Classifications

• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F5/00—Dredgers or soil-shifting machines for special purposes
  • E02F5/30—Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil
  • E02F5/32—Rippers
  • E02F5/326—Rippers oscillating or vibrating

Definitions

• PCT/US79/00306 (81) Designated States: AT, AT (European patent), BR, CH, CH (European patent), DE, DE (European patent),
• a ripping tool (60) positioned below the earth's surface is driven by the output of a vibrating, preferably resonant, force transmitting beam (64) which has lateral dimensions smaller than those ofthe ripping tool and is positioned below the earth's surface.
• the beam is configured to have a single resonant node when restrained from vibrating at such node and is supported (66) so that the single node is above the earth's surface and restrained from vibrating.
• the output ofthe beam is enlarged in thik- kness to form a hammer.
• a protective gap is maintained by a tool stop (62) between the tool and the output ofthe force transmitting beam.
• the width ofthe tool stop is precisely controlled by shimming (63) the tool stop and/or the supports for the force transmitting beam.
• the present invention relates generally to power driving mechanisms, and more particularly to apparatus utilizing a vibratory member for driving a ripping tool into earth, rock, or other earthen material.
• Bodine Patent 3,336,082 discloses a rock ripping tooth that is integral with the lower end of a straight resonant beam.
• Cobb et al Patents 3,770,322 and 4,003,603 describe a ripping tool that is mounted for reciprocal motion; a source of oscillatory force is coupled by a non-resonant force transmitting rod to a hammer that periodically strikes the tool.
• Shatto Patent 3,633,683 discloses a pivotally mounted ripping tool that is driven by a hammer located above the earth's surface. The hammer is attached to the lower end of a straight resonant beam to which a source of vibrations is coupled.
• the requirement that the support for the force transmitting beams be above ground and the ripping tool be below ground makes difficult the design of apparatus for efficiently driving the ripping tool, because of the restraints on the component location and space occupancy.
• a reciprocally mounted ripping tool is driven by a vibrating, preferably, resonant, force transmitting member, the output of which has smaller lateral dimensions than the ripping tool.
• the force transmitting member is supported so its output lies below the earth's surface in close proximity to the cutting surface of the ripping tool.
• the lateral thickness of the ripping tool serves to divert the earthen material outwardly away from the path of the output of the force transmitting member.
• the shank of the ripping tool lying above its cutting surface has its centrally located vertical leading edge that helps cut through the earthen material and divert it outwardly away from the force transmitting member.
• a feature of the invention is a resonant force transmitting member having a single node.
• the force transmitting member is supported so that the single node is above the earth's surface while its output is located below the earth's surface in proximity to the cutting surface of the ripping tool.
• the use of a resonant force transmitting member having a single node shrinks the longitudinal space requirements for the resonant member for a given tool driving stroke.
• Another feature of the invention is a tool stop between the tool and the output of the force transmitting member that maintains a protective gap independent of the relative magnitude of the vibratory force and the tractive force. Th e tool stop limits the backward movement of the tool so it cannot reach the neutral position of the output.
• the tool stop and/or the supports for the force transmitting member are shimmed to precisely set the protective gap width
• FIG. 1 is a side elevational, partially cut away view of tool driving apparatus embodying the invention, with portions broken away;
• FIG. 1A is an enlargement of a portion of FIG. 1;
• FIG. 2 is a top plan view of the left, operative portion of the apparatus illustrated in FIG. 1;
• FIG. 3 is a fragmentary sectional view taken along line 3-3 of FIG. 1;
• FIG. 4 is a fragmentary sectional view taken along line 4-4 of FIG. 1;
• FIG. 5 is a graphical illustration of the operating characteristics of the described tool driving apparatus;
• FIG. 6 is a fragmentary sectional view of a slightly modified version of the apparatus in FIG. 3;
• FIG. 7 is a side view of an alternative version of a portion of the apparatus of FIG. 1.
• Tool driving apparatus employing a vibrating member in a fashion that such vibration of the beam or other force transmitting member will be maintained, regardless of various other forces applied during operation of the apparatus.
• a ripping tool is supported for pivotal motion from a tool frame adjustably supported at the rear of a mobile carrier in the form of a more or less standard tractor, the pivotal support being essentially transverse to the direction of motion of the tractor so that the tool, in turn, swings forwardly and rearwardly along the general direction of tractor motion.
• the tool frame through its adjustable support, can be raised or lowered, and when lowered, the ripping tool can lie several feet below the surface of the earth or other material being engaged thereby.
• a resonant member is utilized, and, more particularly, takes the form of an angle beam having a pair of legs supported in angular relationship from a pivotal support carried by the side plates of the tool frame so that one leg projects substantially vertically downward to lie adjacent the rear surface of the ripping tool whereas the other leg extends from the first leg at a divergent included angle of approximately ninety degrees and thus substantially horizontally forward between the frame plates, to mount at its extremity a sonic generator, eccentric weight oscillator or other means for energizing resonant vibration of the angle beam.
• the pivotal support therefor is at a central node position so that substantially no vibration is transmitted back to the supporting frame.
• the angle beam has lateral dimensions no greater than that of the ripping tool so that it can lie beneath the surface of the earth or other material being cut by the ripping tool without interfering with the operation.
• a short ear extends from the angle beam upwardly from its node position and lies adjacent a stop member disposed between the plates, thus to restrict the pivotal motion of the angle beam about its pivot rod in one direction. Shims, or other means, can be used to provide for adjustment of the position of shim engagement of the ear, and thus define the neutral position of the resonant angle beam, and more particularly the lower tool engaging portion thereof. In turn, the tool is restricted by a stop with adjustment shims so that it cannot swing backward into contact with the adjacent portion of the angle beam when in its defined neutral position.
• the resonant beam is able to swing to and fro in its resonant vibration when appropriately energized by the sonic generator, eccentric weight oscillator, or other means, and no possibility of clamping the beam exists.
• the ripping tool assembly 10 is mounted at the rear of a more or less conventional tractor 12 supported on mobile support means in the form of spaced endless tracks 14 for motion in a forward direction determined by a conventional steering mechanism 16 accessible to an operator seated on a driver's seat 18, with suitable adjacent controls 20 to effect not only the steering but the application of power to the endless tracks from a conventional engine 22, and also energization of hydraulic pumps 38 and 74 connected to certain hydraulic elements of the ripping tool assembly 10, as will be described hereinafter.
• a heavy plate is mounted at the rear of the tractor 12 to carry at laterally spaced and substantially parallel positions a pair of parallelogram units 26, each including a rigid upstanding leg 28 at the rear of the tractor, the tops and bottoms of which carry pivotally supported legs 30, 32.
• Legs 30, 32 extend rearwardly, to in turn pivotally support the upper and lower ends of a vertical rear leg 34 of each parallelogram unit 26 at their rear extremities.
• a double-acting hydraulic ram 36 is pivotally connected between the lower end of the rear legs 34 and the middle of the front legs 28 by a cross rod 31 and another cross rod, not shown, so as to effect a raising or lowering of the rear legs of the parallelogram unit upon application of hydraulic fluid from previously mentioned pump 38 when actuated by the machine operator.
• Rigid cross members 40, 42 extend transversely between the rear extremities of the parallelogram units 26 at both top and bottom to mount centrally brackets 44, 46 with aligned substantially vertical pivot pins 48, 50.
• Pins 48, 50 extend through aligned holes in brackets 52, 54 which are joined rigidly to side plates 56 of the ripping tool assembly 10.
• the ripping tool assembly 10 can pivot about the generally upright axis defined by the pins 48, 50 to accommodate turning of the tractor 12.
• the side plates 56 extend in spaced parallelism rearwardly from the supporting parallelogram units 26 and carry therebetween several elements, including a horizontal pivot pin 58 which supports a ripping tool 60 therefrom for pivotal motion in forward and backward directions.
• the ripping tool 60 has a substantially conventional configuration, with a long shank 60a extending substantially vertically downwardly from the supporting pivot pin 58 and a forwardly and angularly projecting tooth 60b at its lower extremity.
• a retaining pin 60d holds tooth 60b in fixed position at the end of shank 60a.
• the front surface of shank 60a converges to form a centrally located vertical leading wedge shaped edge 60c that helps to cut through the earth.
• a series of parallel tools can be suspended if desired, each having a similar configuration.
• the parallelogram unit When the parallelogram unit is lowered into an operative position, the tool 60 can extend as much as several feet into the underlying earth or other surface, as shown in FIG. 1, to provide the ripping action upon appropriate actuation of the tool driving apparatus and forward motion of the tractor, as will be described in detail hereinafter.
• the ripping tool 60 is completely free to pivot forwardly into contact with the earth or other material to be worked upon, but, in accordance with the present invention, a stop member 62 with removable shims 63 is disposed between the side plates 56 of the frame, to limit its backward motion to a particular position to be described hereinafter, which will not interfere with normal machine operation.
• the tool driving apparatus includes a resonant force transmitting member 64 in the form of an angle beam composed of solid steel or other resilient material and having a pair of straight integral legs extending in divergent paths at or near approximately ninety degrees from their point of juncture.
• the legs of angle beam 64 are preferably equal in length and the vertical end thereof is enlarged in thickness, as illustrated in FIG.
• Stop member 62 comprises a rigid bar fixed to side plates 56 of ripping tool assembly 10 between ripping tool 60 and the rest position of the vertical end of resonant member 64.
• an integral ear 76 projects outwardly from the juncture of the legs of the angle beam so as to bisect the angle between the beam legs.
• integral means that the entire resonant member 64, i.e., the legs and ear 76, is cast or forged as a single unit in a one piece construction.
• Parallel plates 65 are attached as by welding to opposite sides of ear 76. Holes in the plates 65 aligned with the juncture of the beam receive stub shafts 66 welded or otherwise fixedly secured to the plates 65.
• the shafts 66 are pivotally supported in bushings 67, which are in turn mounted in hard rubber hubs 69 supported in the side plates 56.
• the one leg of resonant angle beam 64 extends substantially vertically so the portion of enlarged thickness at its lower extremity, lies closely adjacent the rear face of the ripping tool 60 at its lower extremity, to provide, upon beam actuation, a repeated cyclical series of blows to the rear of the ripping tool, so as to drive tooth 60b repeatedly into the adjacent earth or other earthen material.
• the tool engaging portion of angle beam 64 lies below the earth's surface near tooth 60b, to provide optimum force transfer thereto. As shown in FIG. 1, the tool engaging portion of angle beam 64 thus lies below tracks 14.
• the lower end of the resonant angle beam 64 has a transverse, i.e., lateral, dimension less than that of the adjacent ripping tool 60.
• Means are. provided to energize the resonant angle beam 64 to resonant vibration, and preferably takes the form of sonic generator or eccentric weight oscillator 68, as shown in my copending application Serial No. 973,161, filed on December 26, 1978, herewith, the disclosure of which is incorporated fully herein by reference.
• Oscillator 68 is connected to the end of the horizontal leg of the resonant angle beam for actuation by a hydraulic motor 70 through a belt drive 71.
• Motor 70 is attached to one of the side plates 56, and fluidically connected to hydraulic pump 74 for actuation under control of the machine operator.
• Oscillator 68 is driven by motor 70 such that the eccentric weights rotate at or near the resonant frequency of angle beam 64, which typically is of the order of 100 cycles per second.
• this form of resonant angle beam 64 has but a single central node, namely, at the beam juncture and ear 76 along a line bisecting the angle of beam 64, when the beam is supported so it is restrained from vibrating at the juncture as shown.
• the legs of the beam resonate about this single node, with anti-nodes at the ends of the legs.
• a relatively long lever arm is provided by each of the beam legs so that a considerable stroke, particularly of the lower end of the tool actuating leg, is produced without the necessity of a resonant member or beam of excessive longitudinal dimensions.
• the cyclical reciprocating stroke with an angle beam having a leg length of no more than five feet can have an output amplitude adjacent the ripping tool of one inch or more.
• the single node and the associated node support structure are spaced far from the ends of the beam in comparison to a straight resonant beam having two nodes, as disclosed in my above referenced copending application. This is important in a ripper, where the node support must be above ground level and the ripping tool must be underground.
• the sonic generator is located in a plane displaced a substantial distance from the plane in which the tool is located, as illustrated in FIG. 1.
• the weight of oscillator 68 urges resonant angle beam 64 to pivot or rotate about pin 58 in a clockwise direction, as viewed in FIG. 1.
• a stop member 78 is attached to side plates 56 and extends therebetween adjacent to the end of ear 76 in the path of its clockwise rotation, as viewed in FIG. 1.
• Removable shims 80 are mounted on the surface of stop member 78 facing toward ear 76. Stop member 78 is shimmed so that the end of resonant angle beam 64 adjacent to tool 60 is located in a desired position, usually so the upright leg thereof is vertical when the beam is in its neutral position The neutral position of the beam is its position when at rest, i.e., when not resonating or being deflected.
• oscillator 68 When oscillator 68 is operating, it applies a reciprocating force to the end of the horizontal leg at or near the resonant frequency of angle beam 64. While resonant angle beam 64 resonates, the juncture of its legs, which is the single node, remains stationary and the end of its vertical leg reciprocates in forward and backward directions, striking tool 60 each time it moves forward in its reciprocating excursion. A changing gap is formed between the end of the vertical leg of resonant angle beam 64 and tool 60 — as the vertical leg reciprocates in a forward direction the gap tends to close and as the vertical leg reciprocates in a backward direction the gap tends to open, disregarding the continuous forward movement of the frame.
• Ripping tool 60 comprises a work tool that moves along through the soil, which comprises the work path.
• Ripping tool assembly 10 functions as a tool holder or carrier.
• Resonant angle beam 64 comprises a force transmitting member, the end of its horizontal leg comprising an input to which the reciprocating oscillator force is applied, and the end of its vertical leg comprising an output from which the reciprocating force is transferred to the tool.
• the tool advances intermittently along the work path responsive to the continuous unidirectional force applied by tractor 12 and the reciprocating force applied by oscillator 68.
• a minimum protective gap is established between the neutral position of resonant angle beam 64 and tool 60 by stop members 62 and 78.
• tractor 12 continues to advance until tool 60 abuts stop member 62.
• stop member 62 limits the backward movement of tool 60 so it cannot reach the neutral position of the beam output.
• the end of the vertical beam leg cannot become clamped by tool 60 when tool 60 encounters an immovable object, and destroy the components of the ripping tool assembly.
• the length of the minimum protective gap is adjusted from machine to machine by shims 63 on stop member 62 and shims 80 on stop member 78. Instead of shimming both stop members 62 and 78, one or the other of these stop members alone could be shimmed to establish the minimum protective gap.
• the peak-to-peak excursion of the beam output might be 2 inches
• the minimum protective gap might be 1/4 of an inch, so that the power stroke of the beam output would be 3/4 of an inch.
• the minimum protective gap should be no larger than necessary to prevent cessation of resonance when the tool encounters an immovable object, because the larger this gap, the smaller the power stroke, i.e., the portion of the beam output excursion in which it contacts the tool.
• resonant angle beam 64 If resonant angle beam 64 is driven at or near its resonant frequency without restraining the beam juncture from vibrating as disclosed herein, it has two nodes near its ends, as in the case of a straight resonant beam. Under some circumstances, it may be desirable to operate a resonant angle beam in this way, i.e., with two nodes, by supporting the beam at these two nodes, rather than at the beam juncture.
• stop members 62 and 78 protect ripping tool assembly 10
• the central horizontal line N represents the neutral position of the resonant angle beam 64, and more particularly the output thereof, and the dashed horizontal line S spaced thereabove, represents the rearmost position attainable by the ripping tool 60 when in engagement with stop member 62.
• the distance between N and S represents the minimum protective gap.
• the normal resonant swing of the output of the resonant angle beam 64 is represented by the solid line sine wave indicated at R.
• parall side plates 82 are welded to an outwardly projecting ear 84 formed at the juncture of the legs of the angle beam 85 and extend adjacent the sides of the resonant angle beam 85 beyond its inner edge to support a tube 86 in aligned holes.
• Tube 86 in turn, carries a single shaft 88, mounted by bushings 90, and rubber hubs 92 in the side plates 94 of the frame.
• Tube 86 and beam 85 are fixed relative to shaft 88, which is rotatable in bushings 90 about side plates 94 of the frame. While the tool driving apparatus has been described specifically in connection with a ripping tool, it will be apparent that it can also be applied to a cutter blade as of the type generally shown in my prior application referred to hereinabove, and also to a shovel bucket or other members of various types requiring considerable force in their operative functions. Consequently, the term "tool” is to be broadly construed.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Percussive Tools And Related Accessories (AREA)
• Portable Nailing Machines And Staplers (AREA)
• Operation Control Of Excavators (AREA)
• Vehicle Body Suspensions (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=25420714

Family Applications (1)

Country Status (5)

Cited By (4)

Citations (8)

Family Cites Families (2)

• 1979
  • 1979-05-09 AT AT79901018T patent/ATE5224T1/de not_active IP Right Cessation
  • 1979-05-09 JP JP54500900A patent/JPS6221093B2/ja not_active Expired
  • 1979-05-09 DE DE7979901018T patent/DE2966385D1/de not_active Expired
  • 1979-05-09 WO PCT/US1979/000306 patent/WO1979001066A1/en unknown
  • 1979-12-17 EP EP79901018A patent/EP0016811B1/en not_active Expired

Patent Citations (8)

Also Published As

Similar Documents

Legal Events