US3735818A - Motor-grader implements - Google Patents

Motor-grader implements Download PDF

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Publication number
US3735818A
US3735818A US00081744A US3735818DA US3735818A US 3735818 A US3735818 A US 3735818A US 00081744 A US00081744 A US 00081744A US 3735818D A US3735818D A US 3735818DA US 3735818 A US3735818 A US 3735818A
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auger
earth
hydraulic
subframe
control
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US00081744A
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G W Swisher
D W Smith
G L Oklahoma City Spivey
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CMI Terex Corp
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CMI Corp
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Assigned to COMMERCIAL BANK,N.A., REPUBLICBANK DALLAS,N.A., FIRST NATIONAL BANK OF CHICAGO, THE, HIBERNIA NATIONAL BANK IN NEW ORLEANS THE, MANUFACTURERS HANOVER TRUST COMPANY, CONTINENTAL ILLINOIS NATIONAL BANK AND TRUST COMPANY OF CHICAGO, BANK OF PENNSYLVAIA, MERCATILE NATIONAL BANK AT DALLAS COMMERCE BANK,, FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE, FIDELITY BANK N A., FEDERAL DEPOSIT INSURANCE CORPORATION AS RECEIVER FOR PENN SQUARE BANK,N.A., NORTHERN TRUST COMPANY, THE, BANK OF AMERICA NATIONAL TRUST AND SAVINGS ASSOCIATION, reassignment COMMERCIAL BANK,N.A. MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: CMI CORPORATION, CMI ENERGY CONVERSION SYSTEMS,INC., CMI INTERNATIONAL CORPORATION, CMI OIL CORPORATION, CRAMCO SPECIALTIES,INC., MACHINERY INVESTMENT CORPORATION, PANOPLY REINSURANCE COMPANY LIMITED, SOONER SCALES,INC.
Assigned to FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE reassignment FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CIMOIL CORPORATION, CMI CORPORATION, CMI INTERNATIONAL CORPORATION, GRAMCO SPECIALITIES, INC., MACHINERY INVESTMENT CORPORATION, PANOPLY REINSURANACE COMPANY, LTD.
Assigned to NORTHERN TRUST COMPANY, THE, FIRST NATIONAL BANK OF CHICAGO, CONTINENTAL ILLINOIS NATIONAL BANK AND TRUST COMPANY OF CHICAGO, MERCANTILE NATIONAL BANK AT DALLAS, FIDELITY BANK N.A., REPUBLICBANK DALLAS, N.A., BANK OF PENNSYLVANIA, FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE, MANUFACTURERS HANOVER TRUST COMPANY, COMMERCIAL BANK, N.A., BANK OF AMERICA NATIONAL TRUST AND SAVINGS ASSOCIATION, COMMERCE BANK reassignment NORTHERN TRUST COMPANY, THE Assignors: CMI CORPORATION, CMI ENERGY CONVERSION SYSTEMS, INC., CMI INTERNATIONAL CORPORATION, CMIOIL CORPORATION, GRAMCO SPECIALITIES, INC., MACHINERY INVESTMENT CORPORATION, PANOPLY REINSURANCE COMPANY, LTD., SOONER SCALES, INC.
Assigned to FIRST INTERSTATE BANK OF OKLAHOMA, N.A. reassignment FIRST INTERSTATE BANK OF OKLAHOMA, N.A. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CMI CORPORATION, A CORP. OF OK
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Assigned to CMI CORPORATION A CORP. OF OKLAHOMA reassignment CMI CORPORATION A CORP. OF OKLAHOMA RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BOATMEN'S FIRST NATIONAL BANK OF OKLAHOMA
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/76—Graders, bulldozers, or the like with scraper plates or ploughshare-like elements; Levelling scarifying devices
    • E02F3/78—Graders, bulldozers, or the like with scraper plates or ploughshare-like elements; Levelling scarifying devices with rotating digging elements
    • E02F3/783—Graders, bulldozers, or the like with scraper plates or ploughshare-like elements; Levelling scarifying devices with rotating digging elements having a horizontal axis of rotation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D53/00—Tractor-trailer combinations; Road trains
    • B62D53/02—Tractor-trailer combinations; Road trains comprising a uniaxle tractor unit and a uniaxle trailer unit
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/76—Graders, bulldozers, or the like with scraper plates or ploughshare-like elements; Levelling scarifying devices
    • E02F3/7636—Graders with the scraper blade mounted under the tractor chassis
    • E02F3/764—Graders with the scraper blade mounted under the tractor chassis with the scraper blade being pivotable about a vertical axis
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/0841—Articulated frame, i.e. having at least one pivot point between two travelling gear units
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/16—Cabins, platforms, or the like, for drivers
    • E02F9/166—Cabins, platforms, or the like, for drivers movable, tiltable or pivoting, e.g. movable seats, dampening arrangements of cabins

Definitions

  • the present invention contemplates ,a doublearticulated motor-grader assembly which carries a compound earth-working implement-which is adjustably controlled to carry out cutting, trimming and spreading'opcrations as a unitary operation.
  • the invention consists of motorfgrader structure including mobile ground support elements and an adjustable central frame which carries a further adjustable subframe in controllable position with relation to a selected ground plane.
  • the subframe assembly then carries an earth-working implement consisting of a rotary cutter element and a moldboard or scraper element arranged generally parallel thereto, both elemerits operating in co-action to function in contact at the selected earth plane.
  • FIG. 1 is a side elevation of a motor-grader assembly constructed in accordance with the invention
  • FIG. 2 is a top plan view of the motor-grader assembly as shown in FIG. I;
  • FIG. 3 is an enlarged elevation with parts shown in cutaway of a mobile assembly as constructed in accordance with the invention
  • FIG. 4 is an enlarged top plan view of a mobile assembly of the invention with parts shown in cutaway;
  • FIG. 5 is a section taken along linesS-S of FIG. 1;
  • FIG. 6 is an enlarged section as taken along lines 6-6 of FIG. 5;
  • FIG. 7 is an enlarged side elevation of the main frame of the invention with parts shown in cutaway;
  • FIG. 8 is a front elevation of one form of anger assembly as utilized in the invention.
  • FIG. 9 is a front elevation of a portion of an alternative form of auger assembly, a cutter-auger element, as utilized in the present invention.
  • FIG. 10 is a schematic diagram of the main frame tilt control assembly
  • FIG. 11 is a schematic diagram of the subframe cros slope control assembly
  • FIG. 12 is a schematic diagram of the steering control assembly constructed in accordance with the invention.
  • FIG.'13 is a schematic diagram of additional structure of the steering control assembly
  • FIG. 14 is a schematic diagram of the main frame tilt
  • FIG. 15 is a top plan view of the motor-grader assembly including control sensor support assembly.
  • FIG. 16 is a block diagram of control systems interconnections.
  • a motor-grader assembly 10 consists of an A END mobile assembly 12 and an oppositely oriented B END mobile assembly 14 with a frame assembly 16 pivotally supported therebetween.
  • the A END and B END mobile assemblies 12 and 14 respectively may be identical units supported on tandem wheel assemblies 18a. and 18b bearing on rubber tired wheels 20a and 2017, respectively.
  • motorgrader assembly 10 is shown as being supported on pluralities of tandem arrayed rubber-tired wheels 20a and 20b, it should be understood that various other forms of ground supporting mobile means such as traction units, single or plural wheel assemblies, etc., may be employed in the mobile ground supporting function.
  • Each of mobile assemblies 12 and 14 further consists of a chassis 22a and 22b supported atop tandem wheel assemblies 18a and 18b at a central point (to be further described below) and a suitable power source or engine 24a and 24b is supported thereon.
  • Prototype motorgrader units are presently designed to include 225 horsepower diesel engines of a type which is commercially available from the Caterpillar Tractor Co. of Peoria, Ill.
  • the engines 24a and 24b function with hydraulic pumps and motors which are utilized for various power purposes about motor-grader assembly as will be further described below.
  • Hood cowls 26a and 26b are affixed over respective engines 24a and 24b in secure manner relative to chassis 22a and 22b while conventional bumper structure 28a and 28b, exhaust stack 30a and 30b, and air cleaners 32a and 32b are suitably adapted.
  • the main frame assembly 16 is pivotally supported on the A END mobile assembly 12 about a point indicated by vertical axis designation 34, and it is supported at its other end by the B END mobile assembly 14 about a vertical axis designation 36.
  • the main frame assembly 16 consists of a central frame 38 having each end extending into a downward extremity thereof.
  • Central frame 38 has a mounting plate 48 securely affixed as by welding across its upper, horizontal surface and a pair of bearing shafts 50 and 52 are secured therethrough in parallel, transverse disposition to form a plurality of quadrature arrayed support shafts 54,56,58, and 60.
  • Support shafts 54 and extend outward in parallel, spaced and horizontal disposition from one side of central frame 38 while support shafts 56 and 58 extend in respective opposite dispositions on the other side of central frame 38.
  • the end 40 of central frame 38 includes a pair of beams 62 and 64 (see FIG. 2) and the other end 42 is similarly formed by a pair of tapering beams 66 and 68.
  • the support shafts 54,56,58, and 60 provide support connection for the central frame 38 as they are each pivotally affixed to respective arm ends 70,72,74 and 76 for movement about a transverse axis.
  • the arm ends 70 and 72 form part of a bifurcated frame 78 while the arms 74 and 76 form part of an oppositely disposed bifurcated frame 80.
  • Each of bifurcated ends 70,72,74 and 76 receives a semi-circular bearing bracket 82,84,86 and 88 in secure affixure for the purpose of movably seizing each of the respective support shafts 54,56,58 and 60.
  • the opposite or outer ends of the respective bifurcated frames 78 and 80 are each mounted to respective mobile assemblies 14 and 12 for pivotal afflxure about vertical axes 36 and 34.
  • the hydraulic cylinder is connected within bifurcated frame 78 to extend a piston arm 92 into pivotal connection with pivot eye 46 of central frame end 42.
  • the hydraulic cylinder 94 is affixed upwardly within bifurcated frame 80 to extend a piston rod end 96 downward into pivotal connection with pivot eye 44. Actuation of hydraulic cylinders 90 or 94 enable movement of the central frame 38 relative to each of the bifurcated frames 78 and 80 which motion must necessarily extend through to effect counterbalance at respective tandem assemblies 18b and 18a.
  • the mounting plate 48 of central frame 38 actually provides a smooth plate about which operating cab 100 is supported.
  • the operating cab 100 consisting of operators space 102 and having windshield area 104 is supported on one end of a support arm 106 which, in turn, has it other end pivotally affixed on mounting plate 48 for movement about a vertical axis 108.
  • the support arm 106 includes drive and braking mechanism, as will be further described below, which operates in conjunction with mounting plate 48 to position the operators cab 100 in any desired position relative to main frame 16.
  • a subframe 110 exemplarily shown as being octagonal in construction, is supported beneath main frame 16 in laterally pivotal manner.
  • subframe 110 is pivotally affixed at a first pivot assembly 12 which is rigidly secured beneath a cross member 114 extending between frame arms 62 and 64.
  • first pivot assembly 12 which is rigidly secured beneath a cross member 114 extending between frame arms 62 and 64.
  • pivot assembly 116 which is secured beneath a cross member (not shown), secured as by welding between the opposite bifurcated frame arms 66 and 68.
  • Pivotal or attitude control of subframe 110 relative to main frame 16 is exercised by control of a pair of hydraulic cylinders 1 18 and 120, each of which is pivotally affixed to opposite sides of central frame 38 to extend respective pistons 122 and 124 into a suitable pivotal connection at the opposite sides of the subframe 110.
  • a pair of sensor support arms 119 and 121 extending respective telescoping rods 123 and 125 are securely affixed across opposite sides of subframe 110 to extend transversely relative to motor-grader assembly 10.
  • the subframe 110 provides further movable support of a rotatable ring member 126 which supports a working implement, an auger-moldboard assembly 128, therebeneath.
  • Ring member 126 is supported for circular movement within a plurality of support blocks 130 beneath subframe 110, and suitable drive means (as will be further described) are mounted on subframel10 to provide circular rotation of ring member 126.
  • the working element, auger-moldboard assembly 128, is secured beneath ring member 126 to rotate therewith.
  • auger-moldboard assembly 128 may consist of an auger element 132a and a blade element 132]: each supported by a respective connecting frame 134a and 134b adjustably connected beneath the ring member 126.
  • Each of auger and blade elements 132a and 132k are separately movable as to angle of attack by means of respective hydraulic cylinders 136a and 136b, such structure to be further described in greater detail.
  • FIG. 3, 4 and 5 depict elements of the B END mobile assembly 14 in greater detail.
  • the tandem assembly 18b is actually a commercially available mechanical unit which enables four wheel drive of tandem arranged wheels, e.g. a separate type final drive utilizing a tandem axle.
  • Casings 140 and 142 of tandem assembly 18b each include a separate sprocket and chain drive for each of the respective front and rear wheels 20b.
  • the tandem assemblies include a transverse axle 144, and a pair of oppositely disposed clamping brackets 145 are welded beneath chassis 22b to provide secure engagement for support upon transverse axle 144.
  • the tandem axle 144 receives drive rotation from a straight-through gear drive assembly 146 which is connected to receive rotational input through a coupling 148.
  • the rotational input coupling 148 is taken from the output of a suitable hydraulic motor 150, e.g. a Series 27 Sundstrand hydraulic motor as driven from a suitable hydraulic pump 152, e.g. a Series 25 Sundstrand hydraulic pump. While specific hydraulic pump and motor equipment is identified, it should be understood that a great many combinations of differing power and type might be utilized to provide the drive power.
  • Hydraulic pressure generated in hydraulic pump 152 is also utilized in conventional manner to drive various of the hydraulic control element disposed about the motor-grader assembly 10, as will be further described.
  • the hydraulic pump 152 is energized from diesel engine 24b as rotational engine output applied to a parallel array of flywheels 154 is transmitted on a plurality of V-belts 156 to a plural belt pulley 158 which, in turn, applies rotational input to hydraulic pump 152.
  • Hydraulic pump 152 working in concert with conventional reservoir means (not shown) provides pressure output from a coupling 160 for conduction to an input coupling 162 for energization of the hydraulic motor 150.
  • An additional plurality of flywheel pulleys 164 may be used to provide an additional rotational output from engine 2% for connection to other auxiliary pump means (not shown) which might be employed for powering auxiliary implement control mechanisms and such, as will be further described below. 7
  • a vertical pivot shaft 166 is rigidly secured through a floor plate 168 of chassis 22b (see also FIG. 6), and into rigid connection on top of gear box 146 such that is extends vertically from the center of tandem assembly 18b, i.e. straight-up from the intersection of drive axle 144 through gear drive 146.
  • Pivot shaft 166 is inserted upward through a pivot bearing 170 which is formed to have oppositely disposed yoke arms 172 and 174 extending outward for steering connection as will be described.
  • the pivot bearing 170 is also formed to have two oppositely disposed connecting tabs 176 and 178 (FIG. 5) and these serve to provide a connection for tilt control hydraulics as will be described below.
  • the pivot bearing 170 is mounted on pivot shaft 166 by means of a timken bearing 180 (FIG. 6) of conventional type interposed concentrically therebetween to provide necessary ease of the relative movement.
  • the pivot bearing 170 is formed to have a flange 182 about its upper end, and a frame support bearing 184 having a bottom flange 186 is securely affixed thereon, the placement of support bearing 184 also serving to position and retain the timken bearing 180.
  • the support bearing 184 provides a rotational support for the frame end 78.
  • a steel support rod 188 of suitable size and strangth is securely affixed as by welding through the front plate 190 of end frame 78, and suitable reinforcing such as lateral plate 192 is also provided.
  • suitable reinforcing such as lateral plate 192 is also provided.
  • Various heavy construction techniques may be utilized to assure a strong bond between rod 188 and fame end 78 since the outer end of rod 188 must support the entire end of the main frame 16 upon mobile assembly 14.
  • timken bearing 194 is interposed within the annular space between support rod 188 and the inner surface of support bearing 184 and a retaining plate 196 is secured over the end of support bearing 184 in such manner as to assure secure positioning of timken bearing 194.
  • Steering control is effected by means of hydraulic cylinders 198 and 200 which are connected at pivot ends 202 and 284 to a connecting frame 206 which is rigidly secured through transverse beam 288 to the chassis 22b.
  • Hydraulic pistons 218 and 212 are connected to respective yoke arms 172 and 174 of pivot bearing 178, and energization in concert of hydraulic cylinders 198 and 200 will provide rotation of yoke arms 172 and 174 (pivot bearing 178) relative to the pivot shaft 166 which is also secured to chassis 22b of mobile assembly 14.
  • Tilt control of main frame 16 is effected by control of hydraulic cylinders 214 and 216.
  • Hydraulic cylinders 214 and 216 are each pivotally mounted by means of respective pivot pins 218 and 220 which are affixed thereto and pivotally interconnected with bracket plates 222 and 224 which are secured through suitable spacers 226 on front plate 190 of the bifurcated frame end 78.
  • Hydraulic cylinders 214 and 216 extend respective pistons 228 and 230 downward into pivotal connection with connecting tabs 176 and 178 as disposed on opposite sides of pivot bearing 170. Coordinated control of hydraulic cylinders 214 and 216 effects tilting of frame end 78 and, therefore, main frame 16 about the longitudinal axis established by the bearing of support rod 188 within support bearing 184.
  • Frame locking is provided by a hydraulic cylinder 1 232 which may be selectively actuated to extend its piston rod (not specifically shown) into a locking hole which is formed within a locking block 234.
  • Looking block 234 consists merely of a block of steel with a hole therethrough and which is secured at a front center point of forward plate 190 of end frame 78.
  • Hydraulic cylinder 232 is then supported in longitudinal relationship by a mounting plate 236 suspended by a pair of support plates 238 each rigidly secured above the support bearing 184. The operator can effect control of cylinder 232 to extend the piston into locking block 234, this serving to maintain continuous positioning of the hydraulic locking cylinder 232 in vertical alignment, said vertical alignment assuring lateral horizontal positioning of frame end 78.
  • the main frame 16 is provided with unique adjustability through pivotal connection of end frames 78 and to the central frame 38.
  • the subframe is secured from pivot assemblies 112 and 116 from opposite ends of central frame 38. That is, a bearing sleeve 240 secured from a sleeve hanger 242 as rigidly affixed beneath transverse member 114 (FIG. 2), a part of the main frame 38, is secured about the bearing pin 244 as supported by plates 246 and 248.
  • Pivot assembly 116 at the opposite end is similarly constructed and supported from the opposite end of main frame 38 with a hanger 250 supporting a bearing sleeve 252 for pivotal support about a bearing pin 254 as secured between vertical plates 256 and 258.
  • a plurality of adjustable ring support blocks are disposed at approximately equal distances about the underside of subframe 118 to support the ring member 126 moveably therearound.
  • Each of support blocks 130 is individually adjustable for initial setting of level and centering of the ring 126.
  • a ring drive hydraulic motor 260 is suitably mounted to work into a worm gear 262 which transmits rotational force to a 126.
  • each of the implement extending panels 134a and 13411 which serve to pivotally support adjusting plates 272a and 272b about pivotal connections 274a and 274b.
  • the blade element 132b is secured by a suitable form of rigid connection 276b to said adjusting plate 272b for movement therewith.
  • Hydraulic cylinder 136b pivotally connected to ring member 126, extends a piston 278b into pivotal connection with a lever mechanism 280b which exerts positioning control on the blade element 132b.
  • the bydraulic adjusting cylinder 136b, as well as adjusting plate 272b, connecting mechanism 276b and other related components are duplicated on each side of the ring member 126, ie as associated with each of opposite-side implement support panels 270.
  • the auger element 1320 is secured in like manner by means of a suitable form of connection 276a as secured to a transverse frame member 271 and adjusting plate 272a for movement therewith.
  • the hydraulic cylinders 136a (one on each side of ring member 126) extend respective pistons 278a into pivotal connection with lever mechanisms 280a for positioning control.
  • the auger element 132a may consist of an elongated cylinder 282 having a vane 284 arranged therearound in helical flight, the vane 284 being secured as by welding in helical configuration.
  • the ends of cylinder 284 are then connected via shafts 286 and 288 for rotational retention within oppositelydisposed support assemblies 290 and 292 which extend from transverse frame member 271.
  • a hydraulic motor 294 of well-known type is affixed to the outer portion of support member 292 to impart rotational drive to shaft 288. If desired, additional hydraulic drive can be imparted from a hydraulic motor 296 providing input to the opposite shaft 286.
  • the hydraulic motors may be selected of desired rating from any of various commercially available types.
  • auger element 132a may be broken in the middle, each half being separately, rotationally supported by suitable framing at the mid-point, so that each of the two sides may be independently-driven at the same or different rotational speeds.
  • FIG. 9 illustrates an alternativeform of auger element 298 of the cutter-auger type which includes a first helical flight of cutter bars 300 each carrying a cutter head 302 and a second helically arranged vane flight 304 wound in intersticed relationship.
  • the cutter-auger 298 enables a rotary cutting action which has greater trimming and clearing capabilities, and which is especially attractive for use upon encountering certain difficult or highly compacted forms of earth material.
  • the cutter-auger 298 may be disposed for use with hydraulically drive and support elements similar to those as shown in FIG.8.
  • a frame level control 312 provides setting of the elevation and level of main frame assembly 16. Such height control is effected by adjustment of the hydraulic cylinders and/or 94 (see also FIG. 1).
  • a pair of hydraulic connections 318 and 320 are connected to hydraulic cylinder 94 and to a four-way valve 322.
  • the hydraulic valve 322 is a commercially available four-way type which has a quiescent or lock central portion 324 as well as oppositely porting spool sections 326 and 328.
  • the valve 322 is then controlled by energization of one or the other of the end-mounted solenoids 330 and 332 which provide the proper flow of hydraulic fluid to the hydraulic cylinder 324.
  • Hydraulic connections 334 and 336 are shown connected to a sump which may be any suitable form of hydraulic pump and reservoir system compatible with the available power requirements and drive input energy.
  • Manual lever switch 316 provides A END control by energization of electrical leads 338 and 340 to actuate one or the other of solenoids 330 and 332.
  • manual lever 318 provides B END actuation by energization of respective ones of electrical connections 342 and 344 to actuate solenoids 346 and 348.
  • These solenoids 348 and 346 provide opposite actuation of a fourway hydraulic valve 350 which has a central lock up section 352 as well as oppositely flowing port sections 354 and 356.
  • l-Iydraulic lines 358 and 360 connect between hydraulic cylinder 90 and four-way valve 350, with hydraulic lines 362 and 364 leading to a suitable hydraulic pressure sump.
  • FIG. 11 illustrates a control system 366 which controls the cross slope of the subframe l 10 and whatever the working implement suspended therebeneath.
  • the subframe has its cross slope adjusted in accordance with the actuation of hydraulic cylinders 118 and 120 which are oppositely connected in parallel to hydraulic lines 368 and 370 from a four-way valve 372 thereby to effect reciprocal cylinder action.
  • Four-way valve 372 is connected to source hydraulic lines 374 and 376, and valve 372 consists of a lock up section 378 as well as opposite porting sections 380 and 382 which are positioned by oppositely actuating solenoids 384 and 386, respectively.
  • Solenoids 384 and 386 are controlled via electrical connections 388 and 390 from a suitable cross slope selector 392 which in turn, receives input from a manual cross slope control 394 and an automatic cross slope control 396.
  • the manual cross slope control 394 may be located in the operating cab 100, while the automatic cross slope control 396 refers to control energization originating from suitable control sensors which are responsive to an external reference, as will be further described below.
  • the automatic cross slope control 396 may be such as a gravity responsive switch with suitable output which is adjustable in relation to a pendulum or such.
  • an automatic-manual steering system 400 includes A END steering assembly 402 and a B END steering assembly 404.
  • Manual steering is carried out by means of a steering control unit 406, the subject matter of FIG. 1 1 as will be further described, with steering end selection being made through a manual steering end selector switch 408.
  • Automatic steering in response to sensing of an external reference is carried out in response to an A END steering control 410 or a B END steering control 412 as se lected by a steering selector 414 for input via leads 416 and 418 to each of an A END four-way valve 418 and a B END four-way valve 420.
  • Manual steering is carried out by steering control unit 406 which is controlled to steer one end or the other in response to actuation of manual steering end selector 408.
  • hydraulic fluid output in one direction or the other is present on hydraulic lines 422 and 424 to a double-ended hydraulic cylinder 426.
  • the hydraulic cylinder 426 has one end 428 pivotally connected to a valve spool 430 of a heavy duty hydraulic valve 432, e.g. a thirty gallon four-way valve.
  • the hydraulic valve 432 is energized by hydraulic pressure present on hydraulic lines 434 and 436 from a suitable sump, and valve output is directed through hydraulic lines 438 and 440 which are applied in opposite, parallel connection through respective steering cylinders 198a and 200a.
  • applications of pressure differential as between hydraulic lines 438 and 440, results in reciprocal action ofhydraulic cylinder pistons 212a and 2100 to effect pivoting of the steering yoke 172a-l74a which is in rigid affixure to the main frame 16.
  • Steering of the B END steering assembly 404 is effected by application of a hydraulic fluid differential between hydraulic lines 442 and 444 to a double-ended hydraulic cylinder 446.
  • the hydraulic cylinder 446 drives a reciprocal valve spool 448 of a heavy duty hydraulicvalve 450 in the same manner as described for the A END assembly. That is, hydraulic source input is via lines 452 and 454 with regulating fluid output along hydraulic lines 456 and 458 to each of the hydraulic steering cylinders 460 and 462.
  • the fluid input to hydraulic cylinders 460 and 462 is in parallel but opposite orientation to effect reciprocal movement of respective piston rods 210 and 212 thereby to effect steering movement.
  • Automatic steering would originate as an electrical control signal in the form of a switch closure via leads 416 through 419 to energize predetermined valve solenoids.
  • an energizing voltage on lead 416 to valve solenoid 418 changes four-way valve 418 from its center or lockup position 470 to spool position 472 which directs hydraulic fluid from pressure source lines 474 and 476 through respective hydraulic lines 438 and 440 to cause reciprocal energization of hydraulic cylinders 198a and 200a.
  • Energization via lead 417 energizes solenoid valve 478 such that valve spool section 480 effects an opposite hydraulic pressure differential as between. hydraulic lines 438 and 440.
  • Actuation of solenoid valve 482 moves the valve spool from its lockup position 486 to the position where spool section 488 directs hydraulic fluid flow from source lines 490 and 492 through respective supply lines 456 and 458.
  • Alternate energization of the valve solenoid 484 places spool section 494 in operation to reverse the pressure differential as between hydraulic lines 456 and 458, this effecting an opposite reciprocal effect as between the steering cylinders 460 and462.
  • the steering control unit 406 is shown in greater detail in FIG. 13 which includes various valve interconnections for responding to the manually operated steering wheel 500.
  • Steering wheel 500 is connected by means of a suitable mechanical linkage 502 to operate an orbitrol mechanism 504.
  • the orbitrol 504 is a wellknown type of hydraulic proportioning pump which varies the direction and force of hydraulic flow as between pressure lines 506 and 508.
  • the lines 506 and 508 are connected to supply fluid pressure input to respective four-way hydraulic valves 510 and 512 with pressure return proceeding via hydraulic lines 514 and 516 to a fluid reservoir 518.
  • Pressure relief is afforded by a common fluid connection 520 through oppositely oriented check valves 522 and 524 with return to the respective input pressure lines 506 and 508.
  • a main frame tilt control assembly 550 exercises selected control of lateral tilting of the A END or the B END or both ends simultaneously of the main frame relative to the respective A END and B END mobile assemblies 12 and 14.
  • the B END is in the unlocked position as B END unlock control 552 provides energizing voltage via lead 554 to energize valve solenoid 556 such that a four-way valve 558 is actuated to energize hydraulic locking cylinder 232 such that its locking piston 560 is withdrawn out of engagement with locking block 354.
  • the A END unlock 562 will be de-energized such that valve solenoid 564 does not actuate a four-way valve 566.
  • the valve 566 actuates locking cylinder 3630 such that a locking pin 560a is forced into locking engagement within locking block 234a.
  • a B END tilt control 568 may then be controlled by energization along either of electrical ends 570 or 572 to effect frame tilting relative to the B END mobile assembly.
  • Energization of lead 570 energizes valve solenoid 574 such that a fourway valve 576 is actuated from its lockup spool section 578 to a spool section 58010 place a pressure differential between hydraulic lines 582 and 584.
  • a END tilt control 590 may be selectively actuated to energize one or the other of leads 592 or 594 to energize respective solenoids 596 or 598.
  • a hydraulic valve 600 is normally positioned with the lockup spool section 602 in circuit with pressure lines 604 and 606 and the hydraulic circuit lines 608 and 610. Pressure lines 608 and 610 are then connected in parallel to each of the hydraulic tilt cylinders 216a and 214a to effect reciprocal piston action upon energization of either of relays 596 or 598. Energization of relay 596 brings valve spool section 612 into function, while energization of relay 598 will bring the opposite valve spool section 614 to cause reverse pressure application.
  • a hydraulic override function is provided at each frame end through operation of check valves 616, 618, 620 and 622.
  • valve spool section 558 applies pressure via hydraulic line 624 to open each of the respective check valves 616 and 618 such that they will then allow hydraulic pressure application as present on either of hydraulic lines 582 and 584 to the tilt control cylinders 214 and 216.
  • check valves 620 and 622 are open with application of pressure on hydraulic line 626 (opposite from that shown) to allow hydraulic actuation of tilt cylinders 214a and 216a.
  • a motor-grader assembly carries a suitable tracer bar 630 suspended in outrigged position as carried by support arms 119 and 121 and respective telescoping rods 123 and 125.
  • Support arms 119 and 121 are each welded to opposite segments of subframe 110 to extend laterally outboard, while telescoping rods 123 and 125 are adjustably held within support frames 119 and 121.
  • Telescoping rods 123 and 126 may be extended outward to any length as desired.
  • a pair of pivotal brackets 632 and 634 serve to secure the sensor rods 630 on the ends of respective telescoping rods 123 and 125.
  • the brackets 632 and 634 should be a suitable pivot assembly since it will quite often be required that telescoping rods 123 and 125 extend outward different distances. Such will be the case when motor-grader assembly 10 is operated along an external reference or string line 636 with main frame 16 canted relative to the A END and B END mobile assemblies 12 and 14. It should also be understood that telescoping rods can be readily fitted to extend outboard in the other direction, from the opposite ends of support arms 119 and 120, as exigencies demand.
  • a bracket 638 and support 640 aid in the automatic steering function by carrying a control sensor box 642 having a sensor rod 644 which is guided relative to string line 636.
  • Automatic steering function at the opposite end is carried out by bracket 646, support arm 648, control box 650 and sensor rod 652.
  • the length- ,wise placement of control sensor boxes 642 and 650 may also-be carried for differing applications.
  • sensor boxes 642 and 650 may be aligned with the leading and trailing edges of the furthest displaced (lengthwise) wheels of respective mobile assemblies 12 and 14 as is shown in FIG. 15.
  • Bracket 654 supports a control sensor box 656 and a counter-weighted sensing rod 658 which travels along string line 636.
  • bracket 656 carries a control sensor box 662 having a weighted sensor rod 664.
  • the control sensor boxes 642, 650, 658 and 662 may all be a similar type such as is disclosed in a U.S. Pat. No. 3,514,630 entitled Line Tracer Control Device and issued in the name of Steele et al.
  • Such control sensor box provides an electrical output in response to sensing variations relative to string line 636, such electrical signals being conducted back to appropriate control assemblies on the structure of motor-grader assembly 12.
  • FIG. 16 illustrates the interconnection of the various sensing and control components.
  • output from A END steering sensor 650 is applied to steering selector 414 which may be a main panel control located in the operating cab 100.
  • a END steering output from line 670 is applied via line 672 to cause proper function of hydraulic valve 418 such that steering cylinders 198a and 200a are driven to effect a steering correction of the A END mobile assembly 12.
  • output from B END steering sensor 642 is conducted via lines 674 through steering selector 414 to a control lead 676 which actuates hydraulic valve 420 to effect steering actuation of the B END steering cylinder 198 and 200.
  • Manual steering control from manual control unit 406 is an override control controlling selected ones of hydraulic valves 432 and/or 450 as shown more clearly in FIGS. 12 and 13.
  • Automatic elevation sensing takes place in similar manner in response to sensor control boxes,i.e. A END elevation sensor 662 and B END elevation sensor 658.
  • the respective outputs are applied via leads 678 and 680 for circuit selection in selector 329.
  • Selected outputs via control leads 682 and 684 are applied to respective hydraulic valves 322 and/or 350 to effect variation of height control cylinders 94 and 90.
  • cross slope control be carried out automatically by a suitable form of transversely oriented sensor which provides zero or no output indication relative to a preset elevation value.
  • a suitable transverse level sensing mechanism may provide a control output for use in either the cross slope circuitry (FIG. 11) or the main frame tilt control circuitry and hydraulics (FIG. 14) or both. Such control output could be applied to effect automatic following of support structure which holds auger 132a and moldboard 1321: at proper cutting angle.
  • the motor-grader assembly 10 is capable of operation in either longitudinal direction under control of either an operator or an associated external reference such as a string line.
  • FIGS. 15 and 16 illustrate the manner whereby automatic elevation and steering sensing are carried out with reference to string line 636.
  • the sensor positions are adjacent opposite longitudinal extremities of the motor-grader assembly 10 and in parallel disposition to main frame 16. It should be understood however that sensor rod 630 can be aligned at any angular relationship relative to main frame 16, depending upon the angle of attach of the motor-grader assembly in performing its earth-working undertaking.
  • automatic steering is carried out in response to A END steering control 410 and B END steering control 412 operating through steering selector 414. That is, more particularly, electrical outputs from A END steering sensor 650 and B END steering sensor 642 (FIG. 16) as applied for selective actuation of hydraulic valves 418 and 420.
  • a sensed electrical output from A END automatic steering control 410 is conducted via one or the other leads 416 and 417, depending upon the direction of turning, to activate the associated valve solenoid 468 or 478 such that hydraulic valve 418 provides the requisite pressure direction through steering cylinders 198a and 200a.
  • steering wheel 500 is manipulated to vary the orbitrol pump 504 to operate the proper one of A END or B END hydraulic valves 510 or 512.
  • the valves 510 and 512 serve to energize respective drive cylinders 426 and 446 to position the hydraulic valve spools within respective hydraulic cylinders 432 and 450 (FIG. 12).
  • Valves 432 and 450 are heavy duty hydraulicvalves which allow manual steering as an override function with continual correction being applied from an automatic steeringsource which may actuate then conducted via leads 682 and 684 to energize one or both of hydraulic valves 322 and 350 to activate their respective height control cylinders 94 and 90 located at each end of the main frame 16. Selector 329 also allows use of manual adjustment control 314 which provides parallel control of hydraulic valves 322 and 351).
  • the auger-moldboard assembly 128 is maintained in proper working attitude to a selected earth plane through control of the ring member 126.
  • control of central frame 38 by actuation of hydraulic cylinders 90 and 94, allows setting at any selected longitudinal angle; and hydraulic cylinders 118 and 120 are controlled to set the transverse angle of the ring member 126 with respect to the central frame 38 and, therefore, at desired angle to the earths surface therebeneath.
  • cross slope sensing to provide continual automatic-control of the transverse attitude of the auger-moldboard assembly 128.
  • a double-ended motorgrader assembly has the additional advantage of being reversible in operation such that various turning around maneuvers are eliminated, and this serves to cut down greatly on job time.
  • the control systems disclosed herein offer particular advantages in steering and elevation control of such double-ended machines, elevation control being effected such that an entire midframe assembly is variable both as to elevation and level relative to the earth or other selected references, and automatic-manual steering can be effected even from an offset or canted midframe position, as may be required in particular earth-working situations.
  • the further combination of the rotary cutter and moldboard work implements, functioning in coaction enable operational advantages heretofore unrealizable in motor-grader apparatus or, for that matter, any single type of mobile machine of relatively general earthworking application.
  • first and second mobile means each including drive power source and mobile structure
  • central frame means of generally elongated form having each of first and second ends pivotally affixed to respective first and second mobile means for support therebetween;
  • subframe means secured to and pivotally supported from said central frame means
  • ring member means rotatably affixed beneath said subframe means for circular rotation thereof;
  • rotatable auger means rotatably and pivotally affixed beneath said ring members for circular rotation therewith;
  • moldboard means disposed generally parallel to said auger means and pivotally affixed beneath said ring member means for circular rotation therewith; first and second control means for adjusting the position of each of said augermeans and mold-board means relative to said ring member means; and means accomodating an operator rotatably affixed on top of said central frame means for selected positioning thereon to gain optimum surveillance.
  • first and second hydraulic cylinder means each pivotally connected between said ring member and the respective auger means and moldboard means.
  • Earth-working apparatus as set forth in claim 1 which is further characterized to include:
  • At least a portion of said central frame means is adjustable as to the longitudinal angle
  • At least a portion of said central frame means is adjustable as to longitudinal angle
  • central shaft means of generally elongated form
  • vane means arranged in a continual helical flight making a plurality of revolutions around said shaft means along the length thereof.
  • Mobile earth-working apparatus comprising:
  • subframe means pivotally supported from the frame means
  • ring member means rotatably affixed beneath the subframe means for circular rotation thereof;
  • rotatable auger means rotatably affixed beneath the ring member means for circular rotation therewith;
  • moldboard means disposed generally parallel to the auger means and affixed beneath the ring member means for circular rotation therewith;
  • An apparatus as set forth in claim 10 which is further characterized to include:

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Abstract

Apparatus for earth-working which consists of motor-grader mobile apparatus of the type which carries a subframe element in adjustable planar relationship with respect to the earth, said subframe providing adjustable support for a cutting and trimming implement which includes a first earth-cutting and moving implement in coactive combination with a moldboard for adjustable positioning and contact in a pre-set plane of said earth''s surface.

Description

United States Patent [191 Swisher, Jr. et a1. May 29, 1973 541 MOTOR-GRADER IMPLEMENTS 3,610,341 10/1971 Swisher et a1. .,172 4.5 3,423,859 1/1969 Swisher et al. ..37/l08 [75] f f P" Dmlw 2,068,433 1/1937 Peterson 172/7s5x 5mm, SPWeY, all 0 3,490,539 1/1970 Hilmesetal.... ..37/10s x 1 Oklahoma Y Okla- 3,568,778 3 1971 Swisher etaL. ..172/785 1 2,379,469 7/1945 Bagan 172/119 X 3 Asslsnw 8 Oklamma 3,091,373 6/1963 West ..172 119x k 3,136,078 6/1964 Renault 172/7s4x 22 Filed: Oct 19 1970 3,503,450 3/1970 Day ..172/119 X [21] PP 1 3 Primary Examiner-Robert E. Pulfrey Assistant Examiner-R. T. Rader Related Apphcat'on Data Attorney-Dunlap, Laney, Hessin & Daugherty [63] Continuation-impart of Ser. No. 793,274, Jan. 23,
l 1969, Pat. No. 3,568,778. [57] ABSTRACT 52] U 8 Cl 172/785 172/71 172/119 Apparatus for earth-working which consists of motor- [511 1:302 3/12 grader mobile apparatus of the type which carries a [58] Fi d 781 3 subframe element in adjustable planar relationship 1727785 z' 'g ia {22 with respect to the earth, said subframe providing ad- 3 6 5 9 justable support for a cutting and trimming implement which includes a first earth-cutting and moving imple- 56 R f d ment in coactive combination with a moldboard for. 1 e e adjustable positioning and contact in a pre-set plane of UNITED STATES PATENTS Said earths Surface- 2,494,324 1/1950 Wright I. ..172/793 11 Claims, 16 Drawing Figures SHEET 6 OF 9 PATENTEU HAY 2 91975 MOTOR-GRADER IMPLEMENTS CROSS-REFERENCE TO CO-PENDING APPLICATIONS The subject matter of the present invention constitutes a continuation-impart of U.S. Patent application Ser No. 793,274 now U.S. Pat/No. 3,568,778 entitled Improvements in Motor-Grader Apparatus," as filed BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates generally to mobile earth- .working machinery and, more particularly, but not by way of limitation, it relates to improvements in earth-- working implements as adjustablycarried by motorgrader superstructure.
2. Description of the Prior Art The prior art includes various types-of grading machinery utilizing differing forms of articulation and drive systems. Most prior art teachings have been directed toward improvements relating to the classic type of motor-grader which consistsof such as a scraper blade carried on a movable ring assembly beneath mobile superstructure, which blade assembly serves in an earth-cutting and earth-displacing capacity, such blade being adjustable as to lateral angle, forward angle, pitch, etc. Some prior designs of grader machineryhave been directed to double articulated machinery similar in some respects to that which is fully disclosed in the above-cited co-pending patent applications, and
these are exemplified by a prior art U.S. patent to Wright, U.S. Pat. No. 2,494,324. This patent, as well as many other patents of related teaching adhere to the more classic form of grader machinery and merely employ the cutting and displacing blade for performing the standard grading operation.
SUMMARY OF THE .INVENTION The present invention contemplates ,a doublearticulated motor-grader assembly which carries a compound earth-working implement-which is adjustably controlled to carry out cutting, trimming and spreading'opcrations as a unitary operation. In a more limited aspect, the invention consists of motorfgrader structure including mobile ground support elements and an adjustable central frame which carries a further adjustable subframe in controllable position with relation to a selected ground plane. The subframe assembly then carries an earth-working implement consisting of a rotary cutter element and a moldboard or scraper element arranged generally parallel thereto, both elemerits operating in co-action to function in contact at the selected earth plane.
Therefore, it is an object of the present invention to provide amotor-grader assembly for performing more efficient cutting and earth-displacing operations along a longitudinal alignment axis.
It is also an object of the invention to provide motorgraderapparatus having increased power and traction capabilities which enable the use of the compound earth-working implements of increased size with appreciable precision and ease of handling.
It is still further an object of the present invention .to provide a motor-grader assembly carrying a rotary cutting element and moldboard element which can be controlled from a selected external reference source to perform automated profile grade-cutting.
Finally, it is an object of the present invention to provide an attachable earth-working implement for carriage by a motor-grader assembly, which implement is capable of carrying out plural, compound working earth-working functions in concert.
Other objects and advantages of the invention will be evident from the following detailed description when read in conjunction with the accompanying drawings which illustrate the invention.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevation of a motor-grader assembly constructed in accordance with the invention;
FIG. 2 is a top plan view of the motor-grader assembly as shown in FIG. I;
FIG. 3 is an enlarged elevation with parts shown in cutaway of a mobile assembly as constructed in accordance with the invention;
FIG. 4 is an enlarged top plan view of a mobile assembly of the invention with parts shown in cutaway;
FIG. 5 is a section taken along linesS-S of FIG. 1;
,FIG. 6 is an enlarged section as taken along lines 6-6 of FIG. 5;
FIG. 7 is an enlarged side elevation of the main frame of the invention with parts shown in cutaway;
FIG. 8 is a front elevation of one form of anger assembly as utilized in the invention;
FIG. 9 is a front elevation of a portion of an alternative form of auger assembly, a cutter-auger element, as utilized in the present invention;
FIG. 10 is a schematic diagram of the main frame tilt control assembly;
FIG. 11 is a schematic diagram of the subframe cros slope control assembly;
. FIG. 12 is a schematic diagram of the steering control assembly constructed in accordance with the invention;
FIG.'13 is a schematic diagram of additional structure of the steering control assembly;
FIG. 14 is a schematic diagram of the main frame tilt,
control assembly as constructed in accordance with the invention;
FIG. 15 is a top plan view of the motor-grader assembly including control sensor support assembly; and
FIG. 16 is a block diagram of control systems interconnections.
DETAILED DESCRIPTION OF THE INVENTION Referring to FIGS. 1 and 2, a motor-grader assembly 10, consists of an A END mobile assembly 12 and an oppositely oriented B END mobile assembly 14 with a frame assembly 16 pivotally supported therebetween. The A END and B END mobile assemblies 12 and 14 respectively, may be identical units supported on tandem wheel assemblies 18a. and 18b bearing on rubber tired wheels 20a and 2017, respectively. While motorgrader assembly 10 is shown as being supported on pluralities of tandem arrayed rubber- tired wheels 20a and 20b, it should be understood that various other forms of ground supporting mobile means such as traction units, single or plural wheel assemblies, etc., may be employed in the mobile ground supporting function.
Each of mobile assemblies 12 and 14 further consists of a chassis 22a and 22b supported atop tandem wheel assemblies 18a and 18b at a central point (to be further described below) and a suitable power source or engine 24a and 24b is supported thereon. Prototype motorgrader units are presently designed to include 225 horsepower diesel engines of a type which is commercially available from the Caterpillar Tractor Co. of Peoria, Ill. The engines 24a and 24b function with hydraulic pumps and motors which are utilized for various power purposes about motor-grader assembly as will be further described below. Hood cowls 26a and 26b are affixed over respective engines 24a and 24b in secure manner relative to chassis 22a and 22b while conventional bumper structure 28a and 28b, exhaust stack 30a and 30b, and air cleaners 32a and 32b are suitably adapted.
The main frame assembly 16 is pivotally supported on the A END mobile assembly 12 about a point indicated by vertical axis designation 34, and it is supported at its other end by the B END mobile assembly 14 about a vertical axis designation 36. The main frame assembly 16 consists of a central frame 38 having each end extending into a downward extremity thereof. Central frame 38 has a mounting plate 48 securely affixed as by welding across its upper, horizontal surface and a pair of bearing shafts 50 and 52 are secured therethrough in parallel, transverse disposition to form a plurality of quadrature arrayed support shafts 54,56,58, and 60. Support shafts 54 and extend outward in parallel, spaced and horizontal disposition from one side of central frame 38 while support shafts 56 and 58 extend in respective opposite dispositions on the other side of central frame 38.
The end 40 of central frame 38 includes a pair of beams 62 and 64 (see FIG. 2) and the other end 42 is similarly formed by a pair of tapering beams 66 and 68. The support shafts 54,56,58, and 60 provide support connection for the central frame 38 as they are each pivotally affixed to respective arm ends 70,72,74 and 76 for movement about a transverse axis. The arm ends 70 and 72 form part of a bifurcated frame 78 while the arms 74 and 76 form part of an oppositely disposed bifurcated frame 80. Each of bifurcated ends 70,72,74 and 76 receives a semi-circular bearing bracket 82,84,86 and 88 in secure affixure for the purpose of movably seizing each of the respective support shafts 54,56,58 and 60.
The opposite or outer ends of the respective bifurcated frames 78 and 80 are each mounted to respective mobile assemblies 14 and 12 for pivotal afflxure about vertical axes 36 and 34. The hydraulic cylinder is connected within bifurcated frame 78 to extend a piston arm 92 into pivotal connection with pivot eye 46 of central frame end 42. Similarly, the hydraulic cylinder 94 is affixed upwardly within bifurcated frame 80 to extend a piston rod end 96 downward into pivotal connection with pivot eye 44. Actuation of hydraulic cylinders 90 or 94 enable movement of the central frame 38 relative to each of the bifurcated frames 78 and 80 which motion must necessarily extend through to effect counterbalance at respective tandem assemblies 18b and 18a.
The mounting plate 48 of central frame 38 actually provides a smooth plate about which operating cab 100 is supported. The operating cab 100 consisting of operators space 102 and having windshield area 104 is supported on one end of a support arm 106 which, in turn, has it other end pivotally affixed on mounting plate 48 for movement about a vertical axis 108. The support arm 106 includes drive and braking mechanism, as will be further described below, which operates in conjunction with mounting plate 48 to position the operators cab 100 in any desired position relative to main frame 16.
A subframe 110, exemplarily shown as being octagonal in construction, is supported beneath main frame 16 in laterally pivotal manner. Thus, subframe 110 is pivotally affixed at a first pivot assembly 12 which is rigidly secured beneath a cross member 114 extending between frame arms 62 and 64. Similarly, the opposite end of subframe 110 is pivotally affixed to a pivot assembly 116 which is secured beneath a cross member (not shown), secured as by welding between the opposite bifurcated frame arms 66 and 68. Pivotal or attitude control of subframe 110 relative to main frame 16 is exercised by control of a pair of hydraulic cylinders 1 18 and 120, each of which is pivotally affixed to opposite sides of central frame 38 to extend respective pistons 122 and 124 into a suitable pivotal connection at the opposite sides of the subframe 110. A pair of sensor support arms 119 and 121 extending respective telescoping rods 123 and 125 are securely affixed across opposite sides of subframe 110 to extend transversely relative to motor-grader assembly 10.
The subframe 110 provides further movable support of a rotatable ring member 126 which supports a working implement, an auger-moldboard assembly 128, therebeneath. Ring member 126 is supported for circular movement within a plurality of support blocks 130 beneath subframe 110, and suitable drive means (as will be further described) are mounted on subframel10 to provide circular rotation of ring member 126. The working element, auger-moldboard assembly 128, is secured beneath ring member 126 to rotate therewith. Thus auger-moldboard assembly 128 may consist of an auger element 132a and a blade element 132]: each supported by a respective connecting frame 134a and 134b adjustably connected beneath the ring member 126. Each of auger and blade elements 132a and 132k are separately movable as to angle of attack by means of respective hydraulic cylinders 136a and 136b, such structure to be further described in greater detail.
FIG. 3, 4 and 5 depict elements of the B END mobile assembly 14 in greater detail. It should be understood that the A END mobile assembly 12 may be constructed in identical manner. The tandem assembly 18b is actually a commercially available mechanical unit which enables four wheel drive of tandem arranged wheels, e.g. a separate type final drive utilizing a tandem axle. Casings 140 and 142 of tandem assembly 18b each include a separate sprocket and chain drive for each of the respective front and rear wheels 20b. The tandem assemblies include a transverse axle 144, and a pair of oppositely disposed clamping brackets 145 are welded beneath chassis 22b to provide secure engagement for support upon transverse axle 144. The tandem axle 144 receives drive rotation from a straight-through gear drive assembly 146 which is connected to receive rotational input through a coupling 148. The rotational input coupling 148 is taken from the output of a suitable hydraulic motor 150, e.g. a Series 27 Sundstrand hydraulic motor as driven from a suitable hydraulic pump 152, e.g. a Series 25 Sundstrand hydraulic pump. While specific hydraulic pump and motor equipment is identified, it should be understood that a great many combinations of differing power and type might be utilized to provide the drive power.
Hydraulic pressure generated in hydraulic pump 152 is also utilized in conventional manner to drive various of the hydraulic control element disposed about the motor-grader assembly 10, as will be further described. The hydraulic pump 152 is energized from diesel engine 24b as rotational engine output applied to a parallel array of flywheels 154 is transmitted on a plurality of V-belts 156 to a plural belt pulley 158 which, in turn, applies rotational input to hydraulic pump 152. Hydraulic pump 152 working in concert with conventional reservoir means (not shown) provides pressure output from a coupling 160 for conduction to an input coupling 162 for energization of the hydraulic motor 150. An additional plurality of flywheel pulleys 164 may be used to provide an additional rotational output from engine 2% for connection to other auxiliary pump means (not shown) which might be employed for powering auxiliary implement control mechanisms and such, as will be further described below. 7
A vertical pivot shaft 166 is rigidly secured through a floor plate 168 of chassis 22b (see also FIG. 6), and into rigid connection on top of gear box 146 such that is extends vertically from the center of tandem assembly 18b, i.e. straight-up from the intersection of drive axle 144 through gear drive 146. Pivot shaft 166 is inserted upward through a pivot bearing 170 which is formed to have oppositely disposed yoke arms 172 and 174 extending outward for steering connection as will be described. The pivot bearing 170 is also formed to have two oppositely disposed connecting tabs 176 and 178 (FIG. 5) and these serve to provide a connection for tilt control hydraulics as will be described below.
The pivot bearing 170 is mounted on pivot shaft 166 by means of a timken bearing 180 (FIG. 6) of conventional type interposed concentrically therebetween to provide necessary ease of the relative movement. The pivot bearing 170 is formed to have a flange 182 about its upper end, and a frame support bearing 184 having a bottom flange 186 is securely affixed thereon, the placement of support bearing 184 also serving to position and retain the timken bearing 180.
The support bearing 184 provides a rotational support for the frame end 78. A steel support rod 188 of suitable size and strangth is securely affixed as by welding through the front plate 190 of end frame 78, and suitable reinforcing such as lateral plate 192 is also provided. Various heavy construction techniques may be utilized to assure a strong bond between rod 188 and fame end 78 since the outer end of rod 188 must support the entire end of the main frame 16 upon mobile assembly 14. The outer end of rod 188 is rotationally retained within support bearing 84 in similar manner as that utilized for pivot shaft 166 within pivot bearing 170 That is, a timken bearing 194 is interposed within the annular space between support rod 188 and the inner surface of support bearing 184 and a retaining plate 196 is secured over the end of support bearing 184 in such manner as to assure secure positioning of timken bearing 194.
Steering control is effected by means of hydraulic cylinders 198 and 200 which are connected at pivot ends 202 and 284 to a connecting frame 206 which is rigidly secured through transverse beam 288 to the chassis 22b. Hydraulic pistons 218 and 212 are connected to respective yoke arms 172 and 174 of pivot bearing 178, and energization in concert of hydraulic cylinders 198 and 200 will provide rotation of yoke arms 172 and 174 (pivot bearing 178) relative to the pivot shaft 166 which is also secured to chassis 22b of mobile assembly 14.
Tilt control of main frame 16 is effected by control of hydraulic cylinders 214 and 216. Hydraulic cylinders 214 and 216 are each pivotally mounted by means of respective pivot pins 218 and 220 which are affixed thereto and pivotally interconnected with bracket plates 222 and 224 which are secured through suitable spacers 226 on front plate 190 of the bifurcated frame end 78. Hydraulic cylinders 214 and 216 extend respective pistons 228 and 230 downward into pivotal connection with connecting tabs 176 and 178 as disposed on opposite sides of pivot bearing 170. Coordinated control of hydraulic cylinders 214 and 216 effects tilting of frame end 78 and, therefore, main frame 16 about the longitudinal axis established by the bearing of support rod 188 within support bearing 184.
Frame locking is provided by a hydraulic cylinder 1 232 which may be selectively actuated to extend its piston rod (not specifically shown) into a locking hole which is formed within a locking block 234. Looking block 234 consists merely of a block of steel with a hole therethrough and which is secured at a front center point of forward plate 190 of end frame 78. Hydraulic cylinder 232 is then supported in longitudinal relationship by a mounting plate 236 suspended by a pair of support plates 238 each rigidly secured above the support bearing 184. The operator can effect control of cylinder 232 to extend the piston into locking block 234, this serving to maintain continuous positioning of the hydraulic locking cylinder 232 in vertical alignment, said vertical alignment assuring lateral horizontal positioning of frame end 78.
Referring now to FIG. 7, the main frame 16 is provided with unique adjustability through pivotal connection of end frames 78 and to the central frame 38. The subframe is secured from pivot assemblies 112 and 116 from opposite ends of central frame 38. That is, a bearing sleeve 240 secured from a sleeve hanger 242 as rigidly affixed beneath transverse member 114 (FIG. 2), a part of the main frame 38, is secured about the bearing pin 244 as supported by plates 246 and 248. Pivot assembly 116 at the opposite end is similarly constructed and supported from the opposite end of main frame 38 with a hanger 250 supporting a bearing sleeve 252 for pivotal support about a bearing pin 254 as secured between vertical plates 256 and 258.
A plurality of adjustable ring support blocks (FIG.2) are disposed at approximately equal distances about the underside of subframe 118 to support the ring member 126 moveably therearound. Each of support blocks 130 is individually adjustable for initial setting of level and centering of the ring 126. A ring drive hydraulic motor 260 is suitably mounted to work into a worm gear 262 which transmits rotational force to a 126. Referring to FIG. 7, each of the implement extending panels 134a and 13411 which serve to pivotally support adjusting plates 272a and 272b about pivotal connections 274a and 274b. The blade element 132b is secured by a suitable form of rigid connection 276b to said adjusting plate 272b for movement therewith. Hydraulic cylinder 136b, pivotally connected to ring member 126, extends a piston 278b into pivotal connection with a lever mechanism 280b which exerts positioning control on the blade element 132b. The bydraulic adjusting cylinder 136b, as well as adjusting plate 272b, connecting mechanism 276b and other related components are duplicated on each side of the ring member 126, ie as associated with each of opposite-side implement support panels 270. The auger element 1320 is secured in like manner by means of a suitable form of connection 276a as secured to a transverse frame member 271 and adjusting plate 272a for movement therewith. The hydraulic cylinders 136a (one on each side of ring member 126) extend respective pistons 278a into pivotal connection with lever mechanisms 280a for positioning control.
Referring now to FIG. 8, the auger element 132a may consist of an elongated cylinder 282 having a vane 284 arranged therearound in helical flight, the vane 284 being secured as by welding in helical configuration. The ends of cylinder 284 are then connected via shafts 286 and 288 for rotational retention within oppositelydisposed support assemblies 290 and 292 which extend from transverse frame member 271. A hydraulic motor 294 of well-known type is affixed to the outer portion of support member 292 to impart rotational drive to shaft 288. If desired, additional hydraulic drive can be imparted from a hydraulic motor 296 providing input to the opposite shaft 286. The hydraulic motors may be selected of desired rating from any of various commercially available types. In addition, although not specifically shown herein, it is contemplated that the auger element 132a may be broken in the middle, each half being separately, rotationally supported by suitable framing at the mid-point, so that each of the two sides may be independently-driven at the same or different rotational speeds.
FIG. 9 illustrates an alternativeform of auger element 298 of the cutter-auger type which includes a first helical flight of cutter bars 300 each carrying a cutter head 302 and a second helically arranged vane flight 304 wound in intersticed relationship. The cutter-auger 298 enables a rotary cutting action which has greater trimming and clearing capabilities, and which is especially attractive for use upon encountering certain difficult or highly compacted forms of earth material. The cutter-auger 298 may be disposed for use with hydraulically drive and support elements similar to those as shown in FIG.8.
In prototype equipment, the various control power functions about the motor-grader assembly have been effected by the use of hydraulic equipment; however, it should be understood that these functions can be performed by any of the conventional powering methods such as electrical, pneumatic, mechanical, or any combination of such power circuits. Control functions are readily regulated by the operator in the movable operating cab and, in addition to manual control, it is often desirable to enable automatic control of certain level and steering functions so that the motor-grader assembly 10 can be controlled totally or in part from an external grade reference such as a string line. Such manual-automatic control functions as specifically directed to hydraulic equipmentation are more particularly set forth hereinafter.
As shown in FIG. 10, a frame level control 312 provides setting of the elevation and level of main frame assembly 16. Such height control is effected by adjustment of the hydraulic cylinders and/or 94 (see also FIG. 1). A dual control assembly 314, situated in the operators cab 100, provides a first manual lever switch 316 for controlling A END elevation and a second manual lever control 318 for controlling B END height.
A pair of hydraulic connections 318 and 320 are connected to hydraulic cylinder 94 and to a four-way valve 322. The hydraulic valve 322 is a commercially available four-way type which has a quiescent or lock central portion 324 as well as oppositely porting spool sections 326 and 328. The valve 322 is then controlled by energization of one or the other of the end-mounted solenoids 330 and 332 which provide the proper flow of hydraulic fluid to the hydraulic cylinder 324. Hydraulic connections 334 and 336 are shown connected to a sump which may be any suitable form of hydraulic pump and reservoir system compatible with the available power requirements and drive input energy.
Manual lever switch 316 provides A END control by energization of electrical leads 338 and 340 to actuate one or the other of solenoids 330 and 332. Similarly, manual lever 318 provides B END actuation by energization of respective ones of electrical connections 342 and 344 to actuate solenoids 346 and 348. These solenoids 348 and 346 provide opposite actuation of a fourway hydraulic valve 350 which has a central lock up section 352 as well as oppositely flowing port sections 354 and 356. l- Iydraulic lines 358 and 360 connect between hydraulic cylinder 90 and four-way valve 350, with hydraulic lines 362 and 364 leading to a suitable hydraulic pressure sump.
The schematic representation of FIG. 11 illustrates a control system 366 which controls the cross slope of the subframe l 10 and whatever the working implement suspended therebeneath. The subframe has its cross slope adjusted in accordance with the actuation of hydraulic cylinders 118 and 120 which are oppositely connected in parallel to hydraulic lines 368 and 370 from a four-way valve 372 thereby to effect reciprocal cylinder action. Four-way valve 372 is connected to source hydraulic lines 374 and 376, and valve 372 consists of a lock up section 378 as well as opposite porting sections 380 and 382 which are positioned by oppositely actuating solenoids 384 and 386, respectively.
Solenoids 384 and 386 are controlled via electrical connections 388 and 390 from a suitable cross slope selector 392 which in turn, receives input from a manual cross slope control 394 and an automatic cross slope control 396. The manual cross slope control 394 may be located in the operating cab 100, while the automatic cross slope control 396 refers to control energization originating from suitable control sensors which are responsive to an external reference, as will be further described below. The automatic cross slope control 396 may be such as a gravity responsive switch with suitable output which is adjustable in relation to a pendulum or such.
Referring now to FIG. 12, an automatic-manual steering system 400 includes A END steering assembly 402 and a B END steering assembly 404. Manual steering is carried out by means of a steering control unit 406, the subject matter of FIG. 1 1 as will be further described, with steering end selection being made through a manual steering end selector switch 408. Automatic steering in response to sensing of an external reference is carried out in response to an A END steering control 410 or a B END steering control 412 as se lected by a steering selector 414 for input via leads 416 and 418 to each of an A END four-way valve 418 and a B END four-way valve 420.
Manual steering is carried out by steering control unit 406 which is controlled to steer one end or the other in response to actuation of manual steering end selector 408. Thus, in the case where the A END assembly 402 is to be steered, hydraulic fluid output in one direction or the other is present on hydraulic lines 422 and 424 to a double-ended hydraulic cylinder 426. The hydraulic cylinder 426 has one end 428 pivotally connected to a valve spool 430 of a heavy duty hydraulic valve 432, e.g. a thirty gallon four-way valve. The hydraulic valve 432 is energized by hydraulic pressure present on hydraulic lines 434 and 436 from a suitable sump, and valve output is directed through hydraulic lines 438 and 440 which are applied in opposite, parallel connection through respective steering cylinders 198a and 200a. Thus, applications of pressure differential, as between hydraulic lines 438 and 440, results in reciprocal action ofhydraulic cylinder pistons 212a and 2100 to effect pivoting of the steering yoke 172a-l74a which is in rigid affixure to the main frame 16.
Steering of the B END steering assembly 404 is effected by application of a hydraulic fluid differential between hydraulic lines 442 and 444 to a double-ended hydraulic cylinder 446. The hydraulic cylinder 446 drives a reciprocal valve spool 448 of a heavy duty hydraulicvalve 450 in the same manner as described for the A END assembly. That is, hydraulic source input is via lines 452 and 454 with regulating fluid output along hydraulic lines 456 and 458 to each of the hydraulic steering cylinders 460 and 462. The fluid input to hydraulic cylinders 460 and 462 is in parallel but opposite orientation to effect reciprocal movement of respective piston rods 210 and 212 thereby to effect steering movement.
Automatic steering,- as might be effected from suitable control sensors operating in response to an external reference, would originate as an electrical control signal in the form of a switch closure via leads 416 through 419 to energize predetermined valve solenoids. Thus, an energizing voltage on lead 416 to valve solenoid 418 changes four-way valve 418 from its center or lockup position 470 to spool position 472 which directs hydraulic fluid from pressure source lines 474 and 476 through respective hydraulic lines 438 and 440 to cause reciprocal energization of hydraulic cylinders 198a and 200a. Energization via lead 417 energizes solenoid valve 478 such that valve spool section 480 effects an opposite hydraulic pressure differential as between. hydraulic lines 438 and 440. Upon deis effected in similar manner. That is, electrical energization of 'either of leads 418 or 419 actuates respective valve solenoids 483 and 484. Actuation of solenoid valve 482 moves the valve spool from its lockup position 486 to the position where spool section 488 directs hydraulic fluid flow from source lines 490 and 492 through respective supply lines 456 and 458. Alternate energization of the valve solenoid 484 places spool section 494 in operation to reverse the pressure differential as between hydraulic lines 456 and 458, this effecting an opposite reciprocal effect as between the steering cylinders 460 and462.
The steering control unit 406 is shown in greater detail in FIG. 13 which includes various valve interconnections for responding to the manually operated steering wheel 500. Steering wheel 500 is connected by means of a suitable mechanical linkage 502 to operate an orbitrol mechanism 504. The orbitrol 504 is a wellknown type of hydraulic proportioning pump which varies the direction and force of hydraulic flow as between pressure lines 506 and 508. The lines 506 and 508 are connected to supply fluid pressure input to respective four-way hydraulic valves 510 and 512 with pressure return proceeding via hydraulic lines 514 and 516 to a fluid reservoir 518. Pressure relief is afforded by a common fluid connection 520 through oppositely oriented check valves 522 and 524 with return to the respective input pressure lines 506 and 508.
Electrical input from manual steering end selector 508 (FIG. 12) is provided by signal input on leads 526 and 528. Thus, input on lead 526 energizes solenoid valves 530 and 532 to bring respective valve spool sections 534 and 536 into function, this enabling A END steering control of the A END cylinder 426. Energization on lead 528 actuates valve solenoids 538 and 540 to move spool sections 542 and 544 in the proper flow position such that the B END cylinder 446 is energiz-- able inresponse to the adjustment of orbitrol 504 for manually steering the motor-grader assembly. The center spool positions 546 and 548 of the respective fourway valves 510 and 512 merely provide pressure balancing porting.
Referring now to FIG. 14, a main frame tilt control assembly 550 exercises selected control of lateral tilting of the A END or the B END or both ends simultaneously of the main frame relative to the respective A END and B END mobile assemblies 12 and 14. As shown, the B END is in the unlocked position as B END unlock control 552 provides energizing voltage via lead 554 to energize valve solenoid 556 such that a four-way valve 558 is actuated to energize hydraulic locking cylinder 232 such that its locking piston 560 is withdrawn out of engagement with locking block 354. Alternately, the A END unlock 562 will be de-energized such that valve solenoid 564 does not actuate a four-way valve 566. In this position, the valve 566 actuates locking cylinder 3630 such that a locking pin 560a is forced into locking engagement within locking block 234a.
When the A END unlock 562 de-energ izes to cause locking of the frame A END, a B END tilt control 568 may then be controlled by energization along either of electrical ends 570 or 572 to effect frame tilting relative to the B END mobile assembly. Energization of lead 570 energizes valve solenoid 574 such that a fourway valve 576 is actuated from its lockup spool section 578 to a spool section 58010 place a pressure differential between hydraulic lines 582 and 584.
When the A END unlock 562 is energized to withdraw the locking pin 560a the hydraulic tilt cylinders 216a and 214a may be energized to effect lateral tilting of main frame. Thus, an A END tilt control 590 may be selectively actuated to energize one or the other of leads 592 or 594 to energize respective solenoids 596 or 598. A hydraulic valve 600 is normally positioned with the lockup spool section 602 in circuit with pressure lines 604 and 606 and the hydraulic circuit lines 608 and 610. Pressure lines 608 and 610 are then connected in parallel to each of the hydraulic tilt cylinders 216a and 214a to effect reciprocal piston action upon energization of either of relays 596 or 598. Energization of relay 596 brings valve spool section 612 into function, while energization of relay 598 will bring the opposite valve spool section 614 to cause reverse pressure application.
A hydraulic override function is provided at each frame end through operation of check valves 616, 618, 620 and 622. Thus, not until the B END is unlocked with energization of valve solenoid 556 can the hydraulic tilt cylinders 216 and 214 be actuated. In the unlock attitude, valve spool section 558 applies pressure via hydraulic line 624 to open each of the respective check valves 616 and 618 such that they will then allow hydraulic pressure application as present on either of hydraulic lines 582 and 584 to the tilt control cylinders 214 and 216. Similarly, check valves 620 and 622 are open with application of pressure on hydraulic line 626 (opposite from that shown) to allow hydraulic actuation of tilt cylinders 214a and 216a.
Referring now to FIG. 15, a motor-grader assembly carries a suitable tracer bar 630 suspended in outrigged position as carried by support arms 119 and 121 and respective telescoping rods 123 and 125. Support arms 119 and 121 are each welded to opposite segments of subframe 110 to extend laterally outboard, while telescoping rods 123 and 125 are adjustably held within support frames 119 and 121. Telescoping rods 123 and 126 may be extended outward to any length as desired. A pair of pivotal brackets 632 and 634 serve to secure the sensor rods 630 on the ends of respective telescoping rods 123 and 125. The brackets 632 and 634 should be a suitable pivot assembly since it will quite often be required that telescoping rods 123 and 125 extend outward different distances. Such will be the case when motor-grader assembly 10 is operated along an external reference or string line 636 with main frame 16 canted relative to the A END and B END mobile assemblies 12 and 14. It should also be understood that telescoping rods can be readily fitted to extend outboard in the other direction, from the opposite ends of support arms 119 and 120, as exigencies demand.
A bracket 638 and support 640 aid in the automatic steering function by carrying a control sensor box 642 having a sensor rod 644 which is guided relative to string line 636. Automatic steering function at the opposite end is carried out by bracket 646, support arm 648, control box 650 and sensor rod 652. The length- ,wise placement of control sensor boxes 642 and 650 may also-be carried for differing applications. Thus, sensor boxes 642 and 650 may be aligned with the leading and trailing edges of the furthest displaced (lengthwise) wheels of respective mobile assemblies 12 and 14 as is shown in FIG. 15.
Automatic elevation sensing indications are also derived from string line 636 by means of brackets 654 and 656 which support additional control assemblies. Bracket 654 supports a control sensor box 656 and a counter-weighted sensing rod 658 which travels along string line 636. Similarly, bracket 656 carries a control sensor box 662 having a weighted sensor rod 664. The control sensor boxes 642, 650, 658 and 662 may all be a similar type such as is disclosed in a U.S. Pat. No. 3,514,630 entitled Line Tracer Control Device and issued in the name of Steele et al. Such control sensor box provides an electrical output in response to sensing variations relative to string line 636, such electrical signals being conducted back to appropriate control assemblies on the structure of motor-grader assembly 12.
The block diagram of FIG. 16 illustrates the interconnection of the various sensing and control components. Thus, output from A END steering sensor 650 is applied to steering selector 414 which may be a main panel control located in the operating cab 100. In the automatic attitude, A END steering output from line 670 is applied via line 672 to cause proper function of hydraulic valve 418 such that steering cylinders 198a and 200a are driven to effect a steering correction of the A END mobile assembly 12. Similarly, output from B END steering sensor 642 is conducted via lines 674 through steering selector 414 to a control lead 676 which actuates hydraulic valve 420 to effect steering actuation of the B END steering cylinder 198 and 200. Manual steering control from manual control unit 406 is an override control controlling selected ones of hydraulic valves 432 and/or 450 as shown more clearly in FIGS. 12 and 13.
Automatic elevation sensing takes place in similar manner in response to sensor control boxes,i.e. A END elevation sensor 662 and B END elevation sensor 658. The respective outputs are applied via leads 678 and 680 for circuit selection in selector 329. Selected outputs via control leads 682 and 684 are applied to respective hydraulic valves 322 and/or 350 to effect variation of height control cylinders 94 and 90.
It is also contemplated that cross slope control be carried out automatically by a suitable form of transversely oriented sensor which provides zero or no output indication relative to a preset elevation value. Thus, a suitable transverse level sensing mechanism may provide a control output for use in either the cross slope circuitry (FIG. 11) or the main frame tilt control circuitry and hydraulics (FIG. 14) or both. Such control output could be applied to effect automatic following of support structure which holds auger 132a and moldboard 1321: at proper cutting angle.
Operation The motor-grader assembly 10 is capable of operation in either longitudinal direction under control of either an operator or an associated external reference such as a string line. FIGS. 15 and 16 illustrate the manner whereby automatic elevation and steering sensing are carried out with reference to string line 636. In this case, the sensor positions are adjacent opposite longitudinal extremities of the motor-grader assembly 10 and in parallel disposition to main frame 16. It should be understood however that sensor rod 630 can be aligned at any angular relationship relative to main frame 16, depending upon the angle of attach of the motor-grader assembly in performing its earth-working undertaking.
Referring also to FIG. 12, automatic steering is carried out in response to A END steering control 410 and B END steering control 412 operating through steering selector 414. That is, more particularly, electrical outputs from A END steering sensor 650 and B END steering sensor 642 (FIG. 16) as applied for selective actuation of hydraulic valves 418 and 420. Thus, for A END steering, a sensed electrical output from A END automatic steering control 410 is conducted via one or the other leads 416 and 417, depending upon the direction of turning, to activate the associated valve solenoid 468 or 478 such that hydraulic valve 418 provides the requisite pressure direction through steering cylinders 198a and 200a.
Manual steering is effected in a different manner utilizing overriding power application with the orbitrol and steering wheel structure of FIG. 13. In this case, steering wheel 500 is manipulated to vary the orbitrol pump 504 to operate the proper one of A END or B END hydraulic valves 510 or 512. The valves 510 and 512, in turn, serve to energize respective drive cylinders 426 and 446 to position the hydraulic valve spools within respective hydraulic cylinders 432 and 450 (FIG. 12). Valves 432 and 450 are heavy duty hydraulicvalves which allow manual steering as an override function with continual correction being applied from an automatic steeringsource which may actuate then conducted via leads 682 and 684 to energize one or both of hydraulic valves 322 and 350 to activate their respective height control cylinders 94 and 90 located at each end of the main frame 16. Selector 329 also allows use of manual adjustment control 314 which provides parallel control of hydraulic valves 322 and 351).
The auger-moldboard assembly 128 is maintained in proper working attitude to a selected earth plane through control of the ring member 126. Thus, control of central frame 38, by actuation of hydraulic cylinders 90 and 94, allows setting at any selected longitudinal angle; and hydraulic cylinders 118 and 120 are controlled to set the transverse angle of the ring member 126 with respect to the central frame 38 and, therefore, at desired angle to the earths surface therebeneath. It is also contemplated to employ cross slope sensing to provide continual automatic-control of the transverse attitude of the auger-moldboard assembly 128.
It should be understood that various other schemes, both automatic and manual, may be employed in controlling a motor-grader constructed in accordance with the invention. Automatic control measures may include various other external references in addition to the conventional string line practices, such references being delineated by such as light effects, relative gravity effects, surface or slab sensing, etc. Also, while the motor-grader assembly is shown as carrying a cutter-auger implement 128, it is contemplated that still additional attachment accessories such as ripping implements, trimmer-spreader attachments, excavator assemblies, scanifiers, etc. may be carried beneath the main frame in operative alignment to carry out the earth-working function in response to either manual or automatic control.
The foregoing discloses a novel-working combination for accessory utilization with motor-grader assemblies, such machines serving to enable greater work efficiency per time expenditure. A double-ended motorgrader assembly has the additional advantage of being reversible in operation such that various turning around maneuvers are eliminated, and this serves to cut down greatly on job time. The control systems disclosed herein offer particular advantages in steering and elevation control of such double-ended machines, elevation control being effected such that an entire midframe assembly is variable both as to elevation and level relative to the earth or other selected references, and automatic-manual steering can be effected even from an offset or canted midframe position, as may be required in particular earth-working situations. The further combination of the rotary cutter and moldboard work implements, functioning in coaction, enable operational advantages heretofore unrealizable in motor-grader apparatus or, for that matter, any single type of mobile machine of relatively general earthworking application.
Changes may be made in combination and arrangement of elements as heretofore set forth in the specification and shown in the drawings; it being understood that changes may be made in the embodiments disclosed without departing from the spirit and scope of the invention as defined in the following claims.
What is claimed is:
l. Earth-working apparatus comprising:
first and second mobile means each including drive power source and mobile structure;
central frame means of generally elongated form having each of first and second ends pivotally affixed to respective first and second mobile means for support therebetween;
subframe means secured to and pivotally supported from said central frame means;
ring member means rotatably affixed beneath said subframe means for circular rotation thereof;
rotatable auger means rotatably and pivotally affixed beneath said ring members for circular rotation therewith;
moldboard means disposed generally parallel to said auger means and pivotally affixed beneath said ring member means for circular rotation therewith; first and second control means for adjusting the position of each of said augermeans and mold-board means relative to said ring member means; and means accomodating an operator rotatably affixed on top of said central frame means for selected positioning thereon to gain optimum surveillance.
2. Earth-working apparatus as set forth in claim 1 wherein said first and second control means comprise:
first and second hydraulic cylinder means each pivotally connected between said ring member and the respective auger means and moldboard means.
3. Earth-working apparatus as set forth in claim 1 which is further characterized to include:
drive means connected to said auger means to impart rotationable drive force to said auger means.
4. Earth-working apparatus as set forth in claim 3 wherein said drive means consists of a hydraulic motor.
5. Earth-working apparatus as set forth in claim l which is further characterized in that:
at least a portion of said central frame means is adjustable as to the longitudinal angle; and
means for adjusting said longitudinal angle of said central frame means portion.
6. Earth-working apparatus as set forth in claim 1 which is further characterized in that:
at least a portion of said central frame means is adjustable as to longitudinal angle; and
means for adjusting said longitudinal angle of said central frame means portion.
7. Earth-working apparatus as set forth in claim 1 wherein said auger means comprises:
central shaft means of generally elongated form; and
vane means arranged in a continual helical flight making a plurality of revolutions around said shaft means along the length thereof.
8. Earth-working apparatus as set forth in claim 7 which is further characterized to include:
a plurality of toothed cutter elements arranged in a helical flight and extending around said central shaft means a plurality of times at a pre-set distance displaced from said flight of vane means.
9. Mobile earth-working apparatus, comprising:
frame means;
subframe means pivotally supported from the frame means;
ring member means rotatably affixed beneath the subframe means for circular rotation thereof;
rotatable auger means rotatably affixed beneath the ring member means for circular rotation therewith;
moldboard means disposed generally parallel to the auger means and affixed beneath the ring member means for circular rotation therewith;
hydraulic cylinder means secured to the frame means and to the subframe means pivotally controlling the attitude of the subframe means; thereby controlling the attitude of the auger means and the moldboard means; and control means connected to the auger means and the moldboard means adjusting each relative to the subframe means, the control means comprising: first and second hydraulic cylinder means each having one end connected to the subframe means and having respective remaining ends connected to the moldboard means and the auger means; and actuation means for controlling the hydraulic cylinders to raise and lower the moldboard means and the auger means. 10. Apparatus as set forth in claim 9 wherein said auger means comprises:
central shaft means of generally elongated form; vane means arranged in a continual helical flight and extending a plurality of revolutions around said shaft means along the length thereof. 11. An apparatus as set forth in claim 10 which is further characterized to include:
a plurality of toothed cutter elements arranged in a helical flight extending around said shaft means a plurality of times at a pre-set distance displaced from said flight of vane means.

Claims (11)

1. Earth-working apparatus comprising: first and second mobile means each including drive power source and mobile structure; central frame means of generally elongated form having each of first and second ends pivotally affixed to respective first and second mobile means for support therebetween; subframe means secured to and pivotally supported from said central frame means; ring member means rotatably affixed beneath said subframe means for circular rotation thereof; rotatable auger means rotatably and pivotally affixed beneath said ring members for circular rotation therewith; moldboard means disposed generally parallel to said auger means and pivotally affixed beneath said ring member means for circular rotation therewith; first and second control means for adjusting the position of each of said auger means and mold-board means relative to said ring member means; and means accomodating an operator rotatably affixed on top of said central frame means for selected positioning thereon to gain optimum surveillance.
2. Earth-working apparatus as set forth in claim 1 wherein said first and second control means comprise: first and second hydraulic cylinder means each pivotally connected between said ring member and the respective auger means and moldboard means.
3. Earth-working apparatus as set forth in claim 1 which is further characterized to include: drive means connected to said auger means to impart rotationable drive force to said auger means.
4. Earth-working apparatus as set forth in claim 3 wherein said drive means consists of a hydraulic motor.
5. Earth-working apparatus as set forth in claim 1 which is further characterized in that: at least a portion of said central frame means is adjustable as to the longitudinal angle; and means for adjusting said longitudinal angle of said central frame means portion.
6. Earth-working apparatus as set forth in claim 1 which is further characterized in that: at least a portion of said central frame means is adjustable as to longitudinal angle; and means for adjusting said longitudinal angle of said central frame means portion.
7. Earth-working apparatus as set forth in claim 1 wherein said auger means comprises: central shaft means of generally elongated form; and vane means arranged in a continual helical flight making a plurality of revolutions around said shaft means along the length thereof.
8. Earth-working apparatus as set forth in claim 7 which is further characterized to include: a plurality of toothed cutter elements arranged in a helical flight and extending around said central shaft means a plurality of times at a pre-set distance displaced from said flight of vane means.
9. Mobile earth-working apparatus, comprising: frame means; subframe means pivotally supported from the frame means; ring member means rotatably affixed beneath the subframe means for circular rotation thereof; rotatable auger means rotatably affixed beneath the ring member means for circular rotation therewith; moldboard means disposed generally parallel to the auger means and affixed beneath the ring member means for circular rotation therewith; hydraulic cylinder means secured to the frame means and to the subframe means pivotally controlling the attitude of the subframe means; thereby controlling the attitude of the auger means and the moldboard means; and control means connected to the auger means and the moldboard means adjusting each relative to the subframe means, the control means comprising: first and second hydraulic cylinder means each having one end connected to the subframe means and having respective remaining ends connected to the moldboard means and the auger means; and actuation means for controlling the hydraulic cylinders to raise and lower the moldboard means and the auger means.
10. Apparatus as set forth in claim 9 wherein said auger meaNs comprises: central shaft means of generally elongated form; vane means arranged in a continual helical flight and extending a plurality of revolutions around said shaft means along the length thereof.
11. An apparatus as set forth in claim 10 which is further characterized to include: a plurality of toothed cutter elements arranged in a helical flight extending around said shaft means a plurality of times at a pre-set distance displaced from said flight of vane means.
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US3841410A (en) * 1973-03-05 1974-10-15 V Nikitin Earth-moving and planing machine operable on the sides of hills and mountains
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US20170247049A1 (en) * 2016-02-29 2017-08-31 Bomag Gmbh Steering device, construction machine with a steering device and method for steering a steerable machine
US10604177B2 (en) * 2016-02-29 2020-03-31 Bomag Gmbh Steering device, construction machine with a steering device and method for steering a steerable machine

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