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WO1997016606A1 - Procede et appareil pour excaver dans un materiau solide - Google Patents

Procede et appareil pour excaver dans un materiau solide Download PDF

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Publication number
WO1997016606A1
WO1997016606A1 PCT/AU1996/000687 AU9600687W WO9716606A1 WO 1997016606 A1 WO1997016606 A1 WO 1997016606A1 AU 9600687 W AU9600687 W AU 9600687W WO 9716606 A1 WO9716606 A1 WO 9716606A1
Authority
WO
WIPO (PCT)
Prior art keywords
cutting
wheel
wheels
breaking
solid material
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.)
Ceased
Application number
PCT/AU1996/000687
Other languages
English (en)
Inventor
Christopher Alan Bunker
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.)
University of Queensland UQ
Original Assignee
University of Queensland UQ
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
Application filed by University of Queensland UQ filed Critical University of Queensland UQ
Priority to AU72687/96A priority Critical patent/AU7268796A/en
Publication of WO1997016606A1 publication Critical patent/WO1997016606A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/28—Small metalwork for digging elements, e.g. teeth scraper bits
    • E02F9/2866—Small metalwork for digging elements, e.g. teeth scraper bits for rotating digging elements
    • 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
    • E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
    • E02F3/183—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with digging unit shiftable relative to the frame
    • 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
    • E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
    • E02F3/185—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with digging unit mounted in a plane which is inclined to the direction of travel; with tools digging laterally with respect to the frame
    • 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
    • E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
    • E02F3/20—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels
    • 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
    • E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
    • E02F3/22—Component parts
    • E02F3/24—Digging wheels; Digging elements of wheels; Drives for wheels
    • E02F3/241—Digging wheels; Digging elements of wheels; Drives for wheels digging wheels
    • 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
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/963—Arrangements on backhoes for alternate use of different tools
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C25/00—Cutting machines, i.e. for making slits approximately parallel or perpendicular to the seam
    • E21C25/16—Machines slitting solely by one or more rotating saws, cutting discs, or wheels

Definitions

  • This invention relates to methods and apparatus for cutting solid material or cutting and breaking solid material and particularly relates to an apparatus which can be mounted to a movable vehicle such as an excavator, bulldozer, tractor and the like and which can be used to cut into ground surfaces.
  • a movable vehicle such as an excavator, bulldozer, tractor and the like and which can be used to cut into ground surfaces.
  • ripper tine This tine is formed from steel and allows penetration, fragmentation and loosening of material which cannot be dug by the bucket alone
  • the tine can penetrate weak rock and can be used to pry embedded or jointed material so as to loosen it for subsequent removal by the bucket
  • a disadvantage with the ripper tine is that it is not suitable for anything more than weak rock material
  • rock hammer For hard rock, a rock hammer is provided The rock hammers are extremely common and are used to break up even the strongest type of rock, reinforced concrete staictures and the like. A rock hammer is however extremely noisy and has excessive vibration Rock hammers have a low productivity when used with softer solid material
  • a method of cutting an excavation in solid material comprising cutting the excavation in the material with two cutting wheels supported by support means wherein said cutting wheels are arranged relative to each other whereby reaction forces from the cutting ofthe excavation result in a required net force on the support means.
  • a method of cutting an excavation in solid material comprising: cutting the excavation in the material with two cutting wheels supported by support means; arranging said cutting wheels relative to each other whereby reaction forces from the cutting of the excavation result in a required net force on the support means.
  • the cutting wheels are arranged relative to each other prior to and/or during the cutting. It is especially advantageous to arrange the cutting wheels during the cutting.
  • an apparatus for cutting an excavation in solid material comprising two cutting wheels for cutting an excavation in the material; support means supporting the cutting wheels; and arrangement means operatively associated with the cutting wheels to arrange the cutting wheels relative to each other whereby reaction forces from cutting the excavation in the solid material result in a required net force on the support means lt is particularly advantageous for the support means to support the cutting wheels whereby at least one ofthe cutting wheels is movable relative to the support means
  • the apparatus enables the cutting wheels to be arranged relative to each other prior to and/or during the cutting lt is especially advantageous to arrange the cutting wheels during the cutting.
  • the invention resides in an apparatus for cutting an excavation in solid material the apparatus comprising at least two spaced apart cutting assemblies, each assembly having a shaft and a cutting wheel attached to one end of the shaft, the shafts being generally parallel with respect to each other; a support frame supporting the cutting assemblies, optionally attachment means attached to the support frame which is capable of attaching the support frame to a vehicle; and arrangement means operatively associated with the cutting assemblies to arrange the cutting wheels relative to each other whereby reaction forces from cutting the excavation in the solid material result in a required net force on the support frame
  • the positions ofthe cutting wheels are adjustable relative to one another
  • two cutting wheels may be arranged relative to each other whereby the position of one of the cutting wheels is side by side with the other cutting wheel.
  • the two wheels are so arranged because in this arrangement when cutting in uniform solid (e.g. uniform rock) a near zero net sidewards force on an excavator arm supporting the support frame supporting the wheels (for example) will be typically produced.
  • two cutting wheels may be arranged relative to each other whereby the position of one of the cutting wheels is at a trailing position relative to the other cutting wheel
  • the two wheels are so arranged (one wheel in a trailing position) because in this arrangement when cutting in uniform solid material (e.g.
  • a non-zero sideways force on an excavator arm supporting the support frame supporting the wheels will be typically produced which may be used for steering purposes.
  • the two wheels are so arranged (one wheel in a trailing position) because in this arrangement when cutting in non uniform solid material (e.g non uniform rock) a near-zero sideways force on an excavator arm supporting the support frame supporting the wheels (for example) will be typically produced so as to enable a substantially straight cut.
  • the position of a wheel in a trailing position may be adjusted as required so as to produce a non-zero steering force on an excavator arm supporting the support frame supporting the wheels (for example) so as to enable steering while the wheels are cutting in non uniform solid material (e.g. non uniform rock).
  • the cutting wheel at the trailing position is typically arranged so that its path at least partially intersects the path taken by the other cutting wheel so that the excavation (e.g. groove) cut by the cutting wheel in the trailing position at least partially intersects the excavation (e g groove) cut by the other cutting wheel
  • the depth of the excavation (e.g. groove) cut by the cutting wheel in the trailing position may be substantially the same as or different from the depth of the excavation (e g groove) cut by the other cutting wheel.
  • the depth of the excavation (e g groove) cut by the cutting wheel in the trailing position is substantially the same as the depth of the excavation (e.g groove) cut by the other cutting wheel, enabling, for instance, excavation to a defined plane
  • the usual arrangement for the cutting wheels is side-by-side since non-uniform rock or the need for steering or the need for both simultaneously will be common but not usual
  • the cutting wheel at the trailing position may be arranged whereby its path does not intersect the path taken by the other cutting wheel so that the excavation (e g groove) cut by the cutting wheel in the trailing position does not intersect the excavation (e.g groove) cut by the other cutting wheel
  • the depth of the excavation (e g groove) cut by the cutting wheel in the trailing position may be substantially the same as or different from the depth of the excavation (e g groove) cut by the other cutting wheel It is particularly advantageous that the depth of the excavation (e.g groove) cut by the cutting wheel in the trailing position is substantially the same as the depth of the excavation (e g groove) cut by the other cutting wheel
  • the two excavations (e g grooves) may be close together whereby the solid material between the two excavations (e g grooves) breaks off as a result of the cutting action of the trailing cutting wheel or alternatively, the two excavations (e g grooves) may be spaced apart a sufficient distance whereby the solid material between the two excavations (e g.
  • the cutting wheels may be arranged relative to one another so that when cutting a solid material (e.g.
  • Excavations may be arranged so that later excavations (e.g grooves) are cut deeper than earlier excavations (e g grooves)
  • the later cut excavations may be parallel or non parallel with the earlier excavations (e g grooves). If parallel they may be displaced (e g laterally or sideways) relative to the earlier excavations (e.g. grooves) or alternatively, they may not be displaced (e g laterally or sideways) relative to the earlier excavations (e g. grooves)
  • a method of excavating solid material in bulk comprising
  • a method of excavating a solid material by a cutting and breaking action comprising excavating the material by a cutting and breaking action with two cutting and breaking wheels supported by support means wherein said cutting and breaking wheels are arranged relative to each other whereby reaction forces from the excavating result in a required net force on the support means
  • a method of excavating a solid material in bulk by a cutting and breaking action comprising
  • a method of excavating a solid material in bulk by a cutting and breaking action comprising (i) excavating a portion of the material by a cutting and breaking action with two cutting and breaking wheels supported by support means,
  • the cutting and breaking wheels are arranged relative to each other prior to and/or during the cutting It is especially advantageous to arrange the cutting and breaking wheels during the cutting
  • an apparatus for excavating a solid material by a cutting and breaking action comprising two cutting and breaking wheels for excavating the material by a cutting and breaking action, support means supporting the cutting and breaking wheels, and arrangement means operatively associated with the cutting and breaking wheels to arrange the cutting and breaking wheels relative to each other whereby reaction forces from the excavating the solid material result in a required net force on the support means It is particularly advantageous for the support means to support the cutting and breaking wheels whereby at least one of the cutting and breaking wheels is movable relative to the support means.
  • the apparatus enables the cutting and breaking wheels to be arranged relative to each other prior to and/or during the cutting and breaking lt is especially advantageous to arrange the cutting and breaking wheels during the cutting and breaking
  • the arrangement means may also be at least part of the support means
  • the invention resides in an apparatus for excavating solid material by a cutting and breaking action
  • the apparatus comprising at least two spaced apart cutting and breaking assemblies, each assembly having a shaft and a cutting and breaking wheel attached to one end of the shaft, the shafts being generally parallel with respect to each other, a support frame assembly supporting the cutting and breaking assemblies, optionally attachment means to attach the support frame assembly to a vehicle; and arrangement means operatively associated with the cutting and breaking assemblies to arrange the cutting and breaking wheels relative to each other whereby reaction forces from excavating the solid material result in a required net force on the support frame assembly
  • the step of excavating comprises forming one or more grooves, one or more channels, one or more slits, one or more furrows, one or more gouges, or one or more gutters, or a combination thereof
  • one or two of grooves, channels, slits, furrows, gouges, gutters, or a combination thereof is/are formed in the solid material
  • a plurality of grooves, channels, slits, furrows, gouges, gutters, or a combination thereof may be formed in the solid material and/or the grooves, channels, slits, furrows, gouges, gutters, or a combination thereof, formed by the first excavation/step of excavating may be deepened and/or widened and/or lengthened and/or crossed with the subsequent steps of excavating
  • the two cutting and breaking wheels are spaced apart from one another
  • the cutting and breaking wheels are arranged relative to each other whereby the position of one of the cutting and breaking wheels is at a trailing position relative to the other cutting and breaking wheel
  • the cutting and breaking wheel at the trailing position is arranged so that its path at least partially intersects the path taken by the other cutting and breaking wheel so that the excavation (e g groove) cut by the cutting and breaking wheel in the trailing position at least partially intersects the excavation (e g groove) cut by the other cutting and breaking wheel
  • the depth of the excavation (e g groove) cut by the cutting and breaking wheel in the trailing position may be substantially the same as or different from the depth of the excavation (e.g groove) cut by the other cutting and breaking wheel It is particularly advantageous that the depth of the excavation (e g groove) cut by the cutting and breaking wheel in the trailing position is substantially the same as the depth of the excavation (e g X groove) cut by the other cutting and breaking wheel, enabling, for instance, excavation to a defined plane
  • the cutting and breaking wheel at the trailing position is arranged whereby its path does not intersect the path taken by the other cutting and breaking wheel so that the excavation (e g groove) cut by the cutting and breaking wheel in the trailing position does not intersect the excavation (e g groove) cut by the other cutting wheel
  • the depth of the excavation (e g groove) cut by the cutting and breaking wheel in the trailing position may be substantially the same as or different from the depth of the excavation (e g groove) cut by the other cutting wheel It is particularly advantageous that the depth of the excavation (e g groove) cut by the cutting and breaking wheel in the ti ailing position is substantially the same as the depth of the excavation (e g groove) cut by the othei cutting wheel
  • the two excavations (e g two grooves) may be close together whereby the solid material between the two excavations (e g two grooves) breaks off as a result of the cutting action of the trailing cutting and breaking wheel or alternatively, the two excavations (e g two grooves) may be spaced apart a sufficient
  • the effective distance between the peripheries of the two cutting wheels or the two cutting and breaking wheels is generally small enough that the solid material (e g rock) web between the two wheels will break free when the wheels are in operation cutting/breaking the material
  • the effective distance required to attain this will depend on the material being cut, the stronger and/or less fractured the material the narrower the effective distance
  • the effective distance is 1 -200mm, more typically - ] 00mm, even more typically 30-75mm, yet even more typically 40 - 60mm, more typically 45 - 55mm and advantageously about 50mm
  • one or a plurality of excavations e g grooves (e g 2- 10,000) which may be overlapping or non overlapping, adiacent or non adjacent, parallel or non parallel, are formed in the solid material by repeating a method of the invention a plurality of times in order to excavate the required amount of material from the solid material
  • the apparatus and methods of the invention have many applications such as in excavations for roadworks, foundations, carpai k excavations, foi mmg trenches including trenches for pipe laying, foundations, and may be used for trimming purposes including trimming tunnels, and the like and in mining for excavating solid material such as coal, or rock including asphalt, shale, limestone, metallic ores including some iron ores, gold ores, nickel ores, rock salt, potash, talc, calcspar, fluorspar, gypsum, borax, sandstone, and the like
  • the type of material suitable for excavation is dependent on the strength and fabric of the material and the precise nature ofthe cutting pick or drag tool
  • An apparatus of the invention is typically attached to a vehicle such as an excavator, bulldozer, tractor or the like
  • the apparatus of the invention may include a drive motor to d ⁇ ve each cutting wheel or cutting and breaking wheel
  • the drive motor may be independently powered or may be powered from the vehicle
  • the drive motor may comprise a fluid motor such as an hydraulic or pneumatic motor, and can also include an electric motor, diesel motor, petrol motor and the like It is preferred that the drive motor is an hydraulic drive motor powered by the vehicle
  • Each cutting wheel or cutting and breaking wheel is typically coupled to a drive shaft (integrally or non integrally)
  • the drive motor may be directly or indirectly attached to the shaft to rotate the shaft and therefore the cutting wheel or the cutting and breaking wheel
  • the cutting wheel or the cutting and breaking wheel may be coupled to or integral with the lower end or working end of a shaft
  • the wheel may extend through a plane substantially perpendicular to the longitudinal axis of the shaft
  • the cutting wheel or the cutting and breaking wheel may be provided with cutting tools such as peripheral teeth or picks which can be formed from hard material such as tungsten-carbide
  • the teeth or picks may be adjustable and/or replaceable
  • the cutting and breaking wheel and/oi coupled shaft includes breaking means, typically a bursting wheel or wedge Typically the wheel or wedge are on one or both faces of the cutting wheel.
  • the support means supports the cutting wheels or the cutting and breaking wheels to enable them to engage the solid material at a desired position or angle
  • the support means includes two shafts the lower end or working end of each shaft being coupled to or integral with a cutting wheel or the cutting and breaking wheel to form a cutting assembly, and a support frame assembly
  • the support frame assembly supports the cutting assemblies to allow the cutting wheels or the cutting and breaking wheels to engage the solid material at a desired position or angle
  • the support frame assembly may include an upper attachment area to support an upper part of a said cutting assembly, and a lower attachment area to support a lower in part ofthe cutting assembly.
  • the lower part may support the cutting assembly for movement in two dimensions and in a preferred form this can be achieved by a ball and socket arrangement.
  • the upper attachment area preferably allows movement in one dimension only.
  • the arrangement means may be capable of: (a) passively arranging the cutting wheel or cutting and breaking wheels relative to each other whereby reaction forces from excavating (e.g. forming at least one groove) in the solid material result in a required net force on the support frame assembly (i.e. it may be adjustable prior to commencing cutting wheel or cutting and breaking the solid material); or (b) actively arranging the cutting wheel or cutting and breaking wheels relative to each other whereby reaction forces from excavating (e.g forming at least one groove) in the solid material result in a required net force on the support frame assembly (i.e. it may actively arrange or dynamically arrange the cutting wheel or cutting and breaking wheels during the cutting wheel or cutting and breaking of the solid material).
  • the arrangement means is capable of (b).
  • the arrangement means may comprise a passive or an active linkage arrangement, typically an active parallelogram linkage arrangement.
  • the linkage arrangement may form part of the support frame assembly and is used to adjust, typically actively, the position of the cutting assemblies and more particularly the positions of the two cutting wheels or the cutting and breaking wheels relative to each other whereby reaction forces from excavating (e.g. forming at least one groove) in the solid material result in a required net force on the support means.
  • the linkage arrangement may include a forward link member mounted more towards the vehicle and a rear link member mounted behind the forward link member.
  • the link members are preferably rotatable about a vertical axis and about a position mid-way between the ends of each link member Both link members may extend in the same plane.
  • a cutting assembly comprising a rotatable shaft and a cutting wheel coupled to one end thereof, or a cutting and breaking assembly comprising a rotatable shaft and a cutting and breaking wheel coupled to one end thereof, may be attached to both the forward and the rear link member, and these link members may comprise the upper attachment area as described above. Pivoting movement of the link members causes the cutting assemblies to be moved relative to each other such that one cutting assembly can adopt a leading or preferential cutting position relative to the other cutting assembly
  • the rotatable shafts are parallel to one another and remain parallel to one another during and after the pivoting movement of the link members.
  • the distance between two parallel planes perpendicular to the rotatable shafts and passing through each of the wheels varies in a way which keeps the vertical separation of the wheel in planes parallel to the surface being excavated constant and substantially zero even during orientation of one wheel relative to another, lt is to keep the distance between the planes passing through the centres of the cutting wheels and parallel to the ground (ie. at an angle 'alpha' to the plane of the cutting wheels) that the parallelogram movement has been devised.
  • the arrangement means forms part of the support frame assembly and is an parallelogram linkage arrangement which is capable of adjusting the positions of the two wheels relative to each other whereby reaction forces from excavating in the solid material result in a required net force on the support means and an excavator is coupled to the support means and the linkage arrangement via an excavator arm whereby in use in cutting an excavation with the two wheels the net force on the excavator arm is adjustable via the linkage arrangement so as to permit an operator to steer the apparatus in the required direction and to cut the required excavation in the solid material.
  • the arrangement means forms part of the support frame assembly and is an parallelogram linkage arrangement which is capable of adjusting the positions of the two wheels relative to each other whereby reaction forces from excavating in the solid material result in a required net force on the support means and an excavator is coupled to the support means via an excavator arm and coupled to the linkage arrangement whereby in use in cutting an excavation with the two wheels the net force on the excavator arm is adjustable via the linkage arrangement so as to permit an operator to steer the apparatus in the required direction and to cut the required excavation in the solid material.
  • the linkage allows the wheels, whilst parallel to one another, to adjust the distance between the planes defined by the wheels so as to keep the distance of the centres of the wheels from the ground surface a constant.
  • the two wheels are parallel to one another and remain parallel to one another during and after the pivoting movement of the link members.
  • One or more actuators may be used to pivot the link members, and the actuators may comprise rams.
  • the linkage is adjusted by the operator to arrange the wheels relative to each other whereby the position of one of the wheels is at a trailing position relative to the other wheel
  • the linkage is adjusted so that the wheel at the trailing position is arranged so that its path at least partially intersects the path taken by the other wheel so that the excavation cut by the wheel in the trailing position at least partially intersects the excavation cut by the other wheel
  • the linkage is adjusted as required by the operator so that the depth of the excavation cut by the wheel in the trailing position is substantially the same as or different from the depth of the excavation cut by the other wheel.
  • the two wheels are rotated in opposite directions such that the torque reaction force of one is at least partially cancelled by the other during the excavating to result in a required force on the support means
  • the two wheels may be rotated in opposite directions such that the torque reaction force of one is substantially cancelled by the other during the excavating whereby the net resultant force from the wheels on the support means is substantially zero
  • the two wheels are rotated in opposite directions and the positions of the wheels are adjusted relative to one another such that the force of one is at least partially cancelled by the other during the excavating to result in a required force on the support means
  • the required net force may be that required by an operator of machinery which is attached to the support means (e.g. an excavator) to drive and/or steer and/or control the apparatus for excavating solid material through the solid material in the required direction, or drive and/or steer and/or control the machinery as the apparatus for excavating solid material cuts and/or breaks the solid material
  • the two wheels may be rotated in opposite directions and the positions of the wheels adjusted relative to one another such that the force of one is substantially cancelled by the other during the excavating whereby the net resultant force from the wheels on the support means is substantially zero
  • the two wheels are rotated at substantially the same speeds (but in opposite directions), although they may be rotated at different speeds and in opposite directions, if desired
  • Each of the wheels can be thrust into the solid material such as rock with a force from zero in soft material up to a force that does not stall the motors driving the cutting wheels Typically the wheels are thrust into the solid material such as rock at a force in the range 500- 25,0001b, more typically 1 ,000- 1 ,0001b and even more typically 4,000- 12,000 lb, and yet even more typically 8,000 lb or 4 tonnes This implies a cutting force of about 2 5 tonnes which in turn requires a torque for each wheel of about 5,000 Nm if each wheel is about 400 mm in diameter Larger wheels will require larger forces and larger torques and vice versa
  • By making a cutting and breaking wheel free of picks in the vicinity of the means to break the material all the thrust and torque is available to push the means to break the material into the excavation (e.g. groove) to break under-cut material away
  • suitable wheels for use in this invention include
  • a cutting wheel for excavating a solid material comprising means to cut the material.
  • a cutting wheel for excavating a solid material comprising (a) means to cut the material, and
  • (b) means to allow excavation of an undercut in the solid material comprising means to allow escape of excavated material from the solid material and from the wheel during excavation of the solid material, and
  • a cutting and breaking wheel for excavating a solid material comprising (i) a cutting wheel having
  • a cutting and breaking wheel for excavating a solid material comprising (i) a cutting wheel having
  • a cutting and breaking wheel for excavating a solid material comprising (i) a cutting wheel having (a) means to cut the material,
  • a cutting wheel having a central portion and a plurality of arms extending outwardly and upwardly from and about the periphery of the central portion
  • a cutting wheel having a central portion and a plurality of arms extending outwardly and upwardly from and about the periphery of the central portion
  • a cutting and breaking wheel for excavating a solid material comprising (i) a cutting wheel having a central portion and a plurality of arms extending outwardly and upwardly from and about the periphery of the central portion
  • a method of excavating a solid material may comprise: cutting and breaking the solid material with one of the above wheels (A) to (I).
  • the wheel may be in the form of a disc, drum, barrel, cylinder, annulus, or roller, for example.
  • at least a portion of the wheel adjacent and including the peripheral edge of the wheel is curved or angled upwardly through an angle equal to the angle between the drive shaft and the normal to the surface of the solid material being excavated, so as to allow excavation of an undercut in the solid material effectively parallel to the surface of the solid material.
  • the means to cut the material are located at and attached to the peripheral edge of the wheel.
  • the means to cut the material comprises a plurality of cutting teeth or cutting picks (alternatively called drag tools), typically 2-25, more typically 3- 15, even more typically 5-10) spaced substantially evenly (or unevenly) or uniformly spaced but in orientations determined by a lacing pattern around a portion of the periphery of the cutting wheel
  • drag tools alternatively called drag tools
  • One particular form ofthe cutting wheel comprises nine slots and ten uniformly spaced drag tools and an unoccupied portion ofthe periphery adjacent the bursting wheel.
  • the means to allow excavation of an undercut in the solid material comprises means to allow escape of excavated material which comprises one or more slots (typically 2- 1 , more typically 4-8, even more typically 5-7, and even more typically 6 or 9 slots) in the wheel
  • the slots are apertures through the wheel disposed about the peripheral edge of the wheel or there are one or more slots that form part ofthe peripheral edge of the wheel
  • each slot is located between the means to cut the material such as between adjacent cutting picks (typically forming a spoke-like wheel).
  • the slots are large enough to substantially allow escape of at least some if not substantially all of the excavated material from the solid material and from the wheel during excavation of the solid material Not all the drag tools on each cuttin» wheel need necessarily be at the same radius. ir.
  • the means to break the material may comprise at least one wedge or bursting wheel.
  • the wedge(s) or bursting wheel(s) may be located on the top surface or the bottom surface of the wheel or on both the top and bottom surfaces Alternatively the wedge(s) or bursting wheel(s) may be coupled (integrally or non integrally) to a rotatable shaft member which is also coupled to the wheel.
  • the wedge(s) or bursting wheel(s) is spaced inwardly from the cutting picks and more typically is spaced inwardly from the peripheral edge of the wheel so as to break the material only after it has been undercut by the means to cut the material
  • the wheel can initially cut the excavation (e.g groove) and when the excavation (e.g groove) is at a predetermined depth (corresponding to the spacing between the periphery of the wheel and the wedge or bursting wheel), the wedge or bursting wheel will enter into the cut excavation (e.g groove) and will cause the solid to be broken
  • the wedge or bursting wheel may be located on the flat portion of the wheel or on the curved or angled portion of the wheel When the wedge or bursting wheel is on the angled portion of the wheel the curved or angled portion is lengthened to accommodate the wedge or bursting wheel When the wedge or bursting wheel is located on the curved or angled portion the wear on the cutting and breaking wheel, in use, will be typically less than when it is on the flat portion of the wheel, and/or the wheel may
  • the wedge or bursting wheel may be rotatably mounted relative to the wheel In this manner, the wedge or bursting wheel may be rotatably inserted into a cut excavation (e g groove) which may minimise wear
  • the wedge or bursting wheel may be adjustably mounted with respect to the wheel to allow it to extend from the wheel at a plurality of distances This may be of advantage should the hardness of the solid material vary according to cutting depth It may also allow the wheel to enter deeply into the cut excavation (e g groove) with subsequent expansion of the wedge or bursting wheel to cause the rock to break
  • the wedge or bursting wheel may be spaced inwardly from the peripheral edge of the wheel by varying distances depending on the type of rock to be cut and the cutting action, power capability of the apparatus and the like For instance, with soft friable solid, the wedge or bursting wheel can be spaced more towards the peripheral edge and can have a higher raised profile For strong friable rock, the wedge or bursting wheel can be spaced closer to the centre of the wheel to improve its leverage For strong non-friable rock, the wedge or bursting wheel height may be reduced It is preferred that the cutting and breaking wheel is provided with a pair of wedges or bursting wheels which are connected to an attachment member, the attachment member being mountable in an aperture in the wheel The attachment member may threadingly engage with the opening in the wheel.
  • a first wedge or part of the bursting wheel extends from the top surface of the wheel, and a second wedge or part of the bursting wheel extends from the bottom surface of the wheel.
  • the first and second wedges of the bursting wheel may be coupled together (integrally or non-integrally) with a coupling shaft or shafts which passes through an aperture in the cutting and breaking wheel
  • the first and second wedges of the bursting wheel are releasably mounted relative to each other, and to the cutting and breaking wheel
  • the wedge or bursting wheel profile is symmetrical about its rotation axis
  • the first and second wedges of the bursting wheel are releasably mounted relative to each other, and to the cutting and breaking wheel there is slop or clearance between the coupling shaft or shafts and the aperture in the cutting and breaking wheel to allow dirt and grit which may enter the aperture to leave but without allowing larger particles to get
  • the slop or clearance is 0 5-5mm, more typically 0.75 - 3mm, even more typically 0.8 - 2mm, yet even more typically 0 9- 1 5mm and even more typically about 1mm
  • the first and second wedges of the bursting wheel or bursting wheel assembly may be fitted with bearings and seals so as to prevent the entry of dirt and grit into the aperture
  • profiles for the wedge or bursting wheel may include, for example, in the case of a wedge - a simple wedge shape, or in the case of the wedge or bursting wheel a cone shape or a "pyramid" shape or a "mushroom” shape
  • the angle of inclination of the leading face of the shape and the height of the profile may also vary Typically the angle of inclination of the inclined face is between I to 1 degrees, more typically 2 to 10 degrees and even more typically 3 to 8 degrees
  • the profile of the wedge or bursting wheel surface may vary and may depend on the type of solid to be cut and the type of cutting action If a pair of wedges or bursting wheels are provided, each wedge or bursting wheel may have an identical or a different profile relative to the other.
  • the wedges of the bursting wheels may have identical profiles (such as mushroom shapes) while in another form, one wedge of the bursting I S wheel may be substantially planar while the other wedge or bursting wheel may have a mushroom shape, or a conical shape or a pyramidal shape, for example
  • the top surface ofthe bursting wheel is a mushroom shape and the bottom surface a cone shape designed to roll easily on the floor of the excavation
  • the cutting wheel is coupled (integrally or non integrally) to or adjacent to one end of a rotatable shaft member, the shaft member being rotatably drivable by a drive means (e g a motor)
  • the drive means may be hydraulic, pneumatic, electric or internal combustion
  • the drive means is coupled to a reduction gearbox to provide the rotatable shaft member with a lower rotating speed but high torque
  • a biasing means may be coupled to the rotatable shaft member to bias the rotatable shaft member, and therefore the wheel against and away from the solid material to be cut Typically the biasing means provides sufficient
  • Figure 1 is a perspective view of a cutting and breaking wheel coupled to a rotatable shaft
  • Figure 2 is a side view of a cutting and breaking wheel coupled to a rotatable shaft of Fig. 1 ;
  • Figure 3 is an isometric view of an apparatus according to an embodiment of the invention
  • Figure 4 is a view of the support frame assembly, attachment means and part of the adjustment means ofthe apparatus illustrated in Figure 3;
  • Figures 5A-5D show top, rear, side and isometric views of the apparatus having the two cutting or cutting and breaking assemblies in line with each other;
  • Figures 6A-6D show top, rear, side and isometric views of the apparatus of Figure 3, where the cutting or cutting and breaking assemblies are in an extreme leading and trailing configurations.
  • the assemblies may be at any intermediate positions between the extremes as well as at the extremes;
  • Figure 7 shows a cutting or cutting and breaking wheel shaft cylinder link assembly
  • Figure 8 shows a rear views of the apparatus having the two cutting or cutting and breaking assemblies in line with each other the cutting and breaking wheels attached to the apparatus being of the type depicted in Figs I and 2,
  • Figure 9 is a side view of the cutting and breaking wheel coupled to a rotatable shaft of Fig. 1 excavating an undercut;
  • Figure 10 is a schematic depiction of two cutting and breaking wheels excavating solid material
  • Figure 1 1 is a schematic side view depiction o the apparatus having the two cutting or cutting and breaking assemblies attached to an excavator arm excavating solid material,
  • Figure 12 is a side view of part of an alternative cutting and breaking wheel coupled to a rotatable shaft to that of Fig. 1 ;
  • FIG. 13(c) to 13(i) depict alternative parallelogram linkages which couple, support and arrange two cutting wheels or two cutting and breaking wheels; and
  • Figure 14 is a perspective view of a cutting and breaking wheel coupled to a rotatable shaft;
  • Figure 15 is a side view of a cutting and breaking wheel coupled to a rotatable shaft of Fig. 14 where the wheel of Figure 14 has been rotated through - 180° (arms 607 and 608 of Figure 14 are not depicted);
  • Figure 16(a) schematically depicts a side view of a wheel of the type shown in Figures 1 and 2 cutting an excavation;
  • Figure 16(b) schematically depicts a side view of a wheel of the type shown in Figures 14 and 15 cutting an excavation
  • Wheel 300 has a top surface 302 and a bottom surface 303. Top surface 302 is curved upwardly adjacent the peripheral edge 3 10 of wheel 300 at 304, 305, 306, 307, 308 and 309 to allow excavation of an undercut in the solid material.
  • Wheel 300 typically comprises a strong, tough steel and has a wear resistant steel layer welded by electric arc on its surfaces 302 and 303.
  • Bursting wheel assembly 301 typically comprises case hardened steel.
  • Picks or drag tools 3 1 1 -3 1 may be conventional insert picks, in which a tungsten carbide tool tip is inserted into an axial hole in the steel main body of the pick and are used for gauge cutting Drag tools 3 1 1 -3 1 may be any type of conventional, or unconventional drag tool.
  • Tools 3 1 1 -3 1 may or may not be fitted with means to allow rotation.
  • Tools 3 1 1 -3 15 may or may not be provided with dust suppression or working or assisting water jets.
  • Tools 3 1 1 - 315 may be arranged with any type of conventional or unconventional lacing pattern in which the tools are oriented so as to excavate the undercut Preferably whatever lacing pattern is used will ensure that the excavation (e.g groove) which is cut has sharp stress-concentrating corners, making for easy breaking Picks 3 I 1 -3 15 are arranged such that at least one of the picks extends above top surface 302 (e.g pick 3 12), at least one of the picks extends below bottom surface
  • bursting wheel assembly 301 is formed from a pair of bursting wheel components being upper bursting wheel component 301 a and lower bursting wheel component 301 b, shown exploded with reference to Figure 2 Bursting wheel assembly 301 is rotatable as a single unit such that bursting wheel components 301 a and 301 b are able to rotate independently of wheel 300 Bursting wheel component 301 a has a
  • Each wheel 300 is supported, rotated, and mounted by an assembly, an embodiment of which is illustrated in Figure 3
  • Apparatus 10 which can be attached to an excavator arm, for example, and which can be used for cutting through ground material such as rock and the like.
  • Apparatus 10 has two spaced apart cutting assemblies 1 1 , 12 which shall be described in greater detail below.
  • Cutting assemblies 1 1 , 12 respectively comprise a rotatable shaft 13, 14, the bottom of each shaft coupled to and supporting a cutting or cutting and breaking wheel 15, 16 respectively (note wheels 1 and 16 are depicted as showing the effective cutting width rather than showing details of the wheels per se).
  • a support frame assembly (better shown in Figure 4) supports the two cutting assemblies 1 1, 12 in the desired position which is spaced apart with shafts 13, 14 being generally parallel with respect to each other.
  • each cutting assembly 1 1 , 12 is coupled an upper hydraulic drive motor 17, 18 respectively, each motor being of a type known in the art and which is powered by hydraulic fluid from the vehicle to which it is coupled
  • the drive motors 17, I S drive shafts 1 , 14 which in turn rotate the cutting wheels 1 , 16 Assemblies 1 1 , 12 may be fitted or coupled to an excavator via an excavator arm by attaching plate 23 of Fig 4 to the excavator arm via appropriate "ears" in place of a bucket of an excavator and power is to be taken from the hvdraulic pumps of the excavator, rather than from a power take-off (though a power take off could be used to drive a hydraulic pump if appropriate, or indeed an external separate pump and drive motor could be used).
  • a direct drive motor may be used i.e no gearbox being used
  • Choice of drive motor type petrol, diesel, electric pneumatic etc.
  • type of drive directly or via a gearbox
  • gearbox type and ratio are engineering decisions depending on the precise application of a realisation of this technology.
  • Choice of final speed depends on circumstance, but will generally be such as will give a drag tool a speed through solid rock of 2 or 3 m/sec (though speeds of 0 25 to 5 m/s may be used).
  • a typical operating speed of a cutting wheel operates 70-90rp ⁇ n, more typically about 78rpm.
  • the angle at which shafts 13, 14 (and therefore wheels 1 5 and 16) extends below the drive assembly can be varied
  • the angle of each of shafts 13, 14 to the vertical is typically the same and is typically between 3° to 45°, more typically 5° to 30°, even more typically 10° to 27°, and yet even more typically about 25°
  • Support frame assembly 19 comprises a main mounting structure 20 formed from box steel To the bottom of main mounting structure 20 is an extending end plate 21 which extends under a socket arrangement 22 which shall be described in greater detail below On an upper part of main mounting structure 20 is provided an attachment means 23 to attach the entire apparatus to an excavator arm, but it should be appreciated that the type of attachment means can of course vary depending on to what type of vehicle the apparatus is attached Forward of attachment means 23 is an extending plate 24 which is strengthened by gussets 25, 26 to prevent sag At the front end of extending plates 24 is a pivot connection 27 to pivotally couple a rear link member
  • the rear link member shall be described in greater detail below Intermediate the ends of extending plate 24 is a central support assembly 29 which depends from and is pivotally attached to plate 24 Central support assembly supports a forward link member 30 adjacent its upper end, and supports the socket arrangement 22 adjacent its lower end Forward link member 30 and rear link member 28 form an upper attachment area to which an upper part of each cutting assembly 1 1 , 12 can be attached The socket arrangement 22 forms a lower attachment area to which a lower portion of each cutting assembly 1 1 , 12 can be attached.
  • each cutting assembly has a ball 1 , 32 each ball locating within a respective socket 33, 34 to form a ball and socket connection It can be seen that in this manner the cutting assembly can freely swivel in its socket
  • Each socket is of a split ring configuration which can be seen in Figure 4 to allow the respective ball to be removed therefrom If desired, seals or lubricants can be positioned within the sockets 33, 34
  • the upper end of each cutting assembly 1 1 , 12 is attached to forward and rear link members 28, 30 via a cylinder link assembly as illustrated in Figure 7
  • Cylinder link assembly 35 comprises a hollow tube 36 through which a respective rotatable shaft member ( 13 or 14) can extend with motor at the top and ball joint at the bottom
  • Fixed to the outside of tube 36 is a flat plate 37 which extends in a diametrically opposed manner from tube 36
  • Plate 37 has openings 38, 39 the openings functioning to accommodate pivot pins to pivotally couple plate 37 to one end of forward and
  • Link members 28, 30 are moved by an actuator in the form of two hvdraulic rams 40, 4 1 only one of which is illustrated in Figure 3 but both of which are illustrated in Figures 5A and 6A
  • Each hvdraulic ram is pivotally attached at one end to main mounting structure, and a spacing lug 42 is provided on each side of structure 20 to correctly position the respective ram
  • the other end of each ram is pivotally connected to an arm 43, the arm being rigidly attached to the respective cylinder link assembly 35 (see Figure 7)
  • each ram acts on the respective cylinder link assembly (one link assembly for each cutting assembly), which in turn causes the forward and rear-link members 28, 30 to pivot about their respective vertical axis, at the same time rotating arrangement 22 (of Fig.
  • the ball and socket arrangement facilitates movement of cutting assemblies 1 1 , 12 relative to each other.
  • An excavator is coupled to plate 23 via an excavator arm and coupled to the linkage arrangement comprising link members 28, 30 which are moved by two hydraulic rams 40, 41 whereby in use in cutting an excavation with the two wheels 15 and 16 the net force on the excavator arm via plate 23 is adjustable by appropriately adjusting link members 28, 30 and thus the relative positions of wheels 1 and 16 to each other in the solid material so as to permit an operator to steer the apparatus 10 in the required direction and to cut the required excavation in the solid material.
  • Figures 5A-5D show the apparatus with cutting assemblies 1 1 , 12 in alignment, that is neither of cutting assemblies 1 1 or 12 lead or trail. This arrangement would be suitable when cutting through uniform rock when no steering action is needed Whether the rock is weak (not soft) or strong (not hard) is substantially irrelevant
  • Figures 6A-6D show the arrangement where cutting assembly 1 1 is now the leading cutting assembly and cutting assembly 12 is the trailing cutting assembly, ln this configuration, cutting assembly 1 1 presents its cutting wheel forward of the cutting wheel of cutting assembly 12.
  • FIGs 6A-6D The arrangement of Figures 6A-6D is provided and maintained by operation of the two hydraulic rams 40, 41 and this can be controlled by a driver in the cabin That is, by extension or retraction of rams 40, 41 , the cutting assemblies can adopt a leading/trailing position relative to each other, or an aligned position as illustrated in Figures 5A-5D Relative to the central pivot axis of the apparatus (fig 4-7) the lower ball joints both move in an arc, defined by the distance of the ball from the central pivot axis
  • the outer tubes containing the drive shaft do not rotate with the rotation of the socket arrangement (22) but rather slide within the socket (33, 34) as the socket rotates so that relative to the main frame they do not rotate Motion in an arc without rotation is achieved by a parallelogram linkage of which the struts 28 and 30 fo ⁇ n two sides (the other side being the plate 37 of figure 7 pivoting about holes 39-38)
  • the apparatus 10 typically uses two cutting or cutting and breaking wheels, such as for example, the two cutting and breaking wheels 300 and 300a (similar to that described in Figs 1 and 2 or similar to that described in Figs 14 and 1 ) illustrated in Figure 8 (mounted so as to counter rotate to one another), the orientation of the shafts 316 and 316a of which is at an angle ⁇ to the normal to the rock face, ⁇ being closer to normal to the rock face being excavated than it is to parallel to it
  • the two wheels 300, 300a are counter rotated relative to each other This allows the torque reaction from one wheel 300 to be at least in part cancelled by that from the other wheel 300a and substantially cancelled providing that both wheels 300 and 300a are thrust equally into the same material
  • Each wheel 300, 300a is typically trust into the solid material (e g rock depending on the type of rock) with a force of about 8,000 lb or 4 tonnes This implies a cutting force of about 2 5 tonnes which in turn requires a torque of about 5,000 Nm if each bursting wheel is about 400 mm in
  • ⁇ represent the maximum perpendicular distance between the plane surface of the rock and the upper surface ("top lip") of the "happy smile", when the cut-and-break cutting and breaking wheel 50 is operating at its maximum depth at which the cutting and breaking action will occur.
  • ⁇ will be proportional to the diameter of the cutting and breaking wheel
  • d represent a generalised maximum depth of excavation, d being typically somewhere between about 1/3 and 2/3 of the diameter of the cutting and breaking wheel 50 when the cutting and breaking wheel 50 is operating in comparatively weak or jointed rock 52 (jointed rock 52 will break along the joints rather then in the way described for massive rock), it being understood that a wheel of larger diameter would operate at a larger value of d
  • the cutting and breaking wheel 50 has the appearance of a dish or saucer, the outer portions 66 being bent up at an angle ⁇ in relation to the plane of the central part of the cutting and breaking wheel 67 (Because of the clearance excavated by the gauge tools 54, the angle need not in practice be exactly ⁇ , though the angles are generally substantially the same)
  • Fig 9 which is drawn for the plane in the direction of motion of the centre of the cutting and breaking wheel 50 and including the axis of rotation of the cutting and breaking wheel 50, the quantity d is shown, together with other quantities I, w, x, y and t Of these, I, the depth undercut, will for a given geometry be proportional to the diameter of the cutting and breaking wheel 50 that is, d and I will behave similarly as the diameter of the cutting and breaking wheel is varied It has been found that a value of I in the vicinity of 1 /6 the diameter of the cutting and breaking wheel 50 is appropriate, though values of up about 1/3 may be possible It is desirable to make I as large as possible, since a larger I will make the undercut material more easily broken, and imply an increase in d There are however geometrical constraints which limit the length that be used for I, the distance from the bend in the wheel 50 to the tool tips 54 In particular, it is important cutting and breaking wheel 50 does not nib against the excavation, and so clearance is excavated, represented by x and y in the sketch In the
  • Each drag tool 54 produces fragments of cut material, and these have to be removed from the excavation by being swept aside by the passing tools and their mountings
  • the tools and their mounting boxes project a portion of the distance 1, the remainder of I being the raised portion of the cutting and breaking wheel 50 itself
  • the volume of cuttings may be larger than can easily be accommodated between the tools 54 and their mountings 55 In this case and referring momentarily to Fig 1 it is desirable to increase the available volume, by mounting the tools 3 1 1 -
  • Cut-and-break rock cutting wheel or cutting and breaking wheels are of necessity operated with a substantial torque, so as to apply a suitable load to the drag tools and so cause them to penetrate the rock which has to be cut.
  • the cutting force applied to a drag tool can be several tens of kilo-Newtons, in the case of a 465 mm cutting wheel or cutting and breaking wheel designed to excavate Helidon Sandstone, a resultant of up to 30.000N has been designed for, and a cutting wheel or cutting and breaking wheel may have several tools engaged at one time, but only along a part of the circumference of the cutting wheel or cutting and breaking wheel.
  • the two torque reactions be deliberately arranged to be significantly out-of-balance, so as to allow the tools to follow a path other than directly towards the slew axis of the excavator It would be anticipated that the steering action would involve a combination of steering by the cutting-and-breaking wheels combined with operation of the slew mechanism of the excavator Using this ability to steer the cutting may be an uncommon occurrence, but invaluable when required
  • cut-and-break cutting wheel or cutting and breaking wheels should be operated with the drive shaft at the angle ⁇ discussed above It is also desirable that they should operate at the same, depth, d, which should be close to the maximum possible in that particular rock
  • d should be close to the maximum possible in that particular rock
  • the geometry of the parallelogram linkage may be realised in practice through a combination of ball joints and light rods
  • the passive or active distortion of a parallelogram linkage may be accomplished in numerous different ways. Active distortion methods include fitting a ram or extending screw device between diagonally opposite corners of the parallelogram, or fitting a ram between a fixed point and a corner or side of the parallelogram. Another alternative is to use a motor and a sector plate, the sector being fixed to one of the sides of the parallelogram, the motor to an adjacent side
  • the two cutting wheel or cutting and breaking wheels are not typically thrust equally into the same material, either deliberately or as a consequence of the practical difficulty of doing so.
  • this out-of-balance force may be controlled, and be enhanced or diminished as the operator requires, by using a parallelogram linkage controlled by the operator.
  • the parallelogram linkage allows the direction of the cutting wheel or cutting and breaking wheel shaft to be held constant while the disposition of the cutting wheel or cutting and breaking wheel may be changed, so that one is partially behind the other.
  • Figs 13(a) and 13(b) illustrate, in schematic form, a parallelogram linkage which couples, supports and arranges two cutting wheels or two cutting and breaking wheels 500 and 501 which are coupled respectively to one end as shown of rotatable shafts 502 and 503 Shafts 502 and 503 are linked by linkages 504 and 505 as depicted in Figs. 13(a) and (b).
  • Parallelogram A is formed by linkages 504, 505, 506 and 507, as depicted in Fig. 13(a).
  • Linkage 506 is joined rigidly to linkage 1 I by rotatable linkage structure 508
  • parallelogram A is distorted by movement at joints located where the linkages are joined to one another which allow movement about pins with their axes in the z direction so as to allow movement only in an x - y plane in the x-y plane by rotation of structure 508 in direction 509 to form another parallelogram in the x-y plane, designated parallelogram B in Fig 13(b)
  • Formation of parallelogram B causes wheel 500 and coupled shaft 502 to move in the direction of arrow 510 as depicted in Fig 13(a) so as to trail wheel 501 as depicted in Fig. 13(b).
  • the leading cutting wheel or cutting and breaking wheel will experience more resistance to its motion than the one following it, and so there will be a larger torque reaction from the leading wheel than the one behind it Tt is possible for the operator to choose at will which wheel is the lead wheel, and which is the following wheel, and so he can choose the direction of the unbalanced force created on the excavator about the slew axis.
  • This basic stmcture can be simplified by the omission of any one of the rods 504, 506, 51 1 or 514, provided that the simplified structure includes a rigid connection to ensure that the structure moves in the same way that it would were the fourth rod present.
  • this rigid connection is provided by tube 508 rigidly joining rods 506 and 51 1.
  • wheels 501 and 500 can be moved relative to one another so that wheel 500 trails wheel 501 , parallelogram A is distorted by movement at joints located where the linkages are joined to one another which allow movement about pins with their axes in the z direction so as to allow movement only in an x - y plane in the x-y plane by distortion of parallelogram A to form another parallelogram B in the x-y plane
  • Formation of parallelogram B causes wheel 500 and coupled shaft 502 to move in the direction of arrow so as to trail wheel 501 (not shown but see Fig. 13(b) which illustrates the change in positions of wheels 500 and 501 relative to one another).
  • FIG 13 (c) 512, 5 1 , 516 and 19 are pins passing through and linking the corners ofthe top and bottom parallelograms A and A'. These pins 12, 5 1 5, 16 and 519 are drawn as single pins, though each pin could equally well be two short pins, one in each of the upper and lower parallelograms. Alternative and equally effective arrangements of parallelograms are illustrated in figures
  • FIG. 13(d) has been replaced by long pins, 523 and 524 ln figure 13 (f) two parallelograms, an upper one, designated parallelogram A, formed of linkages 529, 53 1 , 528, 530 together with extensions 535 536 which are linked to shafts 507 and 502, is linked by long pins, 537, 534, 533 and 532 to a lower parallelogram designated parallelogram A', formed by linkages 527, 525, 51 1 and 526
  • Figs 13(a) and 13(b) illustrate, in schematic form, a parallelogram linkage which couples, supports and arranges two cutting wheels or two cutting and breaking wheels 500 and 501 which are coupled respectively to one end as shown of rotatable shafts 502 and 503
  • shafts 502 and 503 are linked by linkages 544 and 5 1 1 as depicted
  • Parallelogram A is formed by linkages 551 1 ,54 1 , 542 and 540, as depicted in Fig 13(g)
  • Linkage 544 is
  • FIG. 13(d) is supported
  • the central tube, 508, is supported by a rigid bar, 508 (a), which passes through it, and which is permanently fixed at the top to the support stmcture which forms a frame, 561 , 562, and 560
  • a rigid bar, 508 (a) which passes through it, and which is permanently fixed at the top to the support stmcture which forms a frame, 561 , 562, and 560
  • Part 508(a)of figure 13 (h) is invisible in figure 4, but is in fact, present inside the tube, 29
  • Figure 13 (h) also illustrates one of a number of alternative possible means of adjusting the shape of parallelogram
  • a In figure 13 (h) is illustrated a ram, 565, which by extending or contracting would rotate the rigid structure 506,
  • Figure 13 (i) illustrates schematically the means which may be used to change the shape of parallelogram A (which is depicted in more detail in Figs 3-7
  • Two rams 572, 575, and attachments 573, 574, 570, 571 connect corners of parallelogram A to the support stmcture 562.
  • one of the rams is visible, 40, the other invisible behind the rest of the apparatus.
  • This electronic control may comprise limited control of the motion of the excavator stick so as to ensure that the speed of motion is such as will keep the cutting wheel or cutting and breaking wheels operating efficiently, or complete operation of the cutting process under computer control, or any alternative between these extremes
  • Fig 9 depicts a single cutting and breaking wheel 50 but the following description is equally applicable the simultaneous use of two cutting and breaking wheels ln order to excavate the undercut 53 each cutting and breaking wheel 50, which is driven by inclined shaft 57, at angle ⁇ , 51 , advances to the right in figure 9
  • the rate of rotation of the cutting wheel or cutting and breaking wheel 50 is determined by the properties of the tips of the drag tools and the available power With conventional tungsten carbide tipped tools, the rate of rotation is such as will give to the tool tips a speed relative to the rock across which they are being driven in the range of 0 1 to 5 metres per second, more typically 0 5 to 3 5 metres pre second, even more typically 1 to 3 metres pre second, a speed of 2 metres per second being typical It is necessary to lace the cutting tools, of which two of several fitted to the wheel are illustrated, 54, 62, the tools being arranged so that they do not all follow the same path, some being angled up 62, some being in the middle 54 and some pointing down not shown Appro
  • Fig. 10 is shown two cut-and-break cutting and breaking wheels 76, 77 being used to excavate a trench 78, the cutting and breaking wheels having undercut rock, 79, the cuttings emerging in the gaps 73 between the tools 72
  • the cutting and breaking wheels are progressing in the direction of the arrow 80
  • the cutting and breaking wheels are driven by shafts, 74 It is appropriate for the cutting and breaking wheels to counter-rotate so that the torque reaction forces they apply to the machine to which they are both attached tend to cancel
  • the rotations shown have the advantage that large fragments of material broken free tend to be carried between the two shafts and be dumped behind the machine
  • the alternative rotation may have advantage if the rock breaks into fragments too large conveniently to pass between the shafts If the opposite rotation is used, the excavated lumps will tend to be dumped beside the excavation Note that the direction in which the tools 72 are fitted depends on the intended rotation It will be seen that cutting and breaking wheel 76 is trailing cutting and breaking wheel 77 in this illustrated example, though the two wheels could be
  • the upper mushroomed shaped portion 90 of the bursting wheel 89 is partially or completely recessed in the thickness of the cutting and breaking wheel, 94 which is coupled to rotatable shaft 98
  • Expansion is achieved by, for example, by admitting high-pressure water into channel 95, and thence to channels 95a and 95b to force portions 90 and 91 apart against spring 93 which is attached to cavities 99 and 100
  • Contraction is achieved by, for example, by releasing the pressure applied to the water in channel 95, and
  • phased high pressure water is provided via channels 95, 95a and 95b to the bursting wheel 89 only when the bursting wheel 89 is in an undercut, to hydraulically separate portions 90 and 1 of a bursting wheel so as
  • Fig 1 1 depicts an articulated excavator arm which comprises three parts, and has three movements, limited normally to a single plane
  • the part of the articulated arm closest to the excavator itself is called the boom, 2 in Fig 1 1 , the associated movements being up and down
  • the boom is jointed to the stick, 5 in Fig 1 1 , which moves in and out Articulated to the end of the stick is the bucket, and its movements are curl, when the bucket moves towards the excavator, and uncurl, when it moves the other way Filling an excavator bucket starts with the stick out, the boom down, and the bucket partially curled In this position the bucket teeth are correctly oriented to dig into the ground
  • the operator is required to bring the bucket towards the excavator whilst maintaining the bucket at the correct orientation for the bucker to fill, and at a constant depth below the surface This is accomplished by '
  • the excavator operator is used to this sequence of operations, to the point where a skilled operator performs this sequence of operations without any substantial conscious thought
  • the excavator operator unhitches the bucket and replaces it with the cut-and-break apparatus, 1 in Fig 1 I connecting the appropriate hydraulic hoses and any electronic transducers associated with the cut-and-break apparatus 10 (see for example Figs 3-6 for more details of apparatus 10)
  • the operator then lifts the apparatus 10 clear of the ground, and verifies that the two cutting and breaking wheels were both at the same distance from the operator, that is, neither wheel is advanced in front of the other
  • the operator will then start the oil flow to the hvdraulic motors, which will begin to turn the cutting and breaking wheels Lowering the boom, sending the stick out, and curling the cut-and-break apparatus 10 slightly will result in the cutting and breaking wheels being poised just above the ground level, at an angle rather greater than , in a position where operating the curl will simultaneously decrease the angle of
  • Wheel 600 has a top surface 602 and a bottom surface 603.
  • Top surface 602 has arms 604, 605, 606, 607, 608 and 609 extending therefrom which are curved (or alternatively angled) upwardly therefrom to allow excavation of an undercut in the solid material.
  • Wheel 600 typically comprises a strong, tough steel and has a wear resistant steel layer welded by electric arc on its surfaces 602 and 603.
  • Bursting wheel assembly 601 typically comprises case hardened steel
  • a cutting pick or drag tool 61 1 , 612, 613, 614 and 615 Attached respectively to the end of each of arms 604, 605, 606. 607 and 608 is a cutting pick or drag tool 61 1 , 612, 613, 614 and 615.
  • Picks or drag tools 61 1 -6 1 5 may be conventional insert picks, in which a tungsten carbide tool tip is inserted into an axial hole in the steel main body of the pick and are used for gauge cutting Drag tools 61 1 -61 5 may be any type of conventional, or unconventional drag tool.
  • Tools 61 1 - 1 may or may not be fitted with means to allow rotation.
  • Tools 61 1 -61 may or may not be provided with dust suppression or working or assisting water jets.
  • Tools 61 1 -615 may be arranged with any type of conventional or unconventional lacing pattern in which the tools are oriented so as to excavate the undercut.
  • whatever lacing pattern is used will ensure that the excavation (e g. groove) which is cut has sharp stress-concentrating coi ners, making for easy breaking
  • Picks 61 1 -61 5 are arranged such that at least one of the picks extends above the surface of its corresponding arm (e.g. pick 612 extends above the upper surface of arm 604), at least one of the picks extends below its corresponding arm (e.g. pick 615 extends below the lower surface of arm 607) and at least one of the picks are in line with their corresponding arms (e picks 613, 614 and 61 1 ).
  • bursting wheel assembly 601 is formed from a pair of bursting wheel components being upper bursting wheel component 601 a and lower bursting wheel component 601 b, shown exploded with reference to Figure 15. Bursting wheel assembly 601 is rotatable as a single unit such that bursting wheel components 601 a and 601 b are able to rotate independently of wheel
  • Bursting wheel component 601 a has a "mushroom” profile which is a consequence of the mushroom shape of its upper surface 622
  • Bursting wheel component 601 b has a "pyramid” profile which is formed when the pyramid shaped bottom ponion 624 of bursting wheel component 601 a is inserted through aperture 625 of wheel component 601 b Prior to or during insertion O ring clip 626 is located over O ring clip retaining portion 627 of wheel component
  • bursting wheel components 601 a and 601 b are fitted to an attachment portion 628 which is in the form of a annulus having an external thread The annulus fits within a corresponding threaded opening within bursting wheel 600 and this results in attachment portion 628 being securely threadingly
  • FIG. 20 Each wheel 600 is typically supported, rotated, and mounted by an assembly, as shown for wheel 300 of Figures 1 and 2 in Figures 3- 13i
  • Figure 16(a) schematically shows an undercut excavation being made by a wheel 300 (as per wheel 300 of Figs I and 2)
  • Figure 16(b) schematically shows an undercut excavation being made by a wheel 600 (as per wheel 600 of Figs. 14 and 1 5)
  • Figures 16(a) and 16(b) that because
  • bursting wheel 601 is located on curved or angled arm 609 on wheel 600, bursting wheel 601 is able to fit more easily under overhang 700 as shown in Figure 16(b) than bursting wheel 301 which is located on flat surface 302 of wheel 300, is able to fit under overhang 800 as shown in Figure 16(a) This enables wheel 600 to break off at least a portion of overhang 700 easily and with less wear on cutting and breaking wheel 600 than on wheel 300

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Earth Drilling (AREA)

Abstract

L'invention concerne un appareil (10) pour former une excavation dans un matériau solide. L'appareil (10) comprend deux roues coupantes (15, 16) pour réaliser une excavation dans ledit matériau, un moyen de support (11-14), (17-42) supportant les roues coupantes (15, 16) et un dispositif (40, 41) coopérant avec les roues coupantes (15, 16) pour les positionner l'une par rapport à l'autre de manière à ce que les forces de réaction, dues au travail d'excavation dans le matériau solide, produisent la force nette requise sur le moyen de support (11-14), (17-42). Il est avantageux d'installer les deux roues coupantes ou la roue coupante et la roue broyeuse pour qu'elles tournent en sens inverse, car dans ce système, les couples antagonistes s'annulent sensiblement. Chaque roue coupante (15, 16) a une surface supérieure courbée vers le haut, près du bord périphérique de la roue. La surface périphérique est pourvue d'une pluralité de pics ou d'outils d'excavation qui creusent une excavation horizontale dans le matériau solide, lorsque les roues (15, 16) tournent. Un dispositif de dislocation peut être installé sur chaque roue coupante (15, 16) pour être poussé dans l'excavation horizontale et disloquer le matériau solide lorsque les roues (15, 16) tournent. Les pics coupants peuvent être montés aux extrémités d'une pluralité de bras s'étendant vers l'extérieur et vers le haut depuis une partie de moyeu de chaque roue (15, 16) pour permettre au matériau détaché, d'être évacué de l'excavation. L'appareil (10) peut être monté à l'extrémité d'un bras sur une excavatrice à chenilles, au moyen d'une plaque de montage (23).
PCT/AU1996/000687 1995-11-01 1996-11-01 Procede et appareil pour excaver dans un materiau solide Ceased WO1997016606A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU72687/96A AU7268796A (en) 1995-11-01 1996-11-01 Methods and apparatus for excavating a solid material

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPN6319 1995-11-01
AUPN6319A AUPN631995A0 (en) 1995-11-01 1995-11-01 Methods and apparatus for excavating a solid material

Publications (1)

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WO1997016606A1 true WO1997016606A1 (fr) 1997-05-09

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ZA (1) ZA969202B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000066840A1 (fr) * 1999-05-03 2000-11-09 Abascal Rubio Jose Manuel Machine centrifuge servant a projeter et a briser des agregats et autres matieres
WO2002001045A1 (fr) * 2000-06-28 2002-01-03 Voest-Alpine Bergtechnik Gesellschaft M.B.H. Machine d'extraction ou de creusement pour l'extraction de roches
FR2839742A1 (fr) * 2002-05-17 2003-11-21 Rene Brunone Engin d'extraction de roche dans une carriere
US6658767B2 (en) 2000-10-23 2003-12-09 Mastenbroek Ltd. Trenching method and apparatus
EP3170939A1 (fr) * 2015-11-18 2017-05-24 Vermeer Manufacturing Company Interface flexible de montage pivotant pour un arbre rotatif

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000066840A1 (fr) * 1999-05-03 2000-11-09 Abascal Rubio Jose Manuel Machine centrifuge servant a projeter et a briser des agregats et autres matieres
ES2153320A1 (es) * 1999-05-03 2001-02-16 Rubio Ignacio Abascal Lanzador-rompedor centrifugo de aridos y otros materiales.
US6591520B1 (en) 1999-05-03 2003-07-15 Jose Manuel Abascal Rubio Centrifugal thrower-crusher for aggregates and other materials
AU769295B2 (en) * 1999-05-03 2004-01-22 Ignacio Abascal Rubio Centrifugal thrower-crusher for aggregates and other materials
WO2002001045A1 (fr) * 2000-06-28 2002-01-03 Voest-Alpine Bergtechnik Gesellschaft M.B.H. Machine d'extraction ou de creusement pour l'extraction de roches
US6658767B2 (en) 2000-10-23 2003-12-09 Mastenbroek Ltd. Trenching method and apparatus
FR2839742A1 (fr) * 2002-05-17 2003-11-21 Rene Brunone Engin d'extraction de roche dans une carriere
EP3170939A1 (fr) * 2015-11-18 2017-05-24 Vermeer Manufacturing Company Interface flexible de montage pivotant pour un arbre rotatif
US10443208B2 (en) 2015-11-18 2019-10-15 Vermeer Manufacturing Company Pivotally flexible mounting interface for a rotatable shaft

Also Published As

Publication number Publication date
AUPN631995A0 (en) 1995-11-23
ZA969202B (en) 1997-05-29

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