FIG. 2 is simultaneously
delivered to points A or B at the piston motors of the embodiment
of FIG. 6. Also, as in the previously described embodiments of this
invention, if it is desirable for the harvester brushes 106 and 107
to rotate through the foliage of the crop being harvested, a power
transfer device (i.e., hydraulic swivel electrical slip rings,
etc.) must be positioned between the framework 11 and cylinders 91
and 92 in the direct drive piston motors of FIG. 6.
[0026] Although the best mode contemplated for carrying out the
present invention has been shown and described herein, it will be
understood that modification and variation may be made without
departing from what is regarded to be the subject matter of the
invention.
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