EP0016811B1 - Tool driving apparatus - Google Patents

Tool driving apparatus Download PDF

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Publication number
EP0016811B1
EP0016811B1 EP79901018A EP79901018A EP0016811B1 EP 0016811 B1 EP0016811 B1 EP 0016811B1 EP 79901018 A EP79901018 A EP 79901018A EP 79901018 A EP79901018 A EP 79901018A EP 0016811 B1 EP0016811 B1 EP 0016811B1
Authority
EP
European Patent Office
Prior art keywords
tool
power apparatus
angle beam
leg
angle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP79901018A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0016811A4 (en
EP0016811A1 (en
Inventor
Raymond A. Gurries
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GURRIES Co
Original Assignee
GURRIES Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to AT79901018T priority Critical patent/ATE5224T1/de
Application filed by GURRIES Co filed Critical GURRIES Co
Publication of EP0016811A1 publication Critical patent/EP0016811A1/en
Publication of EP0016811A4 publication Critical patent/EP0016811A4/en
Application granted granted Critical
Publication of EP0016811B1 publication Critical patent/EP0016811B1/en
Expired legal-status Critical Current

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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

  • the present invention relates to a power apparatus for driving a tool or other member which is pivotally-mounted comprising a vibration generator the vibrations of which are transmitted to the tool via a force-transmitting means having a first leg the end of which lies adjacent the tool within striking distance thereof, and a second leg coupled to the vibration generator, the vibration generator energizing the force transmitting means at or near its resonant frequency, and more particularly to a power apparatus for driving a ripping tool into earth, rock, or other earthen material.
  • U.S. Patent 3,336,082 discloses a rock ripping tool that is integral with the lower end of a straight resonant beam.
  • U.S. 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.
  • U.S. 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.
  • U.S. Patent 3,633,683 also discloses a power apparatus for driving a tool in which a tool in the form of a bar pivotally suspended at about one third of its length from the top and reaching with its other end beneath ground is driven from a vibration generator via a force-transmitting means.
  • the force-transmitting means consist of two legs which are substantially parallel to each other and only one of these legs is bent at the free ends thereof and joined to the vibration generator while the free end of the other leg is configured in the form of a hammer.
  • the other two ends of the two legs of the force-transmitting means are clamped together via spacing pieces with the aid of two bolts in spaced relation. Furthermore the end opposite to the end of the one leg bearing the hammer presses via a spring to the other end of the pivotally mounted bar forming the tool.
  • a ripping tool driving apparatus in which a ripping tool in the form of a U-shaped resonator bar with one leg shorter than the other has been provided.
  • This resonator bar is constructed such that it has two vibrational nodes.
  • the resonator bar is mounted to the movable carrier by two links, the ends of which are pivotally mounted to the resonator bar at the nodal points.
  • the longer leg extends below ground level while the shorter leg of the resonator bar a sonic vibration generator is coupled to transmit vibrations to the ripping tool.
  • the force-transmitting means comprises an integral one- piece beam with two straight divergent legs meeting at a juncture and configured to exhibit a single central vibrational node at that juncture when restrained thereat and anti-nodes at the ends of said angle beam, the angle beam being supported at or near its juncture.
  • the invention relates particularly to a tool which consists of a ripping tool.
  • the force transmitting member that is the force transmitting angle beam
  • the force transmitting member is supported such 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 reduces the height space requirements for the resonant member for a given tool driving stroke.
  • the vibration generator includes an eccentric weight oscillator connected to the end of the second leg of said angle beam.
  • the angle beam has an ear extending from the juncture along a plane approximately bisecting the angle formed between the two divergent legs for fixing said beam position.
  • the support for the angle beam includes a stop against which the ear of the angle beam pivots. Furthermore, shims may be provided between the ear and the stop to adjust the position of the end of the other leg of the angle beam.
  • 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.
  • the 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.
  • the force transmitting member When the tool consists of a ripping tool the force transmitting member preferably has smaller lateral dimensions than the ripping tool.
  • the force transmitting member is supported so that 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 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 outwardly away from the force transmitting member.
  • 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.
  • 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.
  • 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 by 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 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. 1, to form a hammer that increases the mass at the region of impact with ripping tool 60.
  • 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. Therefore, when earth has been dislodged by the tool, substantially no earth contact with the beam will occur. The earth is diverted outwardly by ripping tool 60 much as a mobile snow shovel pushes snow out of its path.
  • Means are provided to energize the resonant angle beam 64 to resonant vibration, and preferably takes the form of a sonic generator or eccentric weight oscillator 68.
  • 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 Hz.
  • 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 150 cm can have an output amplitude adjacent the ripping tool of 2.5 cm 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. 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. Continuous unidirectional force is applied thereto by tractor 12 in a direction parallel to the work path.
  • Oscillator 68 generates a reciprocating force, at least one component of which acts parallel to the work path.
  • 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 5 cm
  • the minimum protective gap might be 0.6 cm, so that the power stroke of the beam output would be 1.8 cm.
  • 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.
  • Fig. 5 wherein 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.
  • a slightly modified stronger mounting arrangement as shown in Fig. 6 can be utilized.
  • parallel 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.
  • 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 or 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.

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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)
  • Percussive Tools And Related Accessories (AREA)
  • Supporting Of Heads In Record-Carrier Devices (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Vehicle Body Suspensions (AREA)
EP79901018A 1978-05-12 1979-12-17 Tool driving apparatus Expired EP0016811B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79901018T ATE5224T1 (de) 1978-05-12 1979-05-09 Antriebsapparat fuer werkzeug.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US90537278A 1978-05-12 1978-05-12
US905372 1986-09-09

Publications (3)

Publication Number Publication Date
EP0016811A1 EP0016811A1 (en) 1980-10-15
EP0016811A4 EP0016811A4 (en) 1980-11-14
EP0016811B1 true EP0016811B1 (en) 1983-11-09

Family

ID=25420714

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79901018A Expired EP0016811B1 (en) 1978-05-12 1979-12-17 Tool driving apparatus

Country Status (5)

Country Link
EP (1) EP0016811B1 (pt)
JP (1) JPS6221093B2 (pt)
AT (1) ATE5224T1 (pt)
DE (1) DE2966385D1 (pt)
WO (1) WO1979001066A1 (pt)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1144210A (en) * 1980-05-02 1983-04-05 Harry J. Stormon Compact resonance drive for earth-working equipment
CN111386832B (zh) * 2020-04-23 2021-05-14 青岛农业大学 一种根茎类作物挖掘装置
CN111910497B (zh) * 2020-08-13 2021-07-16 湖北省工业建筑集团有限公司 一种市政道路损坏沥青路面切割清理设备
CN114575401B (zh) * 2022-05-07 2022-07-19 安徽送变电工程有限公司 一种方坑挖土机器人及应用该挖土机器人的挖坑方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3563316A (en) * 1968-03-20 1971-02-16 Shell Oil Co Low profile resonant plow
DE2614473A1 (de) * 1976-04-03 1977-10-13 Gmeinder & Co Gmbh Geraet zur tiefenlockerung von boeden

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3633683A (en) * 1968-01-04 1972-01-11 Bodine Albert G Nonlinear resonant vibratory work system
US3437381A (en) * 1968-02-05 1969-04-08 Albert G Bodine Vehicle mounted sonic shearing device having propulsion aiding means
US3695365A (en) * 1969-11-14 1972-10-03 Bosch Gmbh Robert Torque and impulse transmitting machine
US3770322A (en) * 1971-04-12 1973-11-06 Caterpillar Tractor Co Apparatus for fracture of material in situ with stored inertial energy
US3897975A (en) * 1971-04-12 1975-08-05 Caterpillar Tractor Co Method for fracture of material in situ with stored inertial energy
US3922017A (en) * 1973-08-23 1975-11-25 Caterpillar Tractor Co Impact material fracturing device for excavators and the like
US3857609A (en) * 1973-09-27 1974-12-31 H Felix Impact ripper shank
US4003603A (en) * 1975-12-01 1977-01-18 Caterpillar Tractor Co. Impact means for ripper

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3563316A (en) * 1968-03-20 1971-02-16 Shell Oil Co Low profile resonant plow
DE2614473A1 (de) * 1976-04-03 1977-10-13 Gmeinder & Co Gmbh Geraet zur tiefenlockerung von boeden

Also Published As

Publication number Publication date
ATE5224T1 (de) 1983-11-15
JPS55500234A (pt) 1980-04-17
WO1979001066A1 (en) 1979-12-13
EP0016811A4 (en) 1980-11-14
DE2966385D1 (en) 1983-12-15
JPS6221093B2 (pt) 1987-05-11
EP0016811A1 (en) 1980-10-15

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