US3743033A - Rotary driven rock cutting equipment - Google Patents

Rotary driven rock cutting equipment Download PDF

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Publication number
US3743033A
US3743033A US00149154A US3743033DA US3743033A US 3743033 A US3743033 A US 3743033A US 00149154 A US00149154 A US 00149154A US 3743033D A US3743033D A US 3743033DA US 3743033 A US3743033 A US 3743033A
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US
United States
Prior art keywords
tool
frame
hammer
rock
rotor
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 - Lifetime
Application number
US00149154A
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English (en)
Inventor
R Taylor
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.)
Anglo Transvaal Consolidated Investment Co Ltd
Original Assignee
Anglo Transvaal Consolidated Investment Co Ltd
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Application filed by Anglo Transvaal Consolidated Investment Co Ltd filed Critical Anglo Transvaal Consolidated Investment Co Ltd
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Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
    • E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
    • E21D9/10—Making by using boring or cutting machines
    • E21D9/106—Making by using boring or cutting machines with percussive tools, e.g. pick-hammers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S37/00—Excavating
    • Y10S37/904—Vibration means for excavating tool

Definitions

  • the invention relates to mobile rock cutting equipment which includes a rotor carrying a series of swing hammers which are adapted to strike cutting tools positioned against a rock face and mounted in the equipment for limited axial movement.
  • the invention further uses this axial movement to determine pressure applied to the cutting tool tip and to use the pressure to operate control mechanisms acting on the rotor and motive power unit for the equipment.
  • Rotary driven rock cutting machines carrying swinging hammers tipped with cutting tips are simple and practical. However, cutting tips such as those used on the hammers are likely to shatter if the energy which they are required to transmit to the rock per blow exceeds a certain maximum for the design of tip used.
  • rock cutting equipment comprising a frame, at least a pair of rock cutting tools supported for limited axial movement in either direction against resilient buffers in the frame and spaced apart, one or more rotors carrying at least two swinging hammers adapted to strike each cutting tool and means for traversing the frame across a rock face with the tools in contact therewith.
  • the equipment would be adapted to hold the tools against the rock to be cut in such a manner that the tools would tend to cut or chip parallel grooves in the rock so spaced that the rock between the grooves would break out easily.
  • An advantage to be obtained from cutting spaced grooves is that cutting tip wear would be less per ton of rock excavated than if the tools cut grooves with no free spaced between.
  • the invention also provides for the speed of movement of the equipment along the rock face to be controlled so as to allow for an optimum rate of excavation (within the capacity of the machine) and for means for preventing the hammers from striking the tools when the tools are not pressing against the rock, and thus possibly damaging the tools or other parts of the equipment.
  • FIG. 1 shows a diagrammatic layout of one rotor carrying one series of hammers for one cutting tool
  • FIG. 2 and FIG. 3 are part sectional elevations showing the arrangement of one hammer with stopblocks on the rotor.
  • the equipment comprises a power driven rotor l carrying a series of three swinging hammers 2a,
  • the hammers carry striking faces 4 which are made of any suitably hard material and these striking faces 4 are preferably made as replaceable inserts so that the hammers may be used for longer periods than would be possible if these faces were integral with the hammers.
  • the hammers are adapted to strike a rigid cutting tool 5 which is adjustably supported in a suitable frame (see below) provided for the equipment.
  • the cutting tool carries a suitably shaped tip 6 of tungsten carbide and is held between stops 7 on the frame and a pair of resilient buffers 8 and 9 are provided on either side of a locating collar 10.
  • These buffers must be carefully designed to give the desired restraining efiect on the cutting tool and may be either metal springs or sleeves of resilient material. Hydraulic cushioning devices may also be used if this is desired.
  • the cutting tool 5 will be mounted in the desired relationship to the hammers and the rotor tool assembly will be mounted in the desired relationship to the rock to be cut. This latter position will preferably be angularly adjustable so that the direction of the blow applied by the cutting tools to the rock may be varied. It will be realized that it is desirable to angle the tool 5 to the rock face so that shear and bending forces in the tool are minimized.
  • the complete mechanism comprising at least two tools with the requisite hammers driven by one or more rotors and together with the necessary backstops and controls would be mounted in the frame and would be made to traverse approximately parallel to the surface of the rock 11 to be cut (in the direction shown by the arrow in FIG. 1) and at a distance from the rock such that the cutting tools could chip the rock at the desired rate of excavation.
  • the device producing the traversing motion which could be similar to that used currently on coal cutters or coal ploughs or tunnelling machines would be controlled by a mechanism sensitive to the loads on the cutting tools.
  • the preferred form of such mechanism is illustrated in the diagram FIG. 1 where the main frame 12 (shown dotted) presses by means of a spring 13 a pressure arm 14.
  • the pressure arm is free to slide within limits in suitable guides 15 attached to the main frame 12 in a direction parallel to the direction of movement of the tool 5 and terminates in a collar 16 into which the tool 5 is placed.
  • the collar 16 would be positioned between the collar 10 and the buffer 9.
  • a further feature of the invention intended to prevent the hammers hitting the tools when little or no resistance is offered by the rock comprises an on-off control button 19 operated by the lug 17.
  • This control button operates retractable catches which, when button 19 is pressed, protrude and engage with notches 21 in the hammers restraining them in their swing back positions.
  • the restraint of the hammers in the swing back position need not be accomplished by catches mechanically engaging in notches in the hammers but friction pads may be used. Should friction pads be used it would be preferable in order to ensure that they grip the hammer only when it is stationary or moving slowly in the swing back position to trigger the application of these pads to coincide with the moment when the hammers are stationary or nearly stationary against the back stop. Such triggering action would only take place while the button 19 was depressed and could be initiated by the hammer striking either a suitably placed trigger or striking the back stop block 22. Such additional triggering action might be preferred for the catches 20 as well as for the friction pads.
  • the complete mechanism housed in 12 should pivot about a point 23 situated ahead of the line 24 drawn at 90 to the rock face and originating in that zone of the rock face where chipping takes place. This point 23 is thus forward of the cutting tip 6 of tool 5.
  • the pivot 23 would be mounted in some form of chassis which would be able to traverse parallel to the rock face and which would be capable of containing any reaction forces transmitted from the rock face.
  • the mechanism housed in 12 would be held in position on this framework by the pivot 23 and some other device such as a shearpin which, should the control button 18 fail to stop the traverse, would shear and allow the mechanism to swing out of engagement with the rock.
  • buttons 19 should operate and the hammers should be held back from striking the tool.
  • the arrangement with the pivot 23 and the shearpin could conveniently be used to set the angle of the tools relative to the chassis.
  • the preferred design of the rotor l and swing hammers 2 is such that when the hammer strikes the cutting tool no shock load is thrown back onto the hammer pivot. It is also desirable that all the energy given up by the hammer in striking the tool is restored to the hammer by the centrifugal force applied thereto during the remaining portion of the revolution of the rotor in order to bring the hammer back into the striking positlon just at the correct time to strike the tool 5.
  • FIGS. 2 and 3 A hammer with its two resilient stop blocks and part of the rotor is shown in FIGS. 2 and 3.
  • the hammer 2 and the stop blocks 22 and 25 are mounted between backing discs 26. Each hammer will normally require two stop blocks, thus if there are three hammers in a row, as shown in the drawings, then six stop blocks will be required.
  • the stop block 22 is required to prevent excessive swing back and the stop block 25 is required to stop the hammer in the swing out position so that it will strike the cutting tool 5.
  • the stop blocks have to absorb and dissipate considerable quantities of energy and it has been found practical to construct them with fluid passages 27 leading to them from the rotor shaft 28 and other fluid passages 29 leading away through nozzles.
  • the passages would be equipped with ball valves 30 or similar one way valves to ensure a one way flow of fluid.
  • stop block consists of a cylindrical metal reinforced hollow rubber bulb similar to the commercially available Oscillith bush construction.
  • the stop block would normally be filled with fluid but when struck by the hammer, would force the fluid out through one or more nozzles at high speed.
  • the fluid In mining the fluid would preferably be water and the jets of water would play on the zone in which the rock was breaking in order that the tool 5 and tip 6 were kept cool and also to allay dust.
  • the hammer acts as a compound pendulum balanced in such a way as to limit the operational impact loading applied to the hammer pivot 3 to a minor proportion of that applied to the hammer striking tip.
  • the eccentricity of the center of gravity of the hammer relative to its pivot, the spacing of the striking tip from the hammer pivot, and the polar radius of gyration of the hammer all co-operate to result in very little shock load being transmitted to the hammer pivot.
  • the method of balancing has been proposed in an earlier patent but is redescribed hereunder.
  • the hammer 2 has its pivotal axis B spaced from the axis of rotation A of the rotor. The distance from the point C to B is equal to the polar radius of gyration of the hammer about the pivot B. The center of gravity of the hammer is indicated at D. The point relative to the rotor at which the hammer strikes the tool 5 is indicated at E.
  • the distance between the hammer axis 3 and the stops 22 and 25 should also be the same as the distance between the hammer axis and the point of impact of the hammer on the cutting tool 5.
  • the resilience of the stops ensures that this requirement is not critical.
  • the rotor l is then driven either electrically or by means of an air motor or the like to rotate the hammers 2 at high speed. These hammers strike the end of the tool repetitively to apply cutting power to the tip.
  • FIG. 1 shows diagrammatically the rotor (which in this case is rotating in a clockwise direction) with a set of three hammers.
  • Hammer 2c is in the act of striking the tool 5.
  • Hammer 2a has swung back to the stop block 22 just after striking the tool and hammer 2b has swung forward again and rests against stop block 25 ready to hit the tool 5.
  • the equipment can be made compact and powerful for use in confined areas such as underground mining or tunnelling operations.
  • control mechanisms can be operated electrically with the initiating pressures arranged to act on strain gauges or the like.
  • Rock cutting equipment comprising:
  • Rock cutting equipment comprising:
  • a control mechanism connected to said tool and said traversing means, for varying the speed of movement of said frame by said traversing means so as to limit the energy applied to said tool by said hammer in accordance with pressure applied to said tool.
  • Rock cutting equipment as claimed in claim 3 including a catch which holds said hammer inoperative and wherein said control mechanism includes means, responsive to the position of said tool relative to said frame, for controlling said catch, said hammer being held inoperative in a position in which the hammer is swung back relative to its pivot and the direction of rotation of said rotor.
  • Rock cutting equipment comprising:
  • control means including a resilient buffer for restraining rearward movement of said tool, a pressure arm connected to said buffer, said pressure arm being movable in parallel with the direction of movement of said tool, means, operative by said pressure arm, for preventing said hammer from free swinging when relatively light pressure is exerted on said tool, and means, operative by said pressure arm, for changing the speed of movement of said frame when relatively heavy pressure is exerted on said tool.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Earth Drilling (AREA)
  • Paper (AREA)
US00149154A 1970-06-04 1971-06-02 Rotary driven rock cutting equipment Expired - Lifetime US3743033A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ZA703787A ZA703787B (en) 1970-06-04 1970-06-04 Improvements in rotary driven rock cutting equipment

Publications (1)

Publication Number Publication Date
US3743033A true US3743033A (en) 1973-07-03

Family

ID=66474574

Family Applications (1)

Application Number Title Priority Date Filing Date
US00149154A Expired - Lifetime US3743033A (en) 1970-06-04 1971-06-02 Rotary driven rock cutting equipment

Country Status (9)

Country Link
US (1) US3743033A (sv)
CA (1) CA938308A (sv)
CH (1) CH525069A (sv)
DE (1) DE2127390A1 (sv)
FR (1) FR2095937A5 (sv)
GB (1) GB1332543A (sv)
NO (1) NO131359C (sv)
SE (2) SE384714B (sv)
ZA (1) ZA703787B (sv)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4079795A (en) * 1975-01-28 1978-03-21 Maschinen-Und Bohrgerate-Fabrik Alfred Wirth & Co., K.G. Method and a device for drilling with several tools in simultaneous operation
US4900093A (en) * 1986-11-10 1990-02-13 Caterpillar Inc. Impact ripper and control
US6203113B1 (en) * 1997-12-09 2001-03-20 Nick Wendel Cutting drum with percussive bits

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1283618A (en) * 1917-03-15 1918-11-05 Oliver Oscar App Excavating-machine.
US1552909A (en) * 1922-05-22 1925-09-08 Brown Harry Lewis Mining machine
US1579840A (en) * 1925-04-01 1926-04-06 Fjeldbor As Rotating hammer
US2829633A (en) * 1957-01-22 1958-04-08 Kaydon Engineering Corp Demolition device
US3397916A (en) * 1964-12-14 1968-08-20 Maruta Seiichi Rock crushing apparatus

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1283618A (en) * 1917-03-15 1918-11-05 Oliver Oscar App Excavating-machine.
US1552909A (en) * 1922-05-22 1925-09-08 Brown Harry Lewis Mining machine
US1579840A (en) * 1925-04-01 1926-04-06 Fjeldbor As Rotating hammer
US2829633A (en) * 1957-01-22 1958-04-08 Kaydon Engineering Corp Demolition device
US3397916A (en) * 1964-12-14 1968-08-20 Maruta Seiichi Rock crushing apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4079795A (en) * 1975-01-28 1978-03-21 Maschinen-Und Bohrgerate-Fabrik Alfred Wirth & Co., K.G. Method and a device for drilling with several tools in simultaneous operation
US4900093A (en) * 1986-11-10 1990-02-13 Caterpillar Inc. Impact ripper and control
US6203113B1 (en) * 1997-12-09 2001-03-20 Nick Wendel Cutting drum with percussive bits

Also Published As

Publication number Publication date
NO131359C (sv) 1975-05-14
NO131359B (sv) 1975-02-03
GB1332543A (en) 1973-10-03
DE2127390A1 (de) 1972-02-17
FR2095937A5 (sv) 1972-02-11
CA938308A (en) 1973-12-11
SE7107200L (sv) 1971-12-06
SE384714B (sv) 1976-05-17
CH525069A (de) 1972-07-15
ZA703787B (en) 1971-08-25

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