US3711971A - Large capacity scraper unit construction - Google Patents

Large capacity scraper unit construction Download PDF

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Publication number
US3711971A
US3711971A US00194897A US3711971DA US3711971A US 3711971 A US3711971 A US 3711971A US 00194897 A US00194897 A US 00194897A US 3711971D A US3711971D A US 3711971DA US 3711971 A US3711971 A US 3711971A
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Prior art keywords
bowl
scraper
frame
arms
frame members
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US00194897A
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W Martin
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WE MARTIN Co
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W Martin
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Assigned to W.E. MARTIN CO. reassignment W.E. MARTIN CO. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MARTIN, ROBERT B. EXECUTOR OF THE ESTATE OF WILLIAM E. MARTIN, DEC'D.
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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
    • E02F3/64—Buckets cars, i.e. having scraper bowls
    • E02F3/6454—Towed (i.e. pulled or pushed) scrapers
    • 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
    • E02F3/64—Buckets cars, i.e. having scraper bowls
    • 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
    • E02F3/64—Buckets cars, i.e. having scraper bowls
    • E02F3/65—Component parts, e.g. drives, control devices
    • E02F3/652—Means to adjust the height of the scraper bowls, e.g. suspension means, tilt control, earth damping control

Definitions

  • ABSTRACT Eickholt AttorneyColton & Stone [57] ABSTRACT
  • the largest capacity earth moving scrapers may be loaded to their rated capacity using a single powered traction unit as opposed to the usual arrangement wherein a towing traction unit is assisted by a pusher traction unit to fully load the scraper bowl.
  • Tractive force is increased by a rigid integration of a traction unit with the scraper frame for pushing rather than towing.
  • Decreased loading resistance is made possible by mounting the scraper bowl for transverse tilting (canting) movement relative to the scraper frame whereby blade draft resistance may be selectively controlled by the operator and particularly during that portion of an excavating operation as the payload approaches rated capacity.
  • Selective bowl cant is, in turn, dependent upon a constructional configuration which will stabilize the bowl, laterally, in the various bowl cant positions and particularly against yaw forces.
  • the constructional configurations herein illustrated for stabilizing the bowl include widel spaced, overhead frame members and additional sta illzmg structure positioned outside the peripheral confines of the bowl for transferring lateral forces to the scraper frame.
  • PAIENTEDJMI 23 I975 SHEET UZUF 11 INVENTOR WILLIAM E. MARTIN ATTORNEYS.
  • PATENIEnJAnza I975 SHEET 10 [1F 11 BY wan/24.;
  • the factors determinative of available tractive force are: (1) road adhesion; (2) vehicle weight; (3) vehicle wheel base length; (4) relationship of the front and rear axles to the center of gravity; (5) coefficient of rolling resistance; and (6) the height of the center of gravity.
  • the cumulative resistance factors making up the overall resistance to forward movement of the scraper unit which must be equalled or exceeded by the applied tractive force during a scraping operation are a function of: (1) blade draft (cutting) resistance; (2) soil cohesion; (3) internal friction of the soil; (4) soil-metal friction; (5) soil-metal adhesion; (6) surcharge (weight of loaded soil); and (7) rolling resistance of the vehicle.
  • blade draft cutting
  • soil cohesion soil cohesion
  • internal friction of the soil (4) soil-metal friction; (5) soil-metal adhesion; (6) surcharge (weight of loaded soil); and (7) rolling resistance of the vehicle.
  • the foregoing factors may be broadly grouped into three categories, viz. (1) rolling resistance; (2) resistance to shear; and (3) resistance to upward movement of the soil. This latter resistance is the preponderant factor in virtually all scraping operations and increases dramatically as the scraping operation continues with the concomitant increase in surcharge.
  • the primary object of the invention is to provide a large capacity self-loading scraper which requires but a single traction unit to load its rated capacity.
  • the invention involves a combination of increasing available tractive force and reducing loading resistance.
  • the increase in tractive force is achieved by rigidly integrating the traction unit with the scraper frame for pushing rather than towing. Steering is effected by a front steerable wheel unit on the forward scraper frame.
  • the decrease in loading resistance is made possible by mounting the scraper bowl for transverse tilting- (canting) movement relative to the scraper frame.
  • the ability to cant the bowl during a scraping operation provides a selective control of blade draft resistance to decrease loading resistance which decreased loading resistance coupled with the increased tractive force available with a rear mounted traction unit permits the largest scraper bowls to be loaded to capacity.
  • This arrangement also permits a first deep cut to be made so that a subsequent cut parallel to and intersecting the first cut may be effected in the bowl level position while yet retaining decreased blade draft since one side of the bowl cutting edge will be doing little if any work during the second run. Reactivation of much larger loads, i.e., starting and stopping during a scraping operation, is also made possible by the decreased blade draft associated with bowl cant operation.
  • P, and P are the maximum tractive forces (in pounds) that can be developed without wheel slip for front and rear wheel drive vehicles, respectivey;
  • p. is the road adhesion coefficient
  • W is the vehicle weight in pounds
  • L is the vehicle wheel base in inches
  • L5 and L are the respective distances from the center of gravity to the front and rear axles in inches;
  • f is the coefficient of rolling resistance
  • H is the height, in inches, of the center of gravity from the ground.
  • the necessary lateral stability is achieved by universally suspending the bowl substantially within the lateral confines of two transversely spaced frame members which are integral with the scraper unit frame and positioning separate stabilizing members outside the lateral bowl confines which are distinct from the suspension structure.
  • Overall bowl control is then effected con jointly by the suspension structure (for raising, lowering and canting the bowl) and the stabilizing members which function alone or in combination with a portion of the suspension structure to effect a transverse interlock between the bowl and scraper frame to preclude transverse movement of the bowl substantially beyond the transverse confines of the transversely spaced frame members.
  • the imposition of lateral forces to the bowl may thus be transmitted laterally through the stabilizing structure to either the transversely spaced frame members or to another portion of the scraper frame.
  • the bowl lift arms are so related to the overhead superstructure as to insure the transmission of lateral forces imposed at that end of the bowl remote from the stabilizing structure to the widely spaced frame members. This diminishes the application of torsional stresses as would be applied to a central supporting frame member as in the aforereferenced prior art patents as well as avoiding the transmission of those forces to the various hydraulic control cylinders.
  • Loading resistance may yet be further decreased, in accordance with various embodiments of the invention, by suspending the bowl in such manner that the fore and aft disposition of the bowl floor may be maintained substantially parallel to the earth in both the level and canted scraping positions. This, of course, reduces the height to which the excavated soil must be lifted which, it will be recalled, is the primary contributing factor in determining loading resistance.
  • the bowl is towed away from the front end of the widely spaced frame members by frame or tow arms downwardly dependent from and rigid with the widely spaced frame members since this arrangement affords a somewhat better transfer of lateral forces, through the bowl lift arms, directly to the spaced frame members.
  • a pair of frame arms downwardly dependent from and rigid with the rear portions of the widely spaced frame members act as push arms through their interconnection with the rear ends of the bowl lift arms thus, again, assuring a direct transfer of lateral forces to the frame members.
  • FIG. 1 is a schematic perspective of a mobile scraper frame and bowl with interconnecting structure between the bowl and scraper frame being omitted;
  • FIG.-2 is a perspective view of a scraper unit employing a front frame towed bowl construction including bowl stabilizing brackets affixed to the bowl side walls;
  • FIG. 3 is a side elevational view of the scraper unit of FIG. 2 with a portion of the rear traction unit broken away to illustrate the bowl pitch control mechanism;
  • FIG. 4 is a top plan view of FIG. 3;
  • FIG. 5 is a sectional view taken along the line 5-5 of FIG. 3 and illustrating the scraper bowl in canted position;
  • FIG. 6 is a sectional detail view of the universal connection between a bowl lift arm and a frame two arm;
  • FIG. 7 is a fragmentary elevational view of a scraper unit similar to that of FIG. 3 but illustrating a modified pitch control mechanism
  • FIG. 8 is a view of the scraper unit of FIG. 7 illustrating a bowl position intermediate the carry and working positions;
  • FIG. 9 illustrates the bowl level working condition of the scraperunit shown in FIGS. 7 and 8'
  • FIG. 10 is an exploded perspective of the pitch control mechanism employed with the scraper unit of FIGS.7-9;
  • FIG. 11 is a fragmentary side elevational view of a scraper unit similar to that of FIG. 7 but employing a modified pitch control mechanism;
  • FIG. 12 is a fragmentary side elevational view of a scraper unit similar to that of FIGS. 7 and 11 but em-. control ploying yet a further modified pitch mechanism;
  • FIG. 13 is a fragmentary side elevational view of a front frame towed bowl wherein both the stabilizing and pitch control mechanism is positioned rearwardly of the bowl;
  • FIG. 14 is a perspective view of the stabilizing and pitch control mechanism of FIG. 13;
  • FIG. 15 is a fragmentary elevational view of a scraper unit employing a modified Watts linkage as the stabilizing mechanism
  • FIG. 16 is a sectional view taken along line 16-16 of FIG. 15;
  • FIG. 17 is an elevational view of a scraper unit em ploying a modified bowl to frame towing connection
  • FIG. 18 is a sectional view taken along line 18-18 of FIG. 17;
  • FIG. 19 is a fragmentary elevational view of a scraper unit similar to that of FIG. 17 but employing a further modified towing connection;
  • FIG. 20 is a sectional view taken along line 20-20 of FIG. 19;
  • FIG. 21 is a fragmentary elevational view of a scraper unit employing a frame pushed bowl construction
  • FIG. 22 is a sectional view taken along line 22-22 of FIG. 21;
  • FIG. 23 is a view similar to that of FIG. 21 but illustrating a modified bowl lift control mechanism
  • FIGS. 24-27 are elevational views of frame pushed bowl constructions having the stabilizing mechanism positioned forwardly of the bowl and pitch control mechanisms positioned rearwardly thereof respectively corresponding to the pitch control mechanisms of FIGS. 2, l1, 7 and 12.
  • each modification of a scraper unit 10 comprises a mobile scraper frame 12 defined by overhead superstructure 14' bridging a rear traction unit 16' and a forward steerable wheel unit 18'.
  • Overhead superstructure 14 is defined by transversely spaced, parallel frame members 20 which terminate at their forward ends in an integral connection with torque tube 22 integrally connected with goose neck 24' and rearwardly thereof in convergent portions 26' terminating in integral connections to the chassis of rear traction unit 16.
  • a scraper bowl 28 is adapted for lateral stabilization and suspension relative to the scraper frame structure for raising, lowering and canting movement relative thereto within the transverse confines of the overhead, parallel frame members 20 by structure not illustrated in FIG. 1. It is the specific structure for suspending and stabilizing the bowl relative to the mobile frame structure that distinguishes the various embodiments.
  • Power steering control of the forward wheel unit about the axis of steering trunnion 30' may be effected from a rear mounted operators station 32' in any desired manner such as by hydraulic or electric control lines traversing the mobile frame structure.
  • the power steering may be remotely powered from a prime mover 34' mounted on the rear traction unit 16 or a separate power steering source may be integrated with the forward wheel unit.
  • a forward control station may be mounted integral with the steering trunnion, if desired.
  • Bowl cant control depends upon lateral stabilization of the bowl relative to the scraper frame.
  • the relationship of the rear mounted traction unit 16' to the overhead superstructure 14' and forward steerable wheel unit 18', as depicted in FIG. 1, satisfies the first essential element of the combination while the particular transverse spacing of the overhead frame members 20', as shown in FIG. 1, to lie substan- Inasmuch as that scraper unit structure depicted in FIG. 1 is common to all of the modifications herein disclosed, the tens and units reference digits used in FIG. 1 are retained throughout the drawings.
  • FIGS. 2-6 A first scraper unit 10 embodying a towed bowl construction is illustrated in FIGS. 2-6 wherein the bowl 28 is adapted to be towed from adjacent the forward end of superstructure 14 through the intermediary of opposed bowl lift arms 36 and tow arms 38 rigidly dependent from superstructure 14 adjacent the forward terminus of overhead frame members 20.
  • Each tow arm 38 consists of spaced brackets 40 between which the lift arms 36 are mounted on self-aligning universal bearing assemblies 42 in the manner more specifically illustrated in FIG. 6.
  • Each bearing assembly 42 includes a shaft 44 rigidly bridging spaced brackets 40 and rigidly supporting, centrally thereof, the inner race 46 of bearing assembly 42.
  • each bearing assembly is rigidly secured within an opening formed in the forward end of each lift arm 36 so that each lift arm may pivot about the axis of shaft 44 and undergo canting movement relative thereto as illu's trated by the phantom line canted position in FIG. 6.
  • each universal bearing assembly 42 The degree of transverse tilt, or cant, permitted by each universal bearing assembly 42 is obviously delimited by the cross sectional height and thickness of lift arm 36, as viewed in FIG. 6, and the transverse spacing between brackets 40.
  • Bowl lift arms 36 are universally connected intermediate the ends thereof with opposed side walls 50 of bowl 28 via universal bearing assemblies 52.
  • the inner and outer races of bearing assemblies 52 are identical with the universal, self-aligning races-46, 48 illustrated in FIG. 6 and the bearing assemblies 52 differ from bearing assemblies 42 only in the cantilever stub shaft mounting illustrated in FIGS.
  • each bearing assembly 52 includes a short stub shaft 54 rigidly secured at one end thereof in an opening in bowl side wall 50.
  • stubshaft 54 extends outwardly of the bowl side wall and rigidly supports an inner race 56 identical to the inner race 46 shown in FIG. 6.
  • a coacting outer race identical to the outer race 48 of FIG. 6, is rigidly mounted in an opening in the adjacentlift arm 36.
  • the bowl may thus pivot relative to lift arms 36 about the common axis of stub shafts 54 and cant relative to the lift arms generally after the manner described in connection with the phantom line showing of FIG. 6.
  • Similar universal bearing connections 58 interconnect the rear ends of lift arms 36 with lift cylinders 60.
  • a bowl pitch control cylinder 62 universally interconnected between brackets 64, 66 on the rear of bowl 28 and the chassis of rear traction unit 16, respectively, completes the description of the bowl towing and suspension structure.
  • the bowl is stabilized laterally and particularly against yaw forces developed during cant bowl operation by a pair of stabilizing brackets 68 secured to bowl side walls 50 which coact with elements of the suspension system, just described, to effect a transverse interlock between the bowl and scraper frame to preclude lateral movement of the bowl substantially beyond the solid line position of FIG. 6.
  • the stabilizing brackets 68 are slotted over an intermediate portion of their lengths to define elongate slots 70 loosely receiving the rear ends of lift arms 36 to captivate the same against lateral movement relative to the bowl side walls within those limits imposed by the relative dimensions of the slots and lift arms.
  • the elongate length of each slot 70 is such as to permit the desired full range of bowl raising and lowering movements as controlled by lift cylinders 60.
  • each slot 70 is calculated to permit limited twisting movement, or rotation generally about the'longitudinal axes, of lift arms 36 relative to the bowl having due regard for the width and thickness of the lift arms where they traverse slots 70.
  • An exemplary dimensional relationship would permit an approximate 2W rotation of the lift arms generally about their longitudinal axes in the manner illustrated in FIG. and as permitted by the universal mountings 42, 52 and 58.
  • the spacings of the brackets 40, defining each towing arm 38 are similarly calculated to permit limited twist or rotation of bowl arms 36, generally about their longitudinal axes, relative to tow arms 38.
  • An exemplary dimensioning might involve a permissible lift arm twist of 2%" relative to the tow arms.
  • the how] could be canted as much as 5 relative to the scraper frame. This will become clear from an inspection of FIG. 5 bearing in mind that the bowl is not only universally mounted on the lift arms but the lift arms are, in turn, universally mounted relative to the scraper frame.
  • lift cylinders 60 upon opposite actuation of lift cylinders 60, as in FIG.
  • lift arms 36 are rotated generally about their longitudinal axes through an angle a relative to the scraper frame and integrally connected tow arms 38; while the bowl 28 rotates generally about a longitudinal axis, relative to lift arms 36, through an angle [3
  • the limits of angle a are defined by the spacing between tow arm brackets 40 whose engagement with opposite diagonal edges of the forward ends of lift arms 36 limits their relative twisting movement as indicated in FIGS. 5 and 6.
  • the rotation of bowl 28 relative to the lift arms (angle 3 is arrested when the opposite diagonal edges of the rear ends of lift arms 36 engage the opposed side walls of slots 70 in bracket 68.
  • the relative angular relationship of parts relates primarily to yaw stabilization when cutting with the bowl in a canted position and it is important to note that the bowl is stabilized against those yaw forces-tending to rotate the bowl about a generally vertical axis irrespective of whether the bowl is in a maximum cant position as just described and'illustrated in FIG. 5. This for the reason that further rotation of the bowl about a generally vertical axis after the play, is taken up in the loose connections defined by the interengagement between lift arms 36, slot and tow arms 38 is resisted by the interlocking engagement of the parts which defines the transverse interlock previously described.
  • yaw stabilization is at a maximum in the maximum bowl cant position since, in this position, the parts are already interlocked as illustrated in FIG. 5. Lateral stabilization against other than yaw forces when cutting in a bowl level mode takes place in a similar manner.
  • the positioning of the bowl substantially within the transverse confines of the widely spaced overhead frame members 20 of superstructure 14 has been found to be essential to provide the requisite yaw stability to resist that magnitude of forces involved in cant bowl operation of the larger size scrapers.
  • the explanation is, of course, one of outboard stabilization, i.e., a transmission of the working forces to a stable superstructure spanning the movable component (bowl) whose lateral movements are to be resisted.
  • a further reduction in loading resistance of the scraper unit 10 is made possible by selective energization of bowl pitch control cylinder 62 to control bowl movement between the solid and dotted line positions of FIG. 3 to maintain the fore and aft orientation of bowl floor 72 substantially parallel to the cut thereby decreasing the height to which the excavated material must be lifted. It is important to note that the various universal connections between the bowl and scraper frame permit the bowl floor to be so oriented even during cant bowl operation.
  • An apron 74 is conventionally mounted on bowl side walls 50 for bowl opening and closing movement about pivots 76 under the control of cylinders 78.
  • scraper unit 10 illustrated in FIGS. 2-6, embodies all three of the previously discussed factors contributing to decreased loading resistance viz. bowl cant, forward frame towing and bowl pitch control.
  • FIGS. 7-10, 11 and 12 differ from the embodiment illustrated in FIGS. 2-6 only in the details of the bowl pitch control mechanism wherein the single pitch control cylinder 62 (FIG. 3) is replaced by various control cylinder operated linkage mechanisms for performing the same function of pitch control.
  • the advantages inherring in the modified constructions employing linkage mechanisms are the permissible use of smaller pitch control cylinders and a further increase in bowl stability.
  • FIGS. 7-10 The details of a parallelogram bowl tilt control assembly 136 are seen in FIGS. 7-10 to include a generally vertically disposed main support link 138 which is universally mounted adjacent an upper end thereof via universal bearing assembly 140 between spaced mounting brackets 142 on rear traction unit 116.
  • a cross shaft 144 is universally mounted, intermediate the ends thereof, adjacent the other end of support link 138 by means of a universal, self-aligning bearing assembly 146 of the type shown in FIG. 6 and pivotally supports, at opposite ends thereof, the opposed parallelogram subassemblies 148, per se.
  • parallelogram subassemblies include generally upright links 150 journalled intermediate the lengths thereof on cross shaft 144 and pivotally mounting, at opposite ends thereof, parallel links 152, 154 which parallel linksare, in turn, pivotally connected to spaced lugs 156 on the rear of bowl 128.
  • the lower links 152 may be interconnected with links 150 by a common pivot shaft158 which pivotally mounts the cylinder end of pitch control ram 160 while the piston end thereof is interconnected with the rear of bowl 128 between spaced, subassembly mounting lugs 162; alternatively, separate control rams could be provided for each parallelogram sub-assembly.
  • a scissor link, bowl tilt control assembly 236 is illustrated in FIG. 11 as including opposed pairs of pivotally related links 238, 240 joined at respective end portions by pivot 242 and at their other ends to rear traction unit 216 and the bowl 228, respectively.
  • the mounting ,oflink 240 to traction unit 216 is by a universal bearing assembly 244.
  • Pivot 242 may be defined by a common pivot shaft which also supports the cylinder end of pitch control ram 246. Concurrent contraction of pitch control ram 246 and extension of lift cylinders 248 results in a' lowering of the bowl from the solid line carry position of FIG. 11 to the phantom line working position, as will'be apparent.
  • a toggle link pitch control assembly is illustrated in FIG. 12 which may include a single main support link 336 universally suspended from rear traction unit 316 and universally supporting, at the other end thereof, a cross shaft 338 to the opposite ends of which are pivoted bell cranks 340 which are fulcrummed on cross shaft 338 and have their opposite ends respectively connected with the bowl 328 and opposed pitch control cylinders 342.
  • Universal connections 344 between the pitch control cylinders and bell cranks completes the description of the toggle link assembly which is operative to maintain a fore and aft parallel bowl positionment in the manner indicated by the relative solid and dotted line positions of FIG. 12 while yet accommodating bowl cant by the universal mounting of hell cranks 340 relative to the rear traction unit.
  • FIGS. 13 and 14 One alternative to the use of stabilizing brackets secured to the bowl side walls for coaction with a part of the suspension system to provide the essential lateral stability is illustrated in FIGS. 13 and 14.
  • the scraper unit 410 fragmentarily shown in FIG. 13, differs from that of FIGS. 7-10 in that the stabilizing brackets 168 have been omitted and a wide, generally I-I-shaped stabilizing plate 436 has been substituted for each pair of links 152 and 154 as best seenin the perspective showing of FIG. 14.
  • the side links 438 are mounted for conjoint universal movement relative to the scraper frame by virtue of the universal pivot mountings 440, 442 interconnecting main support link 444 with the rear traction unit 416 and cross shaft 446, respectively.
  • a third exemplary construction which provides the requisite lateral stability for cant bowl operation involves a modified Watts linkage interacting between the bowl support arms and the scraper frame as illustrated by the scraper unit 510 in FIGS. 15 and 16.
  • the details of the stabilizing structure are best illustrated in FIG. 16 wherein the same is seen to comprise a radius link 5 36 mounted at the center thereof for rotation on a large stub shaft 538 rigid with rear traction unit 516.
  • Relatively massive radius arms 540, 542 are universally connected to opposite ends of radius link 536 and are parallelly extended in opposite directions to universal connections 544 with an upturned extension 546 of one bowl liftarm and a downturned extension 548 of the other lift arm.
  • this modified Watts linkage is to, in effect, provide a rigid link or transverse interlock construction bridging the rear ends of bowl lift arms 550 and, concomitantly, transmit lateral forces directly to the rear traction unit through stub shaft 538.
  • This stabilizing linkage at the rear end of the bowl coacts with the widely spaced tow arms 552 and their method of interlocking with the forward ends of lift arms 550 in the manner previously explained in connection with the embodiment of FIGS. 2-6 to provide an exceptionally stable bowl suspension.
  • the scraper unit 510 is substantially identical to that illustrated in FIGS. 2-6 wherein the modified Watts linkage replaces the function of stabilizing brackets 68 and pitch control is retained by a single cylinder 554.
  • a modified towed bowl construction is illustrated in connection with the scraper unit 610, shown in FIGS. 17 and 18.
  • Scraper unit 610 retains the basic stabilizing mechanism of the scraper unit 510 (FIGS. 15 and 16) and differs therefrom primarily in the details of the bowl to frame parallelogram towing connection 636 which includes the bowl lift cylinder 638 and in the employment of two cylinders 640 interconnected between the overhead frame and bowl for performing the functions of both bowl cant and bowl pitch control.
  • the single tow arm 642 of this embodiment converges downwardly from a large, rigid securement area centrally of superstructure torque tube 622, to terminate in an offset fork 664 between the legs of which fork is rigidly supported a cylinder mounting shaft 646.
  • the relatively massive tow arm body above fork 644 rigidly supports the outer race 648 of a universal, selfaligning bearing assembly 650 whose inner race 652 is rigid with cross shaft 654.
  • Upstanding support links 656 are rigid with the outer ends of cross shaft 654 and are spaced on either side of the convergent portions of tow arm 642 a sufficient distance to permit the same to cant, relative to the tow arm, with their rigidly interconnecting cross shaft 654 about bearing assembly 650 throughout an are equal to that of the'desired bowl cant.
  • Parallelogram links 658, 660 are pivotally interconnected between each of the support links 656, on stub shafts 662, 664 and spaced mounting brackets 666 rigidly carried by torque tube 668 interconnecting the forward ends of bowl lift arms 670 which lift arms are, in turn, rigid with the side walls of bowl 628.
  • links 658, 660 are pivoted to mounting brackets 666 via stub shafts 672 and a cross shaft 674, respectively.
  • a universal connection 676 between the cylinder end of lift cylinder 638 and shaft 646 as well as a conventional piston end connection to cross shaft 674 permits canting movement of the bowl and parallelogram towing connection 636 relative to tow arm 642 about bearing assembly 650.
  • the rear end of the bowl is stabilized by a modified Watts linkage 678 identical to that described in connection with FIGS. 15 and 16 except that the upturned and downturned arms 680, 682 to which radius arms 684 are pivoted'are integrally connected with the rear of bowl 628 rather than being a rearward extension of the lift arms.
  • the pitch/cant cylinders 640 are interconnected between the bowl and overhead frame members 620 to control both bowl pitch and tilt.
  • this embodiment is characterized by all three of the aforenumerated operating advantages, i.e., bowl cant, forward frame towing and bowl pitch control.
  • bowl lift is controlled by cylinder 638 which may be activated, alone, to control depth of cut in the manner of a conventional scraper or, in combination with conjoint extension of cylinders 640, to maintain fore and aft orientation of the bowl parallel to the ground as shown in phantom lines in FIG. 17.
  • cylinders 640 may be oppositely activated to cant the bowl and parallelogram towing connection about ball assembly 650 and the modified Watts linkage 678.
  • the scraper unit 710 (FIGS. 19 and 20) is similar to the unit 610, just described, in that the lift arms 736 are rigid with the bowl and the same is stabilized by a rear mounted modified Watts linkage 738 which linkage is, however, interconnected with upturned and downturned integral extensions 740, 742 of lift arms 736. Accordingly, as in the case of scraper unit 610, raising, lowering and canting bowl movements take place as a direct function of lift arm movement. Due to the fact that relative movement between the lift arms and bowl is precluded, the transmission of lateral forces to the widely spaced frame members 720 may be conveniently accomplished through a single universal towing connection 744 best shown in FIG. 20.
  • a large mounting post 746 including reinforcing ribs 748 terminating in exposed mounting lugs 750 is rigidly dependent from a large central area of torque tube 722.
  • the forward ends of bowl lift arms 736 are rigidly interconnected by a torque tube or brace 752 to the center of which is welded a bearing mounting lug 754 which rigidly mounts, adjacent the forward end thereof, the outer race 756 of a universal bearing assembly 758.
  • the inner race of the bearing is secured to a shaft 760 bridging mounting lugs 750.
  • the bowl 728 is thus towed through a single large central connection with brace 752 rigidly interconnecting the lift arms.
  • the bowl may be lowered from the solid line carry position of FIG. 19 to a lower working position by extension of lift cylinders 762 to pivot.
  • the lift arms and integrally connected bowl downwardly about a generally horizontal axis passing through bearing assembly 758.
  • Opposite actuation of the lift cylinders raises one arm while lowering the other to cant the bowl rigidly carried thereby; the universal pivot connection 758 and modified Watts linkage 738' accommodating such movement in the manner previously described.
  • the frame pushed scraper bowl 828 of scraper unit 810 (FIGS. 21 and 22) is pushed directly by rear traction unit 816 adjacent the lower rear edge of ejector section 836 through a universal bearing assembly 838 which, also, supports the rear end of the bowl for canting movement.
  • the forward end of the bowl is supported from superstructure torque tube 822 via a mounting post 840, modified Watts linkage 842, identical with that previously described, and bowl lift arms 844 rigid with bowl side walls 846.
  • Lift cylinders 848 are universally interconnected between overhead frame members 820 and the forward ends of lift arms 844. It will be apparent that simultaneous extension of lift cylinders 848 will lower the forward end of the bowl from the carry position of FIG. 21 to a lower working position while opposite actuation of the lift cylinders will cant the bowl generally about a longitudinal axis extending between bearing assembly 838 and main pivot shaft 850 of linkage 842.
  • FIG. 23 is illustrated an alternate arrangement for controlling lift arms 936 wherein lift cylinders 938 act through bell cranks 940 and links 942 interconnected between the bell cranks and lift arms.
  • the connections 944, 946 between the bell cranks and lift arms are, of course, universal connections to permit the required bowl cant.
  • FIGS. 24-27 are exemplary wherein the primary distinctions reside in alternate pitch control arrangements.
  • the scraper unit 1010 shown in FIGS. 24 includes a pair of lift arms 1036 universally interconnected with bowl side walls 1038 as illustrated in connection with FIG. 5 and whose rear ends are universally connected with push arms 1040 downwardly dependent from frame members 1020 by universal bearing assemblies 1042.
  • the forward ends of lift arms 1036 are interconnected with superstructure torque tube 1022 in a manner identical to that shown in FIG. 21 and lift cylinders' 1044 are universally interconnected between overhead frame members 1020 and the forward ends of the lift arms.
  • Bowl pitch is controlled by a single pitch control cylinder 1046 universally interconnected between mounting ears 1048 on the rear of bowl 1028 and overhead superstructure 1014.
  • the scraper unit 1110 shown in FIG. 25 is identical to that of FIG. 24 except for the bowl pitch control mechanism which includes scissor link pairs 1136, 1138 interconnected between opposite rear sides of the bowl 1128 and appropriate mounting lugs 1140 on rear traction unit 1116. Adjacent ends of links 1136, 1138 are interconnected by a cross shaft 1142 which may be universally mounted relative to scraper unit 1110 in a manner identical to the mounting of cross shaft 144 in FIG. 10 so that the scissor links, pivotally interconnected by cross shaft 1142 on either side of bowl 1128, may follow canting movement of the bowl as induced by opposite actuation of lift cylinders 1144.
  • the bowl pitch control mechanism which includes scissor link pairs 1136, 1138 interconnected between opposite rear sides of the bowl 1128 and appropriate mounting lugs 1140 on rear traction unit 1116. Adjacent ends of links 1136, 1138 are interconnected by a cross shaft 1142 which may be universally mounted relative to scraper unit 1110 in a manner identical to
  • a pair of pitch control cylinders 1146 may be universally interconnected between the sides of bowl ejector section 1148 and cross shaft 1142 or, alternatively, a single pitch control cylinder may interconnect the rear of bowl 1128 and cross shaft 1142. Retraction of pitch cylinders 1146 in conjunction with extension of lift cylinders 1144 results in a lowering of both the front and rear ends of bowl 1128 from the carry position of FIG. 25 to an excavating position wherein the fore and aft orientation of the bowl is substantially parallel to the cut. Bowl cant is permitted by the universal suspension of cross shaft 1142 from the rear traction unit and the forward modified Watts linkage 1150.
  • Scraper unit 1210 shown in flG. 26 is identical, in construction and operation, to that of FIG. 25 except that a parallelogram pitch control linkage 1236 is substituted for the scissor pitch control linkage of FIG. 25.
  • the construction and operation of the parallelogram pitch control linkage is like that illustrated and described in connection with FIGS. 7-10.
  • Scraper unit 1310 is, also, identical in construction and operation to scraper l 1 10 of FIG. 25 except for the substitution of a toggle link pitch control mechanism 1336 which is like that illustrated and described in connection with FIG. 12.
  • a self loading scraper having a mobile scraper frame defined by overhead superstructure bridging a rear traction unit and a forward wheel unit; said superstructure including transversely spaced frame members rigid with said rear traction unit; a scraper bowl positioned substantially within the transverse confines of said spaced frame members; bowl control means interconnected between said scraper bowl and said said mobile scraper frame for interlocking said bowl and scraper frame against transverse movement of said bowl substantially beyond the transverse confines of said spaced frame members, and for'raising, lowering and canting said bowl relative to said scraper frame; said bowl control means including suspension means suspending said how] substantially within the transverse confines of said spaced frame members for effecting said raising, lowering and canting movements; and said bowl control means further including stabilizing means, in addition to said suspension means, positioned wholly exteriorly of the peripheral confines of said bowl for transmitting lateral working forces between said bowl and said spaced frame members and rigidly interconnected traction unit.
  • suspension means includes bowl lift arms mounted on opposite sides of said bowl and power lift means interconnected between said lift arms and overhead superstructure.
  • the scraper of claim 1 including power operated pitch control means interconnected between said scraper frame and bowl for selectively controlling bowl pitch.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Soil Working Implements (AREA)
  • Carriers, Traveling Bodies, And Overhead Traveling Cranes (AREA)
  • Handcart (AREA)
  • Earth Drilling (AREA)
US00194897A 1971-11-02 1971-11-02 Large capacity scraper unit construction Expired - Lifetime US3711971A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US19489771A 1971-11-02 1971-11-02

Publications (1)

Publication Number Publication Date
US3711971A true US3711971A (en) 1973-01-23

Family

ID=22719311

Family Applications (1)

Application Number Title Priority Date Filing Date
US00194897A Expired - Lifetime US3711971A (en) 1971-11-02 1971-11-02 Large capacity scraper unit construction

Country Status (9)

Country Link
US (1) US3711971A (ja)
JP (1) JPS5211125B2 (ja)
AR (1) AR193424A1 (ja)
BR (1) BR7204681D0 (ja)
CA (1) CA973129A (ja)
DE (1) DE2230166C2 (ja)
GB (1) GB1380332A (ja)
IT (1) IT955333B (ja)
SU (1) SU613728A3 (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5621643A (en) * 1991-04-12 1997-04-15 Komatsu Ltd. Dozing system for bulldozers
US6276077B1 (en) * 1999-08-18 2001-08-21 Jhc Holding Company Tiltable bucket, wheel tractor scraper
US20080060232A1 (en) * 2006-09-08 2008-03-13 Ashland Industries Management Group Skid steer scraper
US10836425B2 (en) * 2017-11-27 2020-11-17 Honda Motor Co., Ltd. Wheel steering system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2004100772A4 (en) * 2004-09-15 2004-10-28 Graham Earnest Calcott Walsh Device for Levelling Ground

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US2111134A (en) * 1934-04-04 1938-03-15 Gar Wood Ind Inc Scraper
US2304527A (en) * 1939-08-16 1942-12-08 Euclid Road Machinery Company Scraper
US3138883A (en) * 1962-08-28 1964-06-30 Martin William E Flexibly suspended scraper receptacle
US3149429A (en) * 1962-11-27 1964-09-22 Martin Co Road scraper with earth moving device connected thereto by articulate link means
US3302316A (en) * 1964-01-30 1967-02-07 William E Martin Scraper bowl for earth moving equipment
US3418735A (en) * 1965-10-18 1968-12-31 Martin Co Load ejecting wall mechanism for scraper bowl equipment
DE1290493B (de) * 1963-06-21 1969-03-06 Rheinstahl Henschel Ag Schuerfkuebelfahrzeug
US3435547A (en) * 1966-12-15 1969-04-01 William E Martin Self-contained scraper bowl assembly adapted for attachment with mobile vehicle
US3443329A (en) * 1965-09-08 1969-05-13 William E Martin Control and nudging means for earth working devices
US3450418A (en) * 1966-11-21 1969-06-17 Caterpillar Tractor Co Means to provide temporary firm support for a resiliently supported earthmoving machine
US3452462A (en) * 1965-10-13 1969-07-01 William E Martin Operating mechanism for scraper bowl material ejector
US3460279A (en) * 1966-03-07 1969-08-12 William E Martin Earth working scraper attachment for farm tractors
US3501856A (en) * 1968-01-18 1970-03-24 William E Martin Self-contained scraper attachment assembly for farm tractor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1020935B (ja) *
US3230646A (en) * 1963-07-11 1966-01-25 Robert G Letourneau Multiple telescoping bucket type excavator

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2111134A (en) * 1934-04-04 1938-03-15 Gar Wood Ind Inc Scraper
US2304527A (en) * 1939-08-16 1942-12-08 Euclid Road Machinery Company Scraper
US3138883A (en) * 1962-08-28 1964-06-30 Martin William E Flexibly suspended scraper receptacle
US3149429A (en) * 1962-11-27 1964-09-22 Martin Co Road scraper with earth moving device connected thereto by articulate link means
DE1290493B (de) * 1963-06-21 1969-03-06 Rheinstahl Henschel Ag Schuerfkuebelfahrzeug
US3302316A (en) * 1964-01-30 1967-02-07 William E Martin Scraper bowl for earth moving equipment
US3443329A (en) * 1965-09-08 1969-05-13 William E Martin Control and nudging means for earth working devices
US3452462A (en) * 1965-10-13 1969-07-01 William E Martin Operating mechanism for scraper bowl material ejector
US3418735A (en) * 1965-10-18 1968-12-31 Martin Co Load ejecting wall mechanism for scraper bowl equipment
US3460279A (en) * 1966-03-07 1969-08-12 William E Martin Earth working scraper attachment for farm tractors
US3450418A (en) * 1966-11-21 1969-06-17 Caterpillar Tractor Co Means to provide temporary firm support for a resiliently supported earthmoving machine
US3435547A (en) * 1966-12-15 1969-04-01 William E Martin Self-contained scraper bowl assembly adapted for attachment with mobile vehicle
US3501856A (en) * 1968-01-18 1970-03-24 William E Martin Self-contained scraper attachment assembly for farm tractor

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5621643A (en) * 1991-04-12 1997-04-15 Komatsu Ltd. Dozing system for bulldozers
US5694317A (en) * 1991-04-12 1997-12-02 Komatsu, Ltd. Blade control system for a bulldozer
US5699248A (en) * 1991-04-12 1997-12-16 Komatsu Ltd. Running slip control system for a bulldozer
US5819190A (en) * 1991-04-12 1998-10-06 Komatsu Ltd. Ground leveling control system for a bulldozer
US6276077B1 (en) * 1999-08-18 2001-08-21 Jhc Holding Company Tiltable bucket, wheel tractor scraper
US20080060232A1 (en) * 2006-09-08 2008-03-13 Ashland Industries Management Group Skid steer scraper
US7454850B2 (en) * 2006-09-08 2008-11-25 Ashland Industries Management Group Skid steer scraper
US10836425B2 (en) * 2017-11-27 2020-11-17 Honda Motor Co., Ltd. Wheel steering system

Also Published As

Publication number Publication date
BR7204681D0 (pt) 1973-09-13
DE2230166A1 (de) 1973-05-10
SU613728A3 (ru) 1978-06-30
JPS4853503A (ja) 1973-07-27
CA973129A (en) 1975-08-19
AR193424A1 (es) 1973-04-23
GB1380332A (en) 1975-01-15
IT955333B (it) 1973-09-29
DE2230166C2 (de) 1981-12-24
JPS5211125B2 (ja) 1977-03-29

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