Case 1:17-cv-00770-RGA-MPT Document 62-1 Filed 11/18/21 Page 1 of 75 PageID #: 9861
`Case 1:17-cv-00770-RGA-MPT Document 62-1 Filed 11/18/21 Page 1 of 75 PagelD #: 9861
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`EXHIBIT 1
`EXHIBIT 1
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`USOO7523995B2
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`(12) United States Patent
`Rio et al.
`
`(10) Patent No.:
`(45) Date of Patent:
`
`US 7,523,995 B2
`Apr. 28, 2009
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`(54) MILLING MACHINE
`(75) Inventors: Federico B. Rio, Bologna (IT): Dean R.
`Potts, Maple Grove, MN (US); Gregory
`H. Dubay, Bologna (IT): Dario
`Sansone, Castello d'Argile (IT)
`(73) Assignee: Caterpillar Paving Products Inc.,
`Minneapolis, MN (US)
`
`(*) Notice:
`
`Subject to any disclaimer, the term of this
`patent is extended or adjusted under 35
`U.S.C. 154(b) by 440 days.
`(21) Appl. No.: 11/180,688
`(22) Filed:
`Jul. 14, 2005
`(65)
`Prior Publication Data
`US 2006/0024134 A1
`Feb. 2, 2006
`
`Foreign Application Priority Data
`(30)
`Jul. 15, 2004
`(IT)
`.......................... TO2OO4AO499
`
`(51) Int. Cl.
`(2006.01)
`EOIC 23/088
`(52) U.S. Cl. ........................ 299/39.6: 404/90; 180/209;
`299/.394
`(58) Field of Classification Search .................. 299/1.4,
`299/15, 39.1, 39.3, 39.4, 39.6; 180/209;
`280/43, 43.17, 6.155; 404/84.05, 90, 93,
`404794
`See application file for complete search history.
`References Cited
`
`(56)
`
`U.S. PATENT DOCUMENTS
`
`7, 1992 Whitaker et al.
`5,127,335 A
`1 1/2002 Smolders et al.
`6,481,924 B1
`2002/01750 18 A1* 1 1/2002 Strong ........................ 180,412
`
`FOREIGN PATENT DOCUMENTS
`
`BE
`EP
`EP
`WO
`
`895198 A2
`O 916 004 B1
`1039037
`WOO2,103 117
`
`3, 1983
`9, 1999
`9, 2000
`12/2002
`
`* cited by examiner
`Primary Examiner Sunil Singh
`(74) Attorney, Agent, or Firm—Finnegan, Henderson,
`Farabow, Garrett & Dunner
`
`(57)
`
`ABSTRACT
`
`Work machines such as road mills having a frame Supported
`by tracked or wheeled ground engaging Support units may
`require the ability to move one or more of the ground engag
`ing units between projecting and retracted positions relative
`to the frame without reversing the running direction of the
`repositioned unit. A disclosed work machine has a machine
`frame Supportable by a plurality of ground engaging units. A
`Support device connected between the machine frame and at
`least one of the ground engaging units has a lifting column
`adapted to controllably raise and lower the ground engaging
`unit relative to the frame. A first actuator is connected to the
`Support device to move the one ground engaging unit between
`the projecting and retracted positions, and a second actuatoris
`connected to the lifting column to maintain the running direc
`tion of the associated ground engaging unit in each of the
`projecting and retracted positions.
`
`4,558,758 A * 12/1985 Littman et al. ............... 1808.1
`
`63 Claims, 5 Drawing Sheets
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`COLUMN
`RASE/LOWER
`COMMAND
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`STEERING
`COMMAND
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`COMMAND
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`BRAKE is
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`COLUMN
`POSITION
`SENSOR
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`DOOR
`SENSOR
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`PIVOT
`SENSOR
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`ROTATE
`SENSOR
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`LIFTING
`COLUMN
`ACTUATOR
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`FIRST
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`CONTROLLER
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`SECOND
`ACTUATOR
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`85
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`ANTI-SWING
`ACTUATOR
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`ANT-ROTATE
`ACTUATOR
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`US 7,523,995 B2
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`1.
`MILLING MACHINE
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`TECHNICAL FIELD
`
`The present invention relates generally to work machines
`for the treatment of roadway Surfaces, and more particularly
`to a road planer or milling machine.
`
`BACKGROUND
`
`Road mills, sometimes called cold planers or scarifiers, are
`work machines that typically include a frame quadrilaterally
`supported by tracked or wheeled support units. The frame
`Supports machine components, including an engine, an
`operator's station, and a milling drum. The milling drum,
`fitted with a plurality of milling tools, is rotated through a
`Suitable interface by the engine to break up a road Surface.
`The Support units generally include lift columns mounted
`between the frame and the tracks or wheels. Extending or
`retracting the lift columns raises or lowers the frame and
`milling drum relative to the tracks or wheels and, conse
`quently, relative to the ground. At least one of the Support
`units, typically a rear unit, is commonly constructed in a
`manner permitting it to Swing or pivot between two different
`operating positions: a projecting position in which the track
`or wheel is positioned substantially outside of the boundaries
`of the machine frame for maximum stability, and a retracted
`position in which the track or wheel is positioned Substan
`tially within the boundaries of the machine frame to enable
`the machine to mill road surfaces close to a curb or wall, for
`example.
`Typically, the tracks or wheels, including the pivotable
`unit, are driven for traction purposes by individual hydraulic
`motors. The necessary pressurized hydraulic fluid is Supplied
`by a pump driven by the frame mounted engine. To move the
`pivotable Supportunit from one position to the other position,
`an operator uses the lift column to lower the frame with
`respect to the Supportunit until the milling drum (or another
`frame mounted component) rests on the ground. Continued
`operation of the lift column raises the track or wheel off the
`ground so that the Support unit can be pivoted. However,
`absent some correction mechanism, repositioning the Support
`unit in this manner also causes the track or wheel to reverse its
`direction of rotation or running direction. Consequently, it is
`desirable to counter-rotate the track or wheel relative to the
`rotation caused by the repositioning to maintain the original
`alignment and direction of rotation, regardless of whether the
`Support unit is in the projecting or retracted position.
`EP 0916 004 proposes using a guide-rod gear to provide a
`pivotable support unit with a counter-rotatable wheel. The
`guide-rod gear is shown connected between the machine
`frame and the Supportunit, and consists of a four-bar linkage
`mechanism having four vertical articulated axles and two
`guide rods pivotable in a horizontal plane. A single hydraulic
`actuator causes the four-bar or parallelogram type linkage to
`pivot the rear wheel supported by a non-rotatable lift column
`between the projecting and retracted positions, while counter
`rotating the wheel and lift column. This design causes the
`weight of the machine resting on the pivotable rear wheel to
`be carried by the four-link mechanism, which may result in
`reduced stability and stiffness of the machine. Also, precise
`and potentially wear-prone couplings have to be employed.
`Further, road mills must be steered, and optimum steering
`angles differ in accordance with the well-known Ackerman
`principle when the Support unit is in the retracted position
`Versus the projecting position. This is a particular problem
`when the machine is fitted with tracks instead of wheels,
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`because the rear tracks, especially the retracted rear track,
`must be steered in concert with the front tracks to avoid
`dragging or skipping of the rear tracks on the road Surface.
`The single actuator guide-rod system of EPO 916 004 does
`not provide integrated Steering capability of the pivotable rear
`wheel, and is not well suited for use with machines fitted with
`tracks.
`International publication WO 02/103117 describes another
`road mill of the general construction discussed above, and
`offers improvements over the guide-rod system. Instead of a
`four-bar linkage, the Support unit is mounted on a sturdy
`Support or Swing arm that is pivotally connected to the
`machine frame with a single large pivot pin. This arrangement
`eliminates the need for a multi-piece linkage. Such as the
`guide rod gear, with numerous pivot joints. The Support arm
`may be pivoted by means of a linear hydraulic cylinder con
`nected between the arm and the frame. A second linear
`hydraulic cylinder is described connected between the Sup
`port arm and an axially rotatable portion of the lift column
`that is, in turn, connected to the track or wheel. When the
`support arm is pivoted by the one hydraulic cylinder the track
`or wheel may be counter-rotated by the other hydraulic cyl
`inder, allowing the Supportunit to Swing between the project
`ing and retracted positions while maintaining constant the
`running direction of the associated track or wheel. Because of
`the independent action of the two hydraulic cylinders, steer
`ing of the pivotable track or wheel can be accomplished using
`the second hydraulic cylinder, making this design Suitable for
`use with machines fitted with either tracks or wheels.
`The above described mechanisms provide different solu
`tions to the problem of pivoting a machine Support unit
`between projecting and retracted positions while maintaining
`the running direction of the pivoted track or wheel, but both
`Solutions place bulky mechanical devices at a location on the
`Support unit which must fit into a tightly confined space,
`especially in the retracted position. In addition, the guide rod
`gear arrangement is not suitable for steering the Supportunit,
`and fine steering control can be difficult to achieve using the
`hydraulic linear cylinder arrangement. The present invention
`is directed to overcoming one or more of these and other
`problems or disadvantages associated with the prior art.
`
`SUMMARY OF THE INVENTION
`
`In accordance with one embodiment of the present inven
`tion, there is provided a work machine having a frame Sup
`portable by a plurality of ground engaging units. A Support
`device is connected between the frame and at least one of the
`ground engaging units, and a first actuator connected to the
`Support device is adapted to move the one ground engaging
`unit between projecting and retracted positions relative to the
`frame. A second actuator associated with the one ground
`engaging unit is adapted to maintain the same rotational
`direction of the ground engaging unit in each of the projecting
`and retracted positions. A controller coordinates the actuation
`of the first and second actuators, at least one of which is a
`rotary actuator.
`In accordance with another embodiment of the present
`invention, there is provided a work machine having a frame
`Supportable by a plurality of ground engaging units. A Sup
`port device is connected between the frame and at least one of
`the ground engaging units, and includes a lifting column
`adapted to controllably raise and lower the associated ground
`engaging unit relative to the frame. A first actuator is con
`nected to the Support device and is adapted to move the one
`ground engaging unit between projecting and retracted posi
`tions relative to the frame. A second actuator is positioned at
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`3
`a location linearly spaced apart from the first actuator along
`an axis of the lifting column and is adapted to cause at least a
`portion of the column to rotate relative to the machine frame
`about the column axis.
`In accordance with another embodiment of the present
`invention, there is disclosed a method of controlling a pair of
`actuators connected to a controller to selectively position one
`of a plurality of ground engaging units connected to a respec
`tive lifting column and Supporting a frame of a self-propelled
`work machine. The method includes the steps of raising the
`one ground engaging unit with the lifting column until the
`unit is free from engagement with the ground, actuating a first
`one of the actuator pair to move the ground engaging unit
`from one to the other of the projecting and retracted positions
`relative to the machine frame, actuating a second one of the
`actuator pair to rotate the one ground engaging unit about the
`lifting column axis in a manner coordinated with the actua
`tion of the first actuator to maintain the same rotational direc
`tion of the ground engaging unit in each of the projecting and
`retracted positions, and lowering the one ground engaging
`unit with the lifting column until the unit is again in frame
`Supporting engagement with the ground.
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`BRIEF DESCRIPTION OF THE DRAWINGS
`
`FIG. 1 is a line drawing of a top plan view of a work
`machine in which features of the present invention may be
`incorporated;
`FIG. 2 is a partially sectioned longitudinal view of a detail
`of a cold planer as depicted in FIG. 1, showing an articulation
`apparatus of a preferred embodiment of the present invention;
`FIG. 3 is a partially sectioned top plan view of the appara
`tus of FIG. 2, with the ground engaging unit arranged in a
`retracted position relative to the frame;
`FIG. 4 is a partially sectioned top plan view of the appara
`tus of FIG. 2, with the ground engaging unit arranged in a
`protracting position relative to the frame; and
`FIG. 5 is a block diagram of control logic associated with
`an embodiment of the present invention.
`
`DETAILED DESCRIPTION
`
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`The self-propelled work machine 10 of FIG. 1 includes a
`machine frame 12 Supportable by a plurality of ground engag
`ing units 14, 16, 18, 20. In a preferred embodiment, the
`plurality of ground engaging units 14, 16, 18, 20 includes a
`pair of front ground engaging units 14, 16 and a pair of rear
`ground engaging units 18, 20. The ground engaging units 14,
`16, 18, 20 each include either a wheel or a track section. At
`least one of the ground engaging units 14, 16, 18, 20, for
`example, the right rear ground engaging unit 20 as seen from
`the operator's perspective, may be pivotable between a pro
`jecting position as shown in Solid lines in FIG. 1 and a
`retracted position in which the one ground engaging unit 20 is
`positioned within the frame 12 as indicated by the recess 22
`shown in hidden lines.
`The frame 12 also Supports an operator's station 24 having
`a steering command element 26, an engine 28 Such as an
`internal combustion engine, and a milling roller 30. The steer
`ing command element 26 is shown to include a steering
`wheel, but other steering devices such as a joystick of levers
`could be used as well. The engine 28 supplies power to drive
`one or more of the ground engaging units 14, 16, 18, 20 to
`propel the work machine 10 relative to the ground. In a
`preferred embodiment, this is accomplished by driving a
`hydraulic pump with an output of the engine 28, which in turn
`supplies high pressure hydraulic fluid to individual hydraulic
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`motors associated with the ground engaging units 14, 16, 18.
`20. This conventional hydraulic drive is well-known in the
`pertinent art and is not depicted in the drawings. The engine
`28 also supplies power to rotate the milling roller 30, for
`example, to break up a road Surface. The broken up material
`may be carried away from the work machine 10 by a conveyor
`31.
`Steering the front ground engaging units 14, 16 of the
`machine 10 may be accomplished in a conventional manner
`using a mechanical linkage from the steering command ele
`ment 26 to the front ground engaging units 14, 16, or by
`detecting motion of the steering command element 26 using
`an appropriate transducer to sense the desired steering motion
`and responsively controlling an actuator Such as a hydraulic
`cylinder associated with the front ground engaging units 14,
`16. This may be accomplished, for example, by delivering
`steering command signals from the steering command ele
`ment 26 to a controller 32 carried on the machine frame 12,
`Such as a programmed computer logic unit and associated
`memory. In a manner well-known in the art, the controller 32
`would translate the steering command signals into appropri
`ate actuation signals delivered to the actuator associated with
`the front ground engaging units. Such steering devices are
`well known in the art and are not depicted in the drawings.
`Steering the rear ground engaging units 18, 20 of the
`machine 10 is more complicated, because the one rearground
`engaging unit 20 may either be in the projecting position
`where it is axially aligned with the other rearground engaging
`unit 18, or in the retracted position where it is not axially
`aligned with the other rear ground engaging unit 18. Depend
`ing on the position of the one ground engaging unit 20, the
`Steering angle of the one ground engaging unit 20 may require
`correction in accordance with the well-known Ackerman
`principle to properly coordinate the steering effect with the
`steering angle of the front ground engaging units 14, 16. Such
`correction may be provided by the controller 32 as is dis
`cussed more fully below.
`Referring now primarily to FIGS. 2 through 4, the work
`machine 10 includes a support device 40 connected between
`the machine frame 12 and the one ground engaging unit 20. A
`first actuator 42 is connected to the support device 40 and is
`adapted to move the one ground engaging unit 20 between the
`projecting position (see FIG. 4) and the retracted position (see
`FIG. 3) relative to the frame 12. A second actuator 44 is
`associated with the Support device 40 and is adapted to main
`tain the same rotational direction of the one ground engaging
`unit 20 in each of the projecting and retracted positions. Each
`of the first and second actuators 42, 44 is associated with the
`controller 32, which is adapted to coordinate the actuation of
`the actuators 42, 44.
`The support device 40 includes a lifting column 46 adapted
`to controllably raise and lower the associated connected
`ground engaging unit 20 relative to the machine frame 12. In
`a typical embodiment of the work machine 10, each of the
`ground engaging units 14, 16, 18, 20 will include a respective
`support device 40 and lifting column 46. The second actuator
`44 is connected to the lifting column 46 and is adapted to
`cause at least a portion of the lifting column 46 to rotate about
`a lifting column axis 48 that is oriented generally vertically
`relative to the work machine 12.
`In one of the preferred embodiments, at least one of the first
`and second actuators 42,44 is a rotary actuator. An actuator of
`the sort available from the Helac Corporation of Enumclaw,
`Wash., for example, the L20 Series Hydraulic Rotary Actua
`tor, has been found to be particularly advantageous in this
`application. This actuator uses a double helix sliding spline
`design to produce high torque rotary motion in a compact
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`device. However, other rotary actuators such as worm or Sun
`gear designs that are well-known mechanical implementa
`tions may also be employed with good result. Such use of a
`rotary actuator provides a compact apparatus to achieve
`rotary motion without the need for complicated and bulky
`linkages, and may also be used to provide fine rotary steering
`control.
`In another of the preferred embodiments, the second actua
`tor 44 is positioned on the lifting column 46 at a location
`spaced apart from the first actuator 42 along the lifting col
`umn axis 48. Preferably, the second actuator 44 is located at
`an upper portion 50 of the lifting column 46 and the first
`actuator 42 is located at a lower portion 52 of the lifting
`column 46. Such spaced apart positioning avoids problems
`caused by an accumulation of mechanical devices at a single
`location on the lifting column 46.
`These embodiments may be advantageously combined by
`employing a rotary actuator as described above as either or
`both of the first and second actuators 42, 44, and by position
`ing these actuators at the specified longitudinally spaced apart
`locations. In this respect, it may also be preferable that at least
`the second actuator 44 be implemented using the rotary actua
`tor construction and placed at the upper portion of the lifting
`column 46.
`As best seen in FIG. 2, the one ground engaging unit 20 is
`supported by a bracket 54. The bracket 54 may be a simple
`axial wheel Support as pictured, or may support a track sec
`tion having rollers, tensioning devices, etc., as is well-known
`in the art. In either case, the track or wheel is adapted to
`revolve in both forward and reverse directions about an axis
`56.
`The lifting column 46 is preferably a hydraulically actu
`ated mechanism that includes an inner tubular member 58that
`is slidable within an outer tubular member 60. The inner
`tubular member 58 is connected to the bracket 54, and the
`outer tubular member 60 is connected to a component of the
`support device 40 which is pivotally connected to the machine
`frame 12.
`The inner tubular member 58 may be moved longitudinally
`vertically relative to the outer tubular member 60 by means of
`40
`a lifting column actuator 62. The lifting column actuator 62
`includes a piston rod 64 connected at one end to the bracket 54
`and slidable within a cylinder 66. The cylinder 66 is supported
`in a rotatably slidable arrangement at one end by a flange 68
`that rests on the outer tubular member 60. The piston rod 64
`and cylinder 66 together constitute a linear hydraulic actuator
`in which the piston rod 64 may be driven in or out of the
`cylinder 66 by the application of hydraulic fluid (not shown).
`Such linear movement of the piston rod 64 causes the inner
`tubular member 58 to move axially within the outer tubular
`member 60, in turn causing the associated ground engaging
`unit 20 to move generally vertically relative to the machine
`frame 12.
`In a preferred embodiment, the housing of the second
`actuator 44 is connected, for example by bolts, to the top of
`the outer tubular member 60. A rotor 70 of the second actuator
`44 includes one or more protrusions 72 that project into
`mating recesses in the top of the cylinder 66. Consequently,
`rotation of the second actuator rotor 70 causes the cylinder 66
`to rotate as the cylinder flange 68 slides on the outer tubular
`member 60. Free sliding rotation of the flange 68 may be
`enhanced as desired with, for example, lubricants, anti-fric
`tion materials such as TFE, or bearings. The cylinder 66 is
`engaged with the inner tubular member 58 by a pair of keys 74
`fitted into corresponding longitudinal keyways. This key and
`keyway arrangement permits linear sliding movement
`between the inner tubular member 58 and the cylinder 66,
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`while preventing relative rotational movement between these
`components. As a result, actuation of the lifting column
`actuator 62 moves the one ground engaging unit 20 up and
`down vertically relative to the machine frame 12, and actua
`tion of the second actuator 44 moves the one ground engaging
`unit 20 rotationally about the lifting column axis 48. A rota
`tion sensor 75, for example, a rotary encoder, may be associ
`ated with the second actuator 44 or with a connected rotating
`component to deliver signals representing the rotation angle
`of the one ground engaging unit 20 relative to the machine
`frame 12.
`The support device 40 includes a swing arm 76 having a
`first end portion 78 pivotally connectable to the machine
`frame 12 with a pivot pin 80, and a second end portion 82
`connected to the outer tubular member 60. Consequently, the
`machine frame 12 supports the swing arm 76 and outer tubu
`lar member 60, which in turn supports the lifting column
`actuator 62 which is connected to the bracket 54 holding the
`one ground engaging unit 20. Actuation of the first actuator 42
`causes the Swing arm 76 to pivot about the pivot pin 80,
`moving the one ground engaging unit 20 between the project
`ing and retracted positions. A pivot sensor 83, for example, a
`linear sensor associated with the first actuator 42 or a rotary
`encoder associated with the pivot pin 80 may deliver signals
`representing the pivot angle of the one ground engaging unit
`20 relative to the machine frame 12.
`An anti-swing device 84 connected to the swing arm 76
`includes an anti-Swing actuator 85 having a protrusion 86 that
`is controllably engageable with either of a pair of receptacles
`88 such as holes or recesses in the machine frame 12. The
`protrusion 86 may be deployed in response to the one ground
`engaging unit 20 being positioned at either of the protruding
`and retracted positions. This locks the Swing arm 76 against
`unintentional pivotal movement relative to the machine frame
`12. The anti-swing device 84 may conveniently be hydrauli
`cally or electrically actuated, although it could also be manu
`ally actuated.
`An anti-rotate device 90 includes a collar 92 connected
`with collar keys 94 to the inner tubular member 58, causing
`the collar 92 to rotate along with the inner tubular member 58
`in response to actuation of the second actuator 44. The collar
`90 includes a pair of receptacles 96 such as holes or recesses
`in spaced apart locations about the collar periphery. An anti
`rotate actuator 98 includes a body portion 100 connected to
`the machine frame 12 and a protrusion 102 controllably
`engageable with either of the pair of collar receptacles 96 in
`response to the one ground engaging unit 20 being direction
`ally aligned with the machine frame 12 and being positioned
`at a corresponding respective one of the projecting and
`retracted positions. This permits locking the inner tubular
`member 58 and the one ground engaging unit 20 against
`unintentional rotational movement when steering control of
`the one ground engaging unit 20 is not desired. The anti-rotate
`device 90 may conveniently be hydraulically or electrically
`actuated, although it could also be manually actuated.
`The controller32 includes a plurality of input interfaces for
`receiving information and command signals from various
`switches and sensors associated with the work machine 10
`and a plurality of output interfaces for sending control signals
`to various actuators associated with the work machine 10.
`Only those input and output interfaces pertinent to the instant
`inventive embodiments are described below, but the suitably
`programmed controller 32 may serve many additional similar
`or wholly disparate functions as is well-known in the art.
`On the input side, the controller 32 may receive signals
`from one or more of the following: an operator initiated
`raise/lower switch command 110 to raise or lower one or
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`10
`
`15
`
`25
`
`30
`
`7
`more of the lifting columns; an operator initiated pivot Switch
`command 112 to pivot or Swing the one ground engaging unit
`20 from one of the projecting and retracted positions to the
`other, a steering command 114 from the steering command
`element 26; a brake set signal 116 from a sensor Such as a
`micro-switch associated with the machine parking brake (not
`shown) indicating that the brake is set and the machine 10 is
`stopped; a machine recess door position signal 118 from a
`sensor Such as a micro-Switch (not shown) indicating that a
`door covering the recess 22 is open or closed; a lifting column
`Vertical position signal 120; a ground engaging unit pivot
`position signal 122; and a ground engaging unit rotational
`position signal 124.
`The lifting column vertical position signal 120 may be
`produced by a sensor Such as a micro-switch or linear position
`sensor (not shown) associated with the lifting column indi
`cating that the one ground engaging unit 20 is in a position
`free from engagement with the ground Such that it may be
`pivoted relative to the machine frame 12. The ground engag
`ing unit pivot position signal 122 is from the pivot sensor 83
`associated with the first actuator 42 or the swing arm 76
`indicating the instantaneous angular position of the Swing
`arm 76 relative to the machine frame 12. The ground engag
`ing unit rotational position signal 124 is from the rotation
`sensor 75 associated with the second actuator 44 indicating
`the instantaneous rotation angle of the one ground engaging
`unit 20 relative to the machine frame 20.
`On the output side, the controller 32 may send control
`signals to one or more of the following: the lifting column
`actuator 62; the first actuator 42; the second actuator 44; the
`anti-swing actuator 85; and the anti-rotate actuator 98. In the
`case of electrically activated actuators, the control signals
`may act directly on the respective actuators. In the case of
`hydraulically activated actuators, the control signals may act
`on electrically controlled valves which in turn control the flow
`of pressurized oil to the actuators. The controller 32 may be a
`separate control unit or it may be part of a central control unit
`operable to control additional functions of the work machine
`10. In view of the foregoing disclosure, one skilled in the art
`may readily conceive or identify additional configurations of
`40
`the controller 32 sufficient to realize the desired control func
`tions.
`
`35
`
`INDUSTRIAL APPLICABILITY
`
`Case 1:17-cv-00770-RGA-MPT Document 62-1 Filed 11/18/21 Page 11 of 75 PageID #: 9871
`
`A work machine 10 equipped as described above may be
`operated in the following manner:
`Absent conditions calling for flush milling, the work
`machine 10 may be configured as shown in FIG.4, with the
`one ground engaging unit 20 in the projecting or outboard
`position relative to the machine frame 12. This configuration
`positions the ground engaging units 14, 16, 18, 20 in a con
`ventional axially aligned four point stance for maximum
`machine stability.
`When flush milling is desired, for example, along a curb or
`close to a wall, the operator may choose to move the one
`ground engaging unit 20 to the retracted position relative to
`the machine frame 12, as shown in FIG. 3. In the preferred
`embodiment disclosed above, this may be accomplished as
`follows:
`First, the operator stops the machine 10 and engages the
`parking brake which sends a brake set signal 116 to the
`controller 32.
`Next, the operator ensures that the door covering the recess
`22 is open, which sends a door position signal 118 to the
`controller 32.
`
`45
`
`50
`
`55
`
`60
`
`65
`
`8
`Next, the operator engages the lifting column raise/lower
`switch which sends a column switch command 110 to the
`controller 32, commanding that the lifting column 46 be
`raised relative to the machine frame 12. The controller 32
`responsively actuates the lifting column actuator 62, causing
`the piston rod 64 to retract into the cylinder 66 and raising the
`ground engaging unit 20 relative to the machine frame 12.
`This effectively lowers the frame 12 relative to the ground
`until the milling roller 30 or some other element associated
`with the frame 12 engages the ground and the ground engag
`ing unit 20 becomes free from ground engagement. Once a
`desired predetermined height of the one ground engaging unit
`20 is reached, the lifting column vertical position signal 120
`is delivered to the controller 32 and the lifting column actua
`tor 62 is deactivated. Typically, both of the rearground engag
`ing units 18, 20 are raised at the same time to keep the
`machine level.
`Next, the operator engages the pivot Switch which sends a
`pivot Switch command 112 to the controller 32, commanding
`that the one ground engaging unit 20 move from the project
`ing position to the retracted position. In response to receiving
`the permissive signals indicating that the machine is safely
`stopped, the recess cover is open, and the one ground engag
`ing unit 20 is suitably elevated, the controller 32 activates the
`anti-swing actuator 85 and the anti-rotate actuator 98 to
`release the corresponding protrusions 86, 102 from engage
`ment with the respective receptacles 88,96. Alternatively,
`these locking devices could be released by separate operator
`controlled Switches or