US3568778A - Motor grader apparatus - Google Patents

Motor grader apparatus Download PDF

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Publication number
US3568778A
US3568778A US793274*A US3568778DA US3568778A US 3568778 A US3568778 A US 3568778A US 3568778D A US3568778D A US 3568778DA US 3568778 A US3568778 A US 3568778A
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frame
mobile
central frame
earth working
hydraulic
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US793274*A
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George W Swisher Jr
Gordon L Spivey
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CMI Terex Corp
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CMI Corp
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Assigned to FIRST NATIONAL BANK OF CHICAGO, THE, COMMERCIAL BANK,N.A., BANK OF AMERICA NATIONAL TRUST AND SAVINGS ASSOCIATION,, FIDELITY BANK N A., BANK OF PENNSYLVAIA, HIBERNIA NATIONAL BANK IN NEW ORLEANS THE, MERCATILE NATIONAL BANK AT DALLAS COMMERCE BANK,, NORTHERN TRUST COMPANY, THE, REPUBLICBANK DALLAS,N.A., MANUFACTURERS HANOVER TRUST COMPANY, FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE, CONTINENTAL ILLINOIS NATIONAL BANK AND TRUST COMPANY OF CHICAGO, FEDERAL DEPOSIT INSURANCE CORPORATION AS RECEIVER FOR PENN SQUARE BANK,N.A. reassignment FIRST NATIONAL BANK OF CHICAGO, THE 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 MERCANTILE NATIONAL BANK AT DALLAS, FIRST NATIONAL BANK AND TRUST COMPANY OF OKLAHOMA CITY, THE, CONTINENTAL ILLINOIS NATIONAL BANK AND TRUST COMPANY OF CHICAGO, COMMERCIAL BANK, N.A., BANK OF AMERICA NATIONAL TRUST AND SAVINGS ASSOCIATION, BANK OF PENNSYLVANIA, COMMERCE BANK, NORTHERN TRUST COMPANY, THE, FIDELITY BANK N.A., REPUBLICBANK DALLAS, N.A., MANUFACTURERS HANOVER TRUST COMPANY, FIRST NATIONAL BANK OF CHICAGO reassignment MERCANTILE NATIONAL BANK AT DALLAS 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.
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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
    • B62D53/023—Tractor-trailer combinations; Road trains comprising a uniaxle tractor unit and a uniaxle trailer unit with two or more coupling joints allowing staggering of the units from a central plane
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D59/00—Trailers with driven ground wheels or the like
    • B62D59/04—Trailers with driven ground wheels or the like driven from propulsion unit on trailer
    • 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

  • Cl- Apparatus for earth working consists of Aolb 51/02, 362d 5/00 two similar mobile assemblies including drive engine and trac- [50] Field of Search 172/785, tion elements and which are oriented in backtmback manner 435, 786-793, 780-784, 292; 37/ 129; 180/77 to support a main frame therebetween in articulated suspen- (S), 5O, 51, 23, 66 sion.
  • the main frame is adapted to carry a subframe which further supports one or more earth working implements in ad- [56] References Cited justable manner therebelow, and the operating cab is movably UNITED STATES PATENTS supported by a support arm which is rotatably affixed at a cen- 2,494,324 l/ 1950 Wright 172/793 tral position on the main frame.
  • the invention relates generally to earth working apparatus, and, more particularly, but not by way of limitation, it relates to improved motor grader machinery having increased power capabilities.
  • the present invention contemplates a double-ended, double-articulated motor grader assembly which includes a fully controllable main frame and working elements as well as a movable operating cab.
  • the invention consists of first and second mobile assemblies each having similar drive power source and mobile elements, and each supporting opposite ends of a main frame which carries a subframe and working elements as well as the rotatable operating cab; the construction being such that the motor grader assembly is fully operable in either direction along its axis of alignment.
  • the apparatus includes power apparatus for controlling steering, main frame tilt, main frame longitudinal attitude, and operating cab position, such control being interactive to provide proper, continual operation of the motor grader assembly along a work path.
  • FIG. 1 is a side elevation of a motor grader assembly constructed in accordance with the invention
  • H6. 2 is a top plan view of the motor grader assembly as shown in FIG. ll;
  • FIG. 3 is an enlarged elevation with parts shown in cutaway of a mobile assembly of 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 lines 5-5 of FIG. 1;
  • FIG. 6 is an enlarged side elevation of the main frame of the invention with parts shown in cutaway;
  • FIG. 7 is a top plan view of the subframe of the invention.
  • FIG. 8 is a section taken along lines 8-8 of FIG. 7;
  • FIG. 9 is an enlarged side elevation of the main frame and operating cab of the invention with parts shown in cutaway;
  • FIG. 10 is a side elevation of an alternative form of working element which may be used with the invention.
  • FIG. 11 is an operational plan view of the motor grader assembly in one form of use.
  • FIG. 12 is an operational plan view of the motor grader assembly in reversed position.
  • 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 20d and 20b, respectively.
  • motor grader 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 22! 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 motor grader 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 purposes about motor grader assembly 10 as will be further described below.
  • Hood cowls 26a and 2611 are affixed over respective engines 24a and 24b in secure manner relative to chassis 22a and 221; while conventional bumper structure 28a and 28b, exhaust stack 30a and 30b, and air cleaners 32a and 321) 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 of 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 curve, i.e. central frame ends 40 and 42 each including a respective pivot eye 44 and 4M5 formed in the 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 therefrom.
  • Support shafts 54 and 60 extend outward in parallel, spaced and horizontal disposition from one side of central frame 33 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 as.
  • 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, 7 4 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 semicircular bearing bracket 82, 84, 86 and 88 in secure affixture for the purpose of movably seizing each of the respective support shafts 54, S6, 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 afiixture about vertical axes 36 and 34.
  • the hydraulic cylinder 98 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 its 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 112 which is rigidly secured beneath a crossmember 114 extending between frame arms 62 and 64.
  • first pivot assembly 112 which is rigidly secured beneath a crossmember 114 extending between frame arms 62 and 64.
  • pivot assembly 116 which is secured beneath a crossmember (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 118 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.
  • the subframe 110 provides further movable support of a rotatable ring member 126 which supports a working implement, e.g. a blade 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 subframe 110 to provide circular rotation of ring member 126.
  • the working element, such as blade assembly 128, is secured beneath ring member 126 to rotate therewith.
  • blade assembly 128 may consist ofa connecting frame 132 supporting an earth cutting blade 134 which is movable as to angle of attack by means of a hydraulic cylinder 136, such structure to be further described in greater detail.
  • the tandem assembly 1812 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 221: 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 elements 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 24b 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.
  • a vertical pivot shaft 166 is rigidly secured through a floor plate 168 of chassis 22b, and into rigid connection on top of gearbox 146 such that it extends vertically from the center of tandem assembly 1812, 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 also be described below.
  • the pivot bearing 170 is mounted on pivot shaft 166 by means of a Timken bearing 180 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 strength 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 frame 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.
  • 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 204 to a connecting frame 206 which is rigidly secured through transverse beam 208 to the chassis 22b.
  • Hydraulic pistons 210 and 212 are connected to respective yoke arms 172 and 174 of pivot bearing 170, and energization in concert of hydraulic cylinders 198 and 200 will provide rotation of yoke arms 172 and 174 (pivot bearing 170) 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 2Z4 anc 216 are each pivotally mounted by means of respective pivot pins 218 and 220 which are affixed thereto and pivotally interconnected within bracket plates 222 and 224 which are secured through suitable spacers 226 or 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 efiects 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 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.
  • Locking 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 mainframe 16 is provided with unique adjustability through pivotal connection of end frames 78 and 80 to the central frame 38.
  • the subframe 110 is secured from pivot assemblies 112 and 116 from opposite ends of central frame 38.
  • 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.
  • subframe 100 is constructed from two parallel, longitudinal beams 260 and 262 which are integrally connected with spaced, vertical plates 256 and 258 at one end and 246 and 248 at the opposite end.
  • a plurality, e.g. six, of frame beams 264 are then welded into a generally equisided polygonal frame, and a transverse beam 266 supports across subframe 110 as secured at opposite lateral points 268 and 270.
  • Further diagonal beams 272 are welded into the framework in supporting manner as shown.
  • a plurality of adjustable ring support bearing assemblies 274 are disposed at approximately equal distances about the underside of subframe 110 to support the ring 126 moveably therearound.
  • each of ring bearing assemblies 274 consists of right-angle block 276 welded to the underside of crossbeam 272, and each contains a plurality of vertical, threaded adjustment holes 278 as well as a plurality of horizontal, threaded adjustment holes 280.
  • a hearing plate 282 having a suitably flame-hardened bearing surface 284 is secured within the block 276 by means of a plurality of threaded fasteners 286 such that the outer end or bearing surface 284 of bearing plate 282 supports a concentric, geartoothed inner flange 288 of ring 126.
  • An additional plurality of horizontal threaded fasteners 290 are inserted through threaded holes 280 for the purpose of laterally positioning the respective ring bearing plate 282.
  • a ring drive hydraulic motor 292 is suitably mounted on a mounting plate 294 as rigidly secured between parallel beams 260 and 262. Hydraulic motor 292 is disposed to work into a worm gear 296 which transmits rotational force to a drive gear 298. Drive gear 298 is positioned in engagement with the inner, gear-toothed flange 288 of ring 126 to transmit motion therethrough.
  • a pair of implement support plates 300 and 302 are rigidly altixed in parallel disposition across opposite sides of ring 126.
  • each of the implement support panels 300 and 302 has a similarly shaped and downward extending panel 132 which serves to pivotally support an adjusting plate 306 about a pivotal connection 308.
  • a blade 134 is secured by a suitable form of connection 312 to said adjusting plate 306 for movement therewith.
  • Hydraulic cylinders 136 pivotally connected to ring 126, extend a piston 316 into pivotal connection with a lever mechanism 318 which exerts positioning control on the blade 134.
  • the hydraulic adjusting cylinder 136, adjusting plate 306, connecting mechanism 312 and other re lated components are duplicated on each side of the ring 126, i.e. as associated with each of implement support panels 300 and 302 (FIG. 7).
  • the operating cab can be controlled for disposition at any position relative to main frame 16.
  • the cab support arm 106 is rotatable about vertical axis 108 as driven by the suitable motor 320.
  • Motor 320 may be any suitable powering device, e.g. a conventional model of Racine Hydraulic Torque motor, and motor 320 provides rotational input into a suitable gear drive box 322 which provides a stepped down rotational output on shaft 324 to pinion gear 326.
  • the pinion gear 326 is in mesh with a ring drive gear 328 which is rigidly secured in conventional manner to bottom panel structure 330 of support arm 106 such that it is integral with the structure of support arm 106.
  • bearing 332 is secured on the top center of mounting plate 48.
  • Bearing 332 may be any acceptable form of bearing, consonant with proper design, for bearing upward against the underside of a bearing plate 334 which is secured as by welding across the upper annulus of ring gear 328.
  • the bearing 332 consists of a concentric race ball bearing assembly which supports ring gear 328 and support arm 106 rotatably and slightly displaced above the upper surface of mounting plate 48.
  • Brake assembly 336 is actuated by a hydraulic cylinder 338 which is controlled by pressure lines 340.
  • Hydraulic cylinder 338 is end-mounted over the top center of a generally round brake housing 342 which is affixed integrally with bottom panel structure 330, ring gear 328 and other of the frame structure of support arm 106.
  • a piston 344 from hydraulic cylinder 338 extends downward into rigid affixture with a circularly shaped pressure pad 346 which carries a layer of brakelining material 348 thereon for braking contact at selected positions around mounting plate 48.
  • a retaining ring 350 is formed of a size to fit under the brake housing 342 and slightly larger than pressure plate 346 such that it retains a plurality of compression springs 352 around a circular comb 354 which is secured about'the upper surface of pressure plate 350.
  • compression springs 352 act'in concert against pressure plate 346 to urge the brake liner material 348 into secure, braking contact at a selected position on mounting plate 48. Actuation of hydraulic cylinder 338 will serve to withdraw piston 344 to release the grip of brake lining material 348 during those times when positioning control of operating cab 100 is being effected by operation of drive motor 320.
  • FIG. 10 discloses an alternative form of working implement which can be employed instead of the blade implement 128 as shown in FIG. 6.
  • the implement of FIG. 10 includes the similar blade assembly 128 as well as an auger distribution assembly 360.
  • the auger assembly 360 may be similarly hung from ring 126 by supporting it on each side by means of a hanger panel 362 and pivot plate 364 as attached at pivotal point 366.
  • An auger element 368 is rotatably supported by the pivot plates 364 and an end-mounted hydraulic motor 370 of suitable size and capacity is affixed thereto in rotational driving connection.
  • a lever arm 372 is secured as by welding to pivot plate 364 and a hydraulic cylinder 374 and piston 376 function to raise and lower auger 368 relative to the work surface.
  • control and power functions about the motor grader assembly have been effected by the use of hydraulic equipment in prototype 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 transmission methods.
  • Control functions are readily regulated by the operator in the 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 stringline.
  • the motor grader assembly 10 may be employed for any of a large number of diverse grading or scraping operations and the operator can exercise a very high degree of control over the entire structure even though it is quite large.
  • the main frame 16 is controllable as to lateral or sideways tilt relative to either one or both of the A END and B END mobile assemblies 12 and 14, respectively.
  • hydraulic cylinders 214 and 216 in concert will enable such tilt control to whatever the desired tilt angle, and this also imparts tilt angle to the subframe 110 and working implement 128 suspended underneath main frame 16.
  • Steering is effected by concerted control of hydraulic cylinders 198 and 200 (see FIG. 4) on each of the A END and 8 END mobile assemblies 12 and 14.
  • Control of hydraulic cylinders 198 and 2% turns the respective mobile unit relative to main frames 16 in order to effect an overall machine turning action. It should be noted too, however, that necessity for turning the motor grader assembly 10 is lessened by a great margin since it is effectively a double-ended machine capable of equal degrees of reliability and efficiency of operation in either direction.
  • the motor-grader assembly can make continual grading passes along a work path without the necessity for turning the entire machine around.
  • the motor grader assembly 10 is proceeding in the direction of arrow 380 with B END mobile assembly 14 in front and the A END mobile assembly 12 at the rear.
  • the main frame 16 is canted at an optimally adjusted angle between the A END and B END units 12 and 14 so that blade 134 can be brought into contact with the rough earth mass 382 at the best grading angle.
  • the operating cab 100 is positioned at a place where the operator will have the best view of the grading path, i.e. maximum ability to see not only the work path but in front of the forward mobile assembly 14 and behind the rear or A END mobile assembly 12. Operating cab 100 is readily adjustable at any time to gain advantage of a better view.
  • the motor grader assembly 10 can, with slight adjustment, be reversed to proceed back along the work area, rough earth mass 382, in the direction of arrow 384.
  • the A END mobile assembly 12 leads while the operator has steered the B END mobile assembly 14 leftward to reverse the cant of main frame 16 relative to A END mobile assembly 12.
  • the operator has repositioned his operating cab 100 at a most optimum viewing position relative to the work area.
  • the blade 134 is continuously rotatable under subframe 110, and it is here readjusted for its grading function in the direction of arrow 384.
  • main frame 16 in addition to steering and tilt control of main frame 16 relative to the A END and 8 END mobile assemblies 12 and 14, main frame 16 embodies additional positioning control for effecting height and/or level control of central frame 38.
  • Hydraulic cylinders 90 and 9 5 can be operated to alter the relative position of respective end frames 78 and 80 with respect to the central frame 38. For example, if both of cylinders and 94 are operated to withdraw pistons 92 and 96, the general level of central frame 38 will be raised. Countermovement to or compensation for the raising of central frame 38 results in a clockwise (as shown in FIG.
  • chassis 22b of B END mobile assembly 14 moves about the support center of tandem assembly 18b, and it results in counterclockwise movement of chassis 22a of A END mobile assembly 12 about the supporting center of tandem assembly 18a.
  • the hydraulic cylinders 90 and 94 can be operated varying amounts to adjust subframe 110 and the working element or blade assembly 128 to an optimum position.
  • hydraulic cylinders 118 and 120 can be operated to exercise control tilt of subframe relative to main frame 16.
  • subframe rests pivotally from pivot assemblies 112 and 116 it can be adjusted hydraulically to a desired attitude of transverse angle or level, and this placement carries through for coarse positioning of the blade 134 of blade assembly 128.
  • FIG. 10 depicts a working unit which includes both a blade 134 and an auger distributing assembly 360.
  • This is only one of many forms of working element which may be compatible for use with the motor grader assembly 10. It is contemplated that various other forms of rotary cutter, cutter-moldboard combinations, snow attachments, asphalt ripping implements, subsoil plows, etc. are readily adaptable for mounting below the subframe 110.
  • Motor grader assembly 10 may also be readily used in a form of automatic profile grading wherein both the steering and working implement level control are controlled from an external reference such as a stringline.
  • the foregoing discloses a novel motor grader apparatus which is more powerful and more efficient for a wider range of applications than any of the existing types of similar equipment.
  • the motor grader is capable of manual, automatic, or combined manual-automatic control for use in a variety of applications ranging from surface maintaining to rough grade cutting.
  • the machine enjoys particular advantages from the operators viewpoint in that it embodies a readily movable cab which is easily controllable by the operator for positioning at a point which renders the most advantageous v ew of the work area, machine components, etc.
  • Earth working apparatus comprising: first mobile means, including a drive power source, a tandem wheel assembly, and support means supporting said drive power source and being connected to said tandem wheel assembly at a point which is central with respect to the tandem wheel assembly; second mobile means, including a drive power source, a tandem wheel assembly, and support means supporting said drive power source and being connected to said tandem wheel assembly at a point which is central with respect to the tandem wheel assembly; first frame end means having a bifurcated end and a single end and being pivotally affixed to said first mobile means;
  • second frame end means having a bifurcated end and a single end and being pivotally affixed to said second mobile means;
  • central frame means having elongated form and being pivotally affixed at first and second points along its long dimension to respective bifurcated ends of said first and second frame end means;
  • Earth working apparatus asset forth in claim 2 which is further characterized to include: v
  • Earth working apparatus as set forth in claim 1, wherein said first mobile means is further characterized to include:
  • first hydraulic means connected centrally on said mobile means and to a side position of said central frame means; actuating means for controlling said first hydraulic means to effect tilt positioning of said central frame means;
  • pivot bearing means including first and second steering levers affixed to said first frame end means such that said first and second steering levers extend outward on opposite sides thereof; v first hydraulic means connected between said first steering lever and said first mobile means to effect pivotal movement between said first mobile means and said first frame end means; and second hydraulic means connected between said second steering lever and said first mobile means to effect opposite pivotal movement between said first mobile means and said first frame end means.
  • pivot bearing means including first 1 and second steering levers afiixed to said first frame endmeans such that said posite sides thereof;
  • first hydraulic means connected between said first steering lever and said first mobile means to effect pivotal movement between said first mobile means and said first frame end means;
  • pivot bearing means affixed to each of said first and second frame end means to extend steering levers outwardly on each side;
  • first and second hydraulic steering means each connected to opposite sides of said first and second mobile means and to opposite ones of said steering levers to effect reciprocal steering action.
  • Earth working apparatus as set forth in claim 1, which is further characterized to include:
  • first power means affixed on said central frame and controllable to move said first frame end means relative to said central frame means to raise and lower said central frame means;
  • first and second steering levers extend outward on opfirst power means connected between a first end of said central frame means and an end of said first end frame means such that said first power means can be actuated to vary the angle of joinder of said central frame means and first end frame means at said respective pivotal connection;
  • second power means connected between a second'end of said central frame means and an end of said second end frame means such that said second power means can be actuated to vary the angle of joinder of said central frame means and second end frame means at said respective pivotal connection.
  • operating cab means including seat space and controls rigidly affixed to the second end of said support arm means;
  • control means including drive and brake structure for positioning said support arm means and operating cab means at a selected position relative to said central frame means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Body Structure For Vehicles (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
  • Agricultural Machines (AREA)
US793274*A 1969-01-23 1969-01-23 Motor grader apparatus Expired - Lifetime US3568778A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US79327469A 1969-01-23 1969-01-23

Publications (1)

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US3568778A true US3568778A (en) 1971-03-09

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ID=25159533

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US793274*A Expired - Lifetime US3568778A (en) 1969-01-23 1969-01-23 Motor grader apparatus

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Country Link
US (1) US3568778A (enrdf_load_stackoverflow)
JP (1) JPS4923681B1 (enrdf_load_stackoverflow)
CH (1) CH506662A (enrdf_load_stackoverflow)
DE (1) DE1931015C3 (enrdf_load_stackoverflow)
FR (1) FR2028914B1 (enrdf_load_stackoverflow)
GB (1) GB1219037A (enrdf_load_stackoverflow)

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3637036A (en) * 1970-06-15 1972-01-25 Cmi Corp Hydrostatic drive system
US3693722A (en) * 1970-08-11 1972-09-26 Brohigbu Ltd Fine grading device for rubber tire road grader
US3735818A (en) * 1969-01-23 1973-05-29 Cmi Corp Oklahoma City Motor-grader implements
US3791052A (en) * 1970-01-26 1974-02-12 Lely Nv C Van Der Tractor comprising a pivotable driver seat
US3884310A (en) * 1972-06-30 1975-05-20 Vyzk Ustav Zemedelskych Stroju Working aggregate, more particularly for soil cultivation
US3891003A (en) * 1974-06-18 1975-06-24 Clark Equipment Co Hydraulic manifold
US3905446A (en) * 1971-07-06 1975-09-16 Western Geophysical Co Self-propelled seismic signal generator
DE2544525A1 (de) * 1974-10-05 1976-05-06 Coles Cranes Ltd Fahrbarer kran
US3972378A (en) * 1975-01-23 1976-08-03 Caterpillar Tractor Co. Swing lock means for an hydraulic excavator
US3999615A (en) * 1975-04-23 1976-12-28 Caterpillar Tractor Co. Motor grader with circle mounting blade and wedge control system
US4015669A (en) * 1976-03-03 1977-04-05 Caterpillar Tractor Co. Circle mounting bar and circle assembly for a motor grader
US4074768A (en) * 1976-08-30 1978-02-21 Caterpillar Tractor Co. Blade support and control arrangement for a motor grader
US4167826A (en) * 1975-08-18 1979-09-18 Feliz Jack M Self-loading dualistic earth excavator with connecting telescopic conveying and dualistic distribution means
US4279312A (en) * 1979-03-29 1981-07-21 Pyle Donald L Dual tractor road grader with double arched center frame
FR2551015A1 (fr) * 1983-08-25 1985-03-01 Lignones Hubert Vehicule a train avant et chassis deportables lateralement relativement
US4611683A (en) * 1981-07-23 1986-09-16 Hilmer Elwyn P Farm tractor
US4768601A (en) * 1986-07-01 1988-09-06 Kabushiki Kaisha Okano Kosan Uneven ground vehicles
US4819738A (en) * 1985-07-29 1989-04-11 Fountain Glen L Vehicle for supporting an implement
US4947956A (en) * 1987-10-13 1990-08-14 Clark Equipment Company Hydrostatic transmissions system for an articulated vehicle
US5190398A (en) * 1991-03-12 1993-03-02 Swisher Jr George W Apparatus for preparing a road bed
US5813228A (en) * 1995-03-29 1998-09-29 Shin Caterpillar Mitsubishi Ltd. Carrier vehicle equipped with a swing table
US6029431A (en) * 1994-11-23 2000-02-29 Dowler; David Vehicle
US6149342A (en) * 1999-03-25 2000-11-21 Cmi Corporation Anti-bridging mechanism
US6637532B2 (en) 2000-10-24 2003-10-28 Timberjack Oy Method in working machine
US6942041B1 (en) * 2004-06-10 2005-09-13 Deere & Company Self-propelled agricultural vehicle constructed using a standard row-crop tractor as a base
US20060151187A1 (en) * 2002-12-18 2006-07-13 Damm Juergen Rear chassis for a grader
USD531647S1 (en) 2005-10-25 2006-11-07 Deere & Company Cab for a motor grader
US20080110651A1 (en) * 2006-10-31 2008-05-15 Deere & Company Full support bearing for grader circle
US20080169110A1 (en) * 2005-08-08 2008-07-17 Horst Schwab Gmbh Multi-Purpose Working Device
US8006796B1 (en) * 2007-10-18 2011-08-30 Fontaine Roger F Personal vehicle
US20220355884A1 (en) * 2021-05-06 2022-11-10 Alexey INKIREV Vehicle with a stability system that compensates for the centrifugal force and the transverse component of the inertia force when cornering

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1058247A (en) * 1975-12-01 1979-07-10 Robert N. Stedman Cab, pinned on for double articulated tractor
JPS5491543U (enrdf_load_stackoverflow) * 1977-12-10 1979-06-28
JPS5835013U (ja) * 1981-09-01 1983-03-07 エヌ・テ−・エヌ東洋ベアリング株式会社 輪体の回り止め装置
DE8303097U1 (de) * 1983-02-05 1983-06-16 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Gelenkomnibus
RU2149955C1 (ru) * 1998-12-15 2000-05-27 Брянская государственная инженерно-технологическая академия Рабочее оборудование автогрейдера
WO2009121415A1 (en) * 2008-04-03 2009-10-08 Horst Schwab Gmbh Multi-purpose device for producing flat surfaces

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2494324A (en) * 1944-04-29 1950-01-10 Galion Iron Works & Mfg Co Road grader
US2883774A (en) * 1955-06-20 1959-04-28 Robert L Clifford Earth moving equipment
US3319366A (en) * 1963-08-26 1967-05-16 Atlas Motor Graders Inc Earth handling machine
US3324583A (en) * 1964-08-05 1967-06-13 Kenneth R Harris Articulated grader
US3346975A (en) * 1964-04-13 1967-10-17 Lajoye Pierre Motor-scraper
US3398984A (en) * 1966-06-02 1968-08-27 Koehring Co Motor vehicle with laterally adjustable cab

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2494324A (en) * 1944-04-29 1950-01-10 Galion Iron Works & Mfg Co Road grader
US2883774A (en) * 1955-06-20 1959-04-28 Robert L Clifford Earth moving equipment
US3319366A (en) * 1963-08-26 1967-05-16 Atlas Motor Graders Inc Earth handling machine
US3346975A (en) * 1964-04-13 1967-10-17 Lajoye Pierre Motor-scraper
US3324583A (en) * 1964-08-05 1967-06-13 Kenneth R Harris Articulated grader
US3398984A (en) * 1966-06-02 1968-08-27 Koehring Co Motor vehicle with laterally adjustable cab

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3735818A (en) * 1969-01-23 1973-05-29 Cmi Corp Oklahoma City Motor-grader implements
US3791052A (en) * 1970-01-26 1974-02-12 Lely Nv C Van Der Tractor comprising a pivotable driver seat
US3637036A (en) * 1970-06-15 1972-01-25 Cmi Corp Hydrostatic drive system
US3693722A (en) * 1970-08-11 1972-09-26 Brohigbu Ltd Fine grading device for rubber tire road grader
US3905446A (en) * 1971-07-06 1975-09-16 Western Geophysical Co Self-propelled seismic signal generator
US3884310A (en) * 1972-06-30 1975-05-20 Vyzk Ustav Zemedelskych Stroju Working aggregate, more particularly for soil cultivation
US3891003A (en) * 1974-06-18 1975-06-24 Clark Equipment Co Hydraulic manifold
DE2544525A1 (de) * 1974-10-05 1976-05-06 Coles Cranes Ltd Fahrbarer kran
US3972378A (en) * 1975-01-23 1976-08-03 Caterpillar Tractor Co. Swing lock means for an hydraulic excavator
US3999615A (en) * 1975-04-23 1976-12-28 Caterpillar Tractor Co. Motor grader with circle mounting blade and wedge control system
US4167826A (en) * 1975-08-18 1979-09-18 Feliz Jack M Self-loading dualistic earth excavator with connecting telescopic conveying and dualistic distribution means
US4015669A (en) * 1976-03-03 1977-04-05 Caterpillar Tractor Co. Circle mounting bar and circle assembly for a motor grader
US4074768A (en) * 1976-08-30 1978-02-21 Caterpillar Tractor Co. Blade support and control arrangement for a motor grader
US4279312A (en) * 1979-03-29 1981-07-21 Pyle Donald L Dual tractor road grader with double arched center frame
US4611683A (en) * 1981-07-23 1986-09-16 Hilmer Elwyn P Farm tractor
FR2551015A1 (fr) * 1983-08-25 1985-03-01 Lignones Hubert Vehicule a train avant et chassis deportables lateralement relativement
US4819738A (en) * 1985-07-29 1989-04-11 Fountain Glen L Vehicle for supporting an implement
US4768601A (en) * 1986-07-01 1988-09-06 Kabushiki Kaisha Okano Kosan Uneven ground vehicles
US4947956A (en) * 1987-10-13 1990-08-14 Clark Equipment Company Hydrostatic transmissions system for an articulated vehicle
US5190398A (en) * 1991-03-12 1993-03-02 Swisher Jr George W Apparatus for preparing a road bed
US6029431A (en) * 1994-11-23 2000-02-29 Dowler; David Vehicle
US5813228A (en) * 1995-03-29 1998-09-29 Shin Caterpillar Mitsubishi Ltd. Carrier vehicle equipped with a swing table
US6149342A (en) * 1999-03-25 2000-11-21 Cmi Corporation Anti-bridging mechanism
US6637532B2 (en) 2000-10-24 2003-10-28 Timberjack Oy Method in working machine
US7841423B2 (en) * 2002-12-18 2010-11-30 Cnh Baumaschinen Gmbh Rear chassis for a grader
US20060151187A1 (en) * 2002-12-18 2006-07-13 Damm Juergen Rear chassis for a grader
US6942041B1 (en) * 2004-06-10 2005-09-13 Deere & Company Self-propelled agricultural vehicle constructed using a standard row-crop tractor as a base
US20080169110A1 (en) * 2005-08-08 2008-07-17 Horst Schwab Gmbh Multi-Purpose Working Device
USD531647S1 (en) 2005-10-25 2006-11-07 Deere & Company Cab for a motor grader
US20080110651A1 (en) * 2006-10-31 2008-05-15 Deere & Company Full support bearing for grader circle
US7575068B2 (en) * 2006-10-31 2009-08-18 Deere & Company Full support bearing for grader circle
US8006796B1 (en) * 2007-10-18 2011-08-30 Fontaine Roger F Personal vehicle
US20220355884A1 (en) * 2021-05-06 2022-11-10 Alexey INKIREV Vehicle with a stability system that compensates for the centrifugal force and the transverse component of the inertia force when cornering
US12371120B2 (en) * 2021-05-06 2025-07-29 Alexey INKIREV Vehicle with a stability system that compensates for the centrifugal force and the transverse component of the inertia force when cornering

Also Published As

Publication number Publication date
DE1931015C3 (de) 1974-06-12
FR2028914A1 (enrdf_load_stackoverflow) 1970-10-16
DE1931015A1 (de) 1970-07-30
CH506662A (fr) 1971-04-30
GB1219037A (en) 1971-01-13
JPS4923681B1 (enrdf_load_stackoverflow) 1974-06-18
FR2028914B1 (enrdf_load_stackoverflow) 1973-03-16
DE1931015B2 (de) 1973-11-08

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