WO2012031311A1 - Fleuret de mine amélioré - Google Patents

Fleuret de mine amélioré Download PDF

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Publication number
WO2012031311A1
WO2012031311A1 PCT/AU2011/000220 AU2011000220W WO2012031311A1 WO 2012031311 A1 WO2012031311 A1 WO 2012031311A1 AU 2011000220 W AU2011000220 W AU 2011000220W WO 2012031311 A1 WO2012031311 A1 WO 2012031311A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
fluid circuit
damping
stroke length
circuit
Prior art date
Application number
PCT/AU2011/000220
Other languages
English (en)
Inventor
Alexander Sangster
Dechun Kang
Geoffrey Whyte
Original Assignee
Rockdrill Services Australia Pty Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AU2010904066A external-priority patent/AU2010904066A0/en
Application filed by Rockdrill Services Australia Pty Ltd filed Critical Rockdrill Services Australia Pty Ltd
Priority to US13/819,389 priority Critical patent/US20140144660A1/en
Priority to EP11822919.4A priority patent/EP2614217A4/fr
Priority to AU2011301130A priority patent/AU2011301130A1/en
Priority to CA2810914A priority patent/CA2810914A1/fr
Priority to JP2013527422A priority patent/JP2013537266A/ja
Priority to CN2011800433623A priority patent/CN103097654A/zh
Publication of WO2012031311A1 publication Critical patent/WO2012031311A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • E21B6/06—Drives for drilling with combined rotary and percussive action the rotation being intermittent, e.g. obtained by ratchet device
    • E21B6/08—Separate drives for percussion and rotation
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/16—Valve arrangements therefor
    • B25D9/18—Valve arrangements therefor involving a piston-type slide valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • the present invention relates to industrial ore mining drill tools and specifically to rock drills that provide percussive and rotary energy to a drill string.
  • Rock drills drive a drill rod (also known as a drill shank) that transmits (via a drill string) rotary and percussive energy to a drill bit which has a working or rock facing end.
  • the drilling tool also supplies flushing medium (commonly air or water) via the drill rod and drill string.
  • a mining rig has a 'central' pump supplying fluid into a 'central' pressurised hydraulic system.
  • Various parts of the rig and rock drill are operated using the pressurised hydraulic system.
  • the 'central' pump may be driven by an electric 'central' motor.
  • the rock drill also has another motor (which may receive hydraulic supply from the 'central' hydraulic system), which generates high speed rotary motion of the drill rod via a gearing arrangement involving an offset drive shaft.
  • the drill rod rotates at speeds of up to around 220 rpm. This rotation is transmitted via the drill string to the drill bit at the rock face to enable holes to be drilled in the rock.
  • Rock drills also generate percussive force on the drill rod, by generating a shock wave that is transmitted via the drill string to the drill bit and rock face.
  • This percussive force or shock wave is generated by impact force from an impact piston (housed in an impact body) aligned on the same axis as the drill rod.
  • the impact piston is hydraulically driven back and forth so that an end impacts an end of the drill rod.
  • the hydraulic driving circuit is usually supplied by the 'central' hydraulic system. Force on the order of 2.8 tonnes at 60 Hz is typical.
  • a damping body cushions the chuck holding the end of the drill rod.
  • Such rock drills are frequently required to drive a drill string of around 3 to 6 metres weighing around 35 kilograms. Depending on the nature of the rock, they may drill through up to around 60 metres of rock per hour.
  • the rock drill is advanced along a beam towards the rock face, keeping the tip of the drill bit in contact with the working face.
  • the drill bit rotation and percussive Shockwaves break up the rock face, in some circumstances fluidising the rock at the tip of the drill bit.
  • Rock drills suffer from numerous problems in actual operation. The operating conditions are difficult and dirty, the loads and forces involved are significantly high, and a number of failure modes are common.
  • the pressure experienced at the rock face is related to these parameters and also experienced by the rock drill damping body. This is known as the back pressure.
  • the back pressure experienced by the drill is thus related to these parameters.
  • the main way in which back pressure is affected is by a change in the actual rock - hard rock will provide high back pressure as the drill tip advances along the beam against the hard rock.
  • the rock is soft, but the drill is set for hard rock and the drill tip advances at a hard rock rate, there is an almost total loss in back pressure as rock is cracked or fluidised at a greater distance in advance of the drill bit tip in soft rock than in hard rock, resulting in the drill bit tip working against a non-resistive substance rather than a surface against which pressure may be exerted.
  • the drill rod associated with the rock drill in use is held in a chuck. Rotation of the chuck is generated via a gear box, thus rotating the drill rod.
  • the chuck is cushioned against backpressure and vibration by a damping body.
  • the chuck presses against a damping piston located in a hydraulic fluid chamber in the damping body, acting as the cushion.
  • This damping fluid chamber is independent of the 'central' hydraulic fluid system - movement of the damping piston simply increases or decreases pressure to absorb the vibration and backpressure. In this way, the forces exerted during operation are, to the extent possible, isolated from the main parts of the drill or at least are damped.
  • a loss in back pressure causes the chuck to move forward relative to the damping body and impact body, moving the end of the drill rod forward away from the impact body and thus changing the impact piston stroke length to a longer throw.
  • an even higher impact force is then applied to the drill rod. This increases the force at the rock face, further reduces the back pressure and an over-stroking loop quickly develops.
  • the impact piston throw increases but since there is no back pressure through the drill rod the frequency may also increase.
  • a first aspect of the invention provides a rock drill including:
  • a first fluid circuit 70 suppliable with fluid via the first control valve 80 b) a first fluid circuit 70 suppliable with fluid via the first control valve 80; c) an impact piston 66 driveable by fluid pressure in the first fluid circuit 70; d) a plurality of first fluid circuit feedback paths 72 from the impact piston 66 to the control valve 80;
  • a damping body 50 for damping backpressure from a rock face e) a damping body 50 for damping backpressure from a rock face; f) a damping fluid chamber 52, associated with the damping body 50;
  • the stroke length of the impact piston is automatically adjustable or controllable in response to a change in drill backpressure communicated to the damping body fluid chamber. Problems associated with sensitive electronic detection and control equipment are avoided. The lack of automatic response, loss of manual pins, and the dirt and contamination problems associated with manual reconfigurations are avoided - the fluid circuits may be sealed during normal field use, rather than being vulnerable to contamination when parts are changed over.
  • said stroke length control mechanism 91 is hydraulically actuable by fluid pressure in the second fluid circuit 56 to hydraulically open and/or close said plurality of first fluid circuit feedback paths 72 to adjust the driveable stroke length of said impact piston 66.
  • said stroke length control mechanism 91 includes an actuator piston 94 in fluid communication with and actuable by fluid pressure in the second fluid circuit 56.
  • said stroke length control mechanism 91 includes an adjustor pin 92 driveable by the actuator piston 94, whereby movement of the adjustor pin 92 opens and/or closes said plurality of first fluid circuit feedback paths 72.
  • said adjustor pin 92 is in fluid communication with the first fluid circuit 70.
  • said adjustor pin 92 has a balancing port 92b.
  • said actuator piston 94 has a balancing port 94b.
  • said stroke length control mechanism 91 includes a return spring 95.
  • the rock drill has four forward first circuit fluid feedback paths 72 and two rearward first circuit fluid feedback paths 72.
  • a second aspect of the invention provides a rock drill including:
  • a stroke length control mechanism 91 in fluid communication with each of the first fluid circuit and the second fluid circuit, the stroke length control mechanism 91 actuable by fluid pressure in the second fluid circuit 56 to reconfigure fluid paths in the first fluid circuit 70; whereby the driveable stroke length of the impact piston 66 is automatically adjustable in response to backpressure from the rock face.
  • a third aspect of the invention provides a rock drill including:
  • a stroke length control mechanism 91 hydraulically actuable by fluid pressure in the second fluid circuit 56 to hydraulically open and/or close fluid paths in the first fluid circuit 70;
  • a fourth aspect of the invention provides a method of adjusting the drivable stroke length of an impact piston 66 in a rock drill, the method including the steps of:
  • Figure 1 is a perspective view of a rock drill according to an embodiment of the invention, mounted upon a cradle movable along a beam;
  • Figure 2 is a front elevation of the embodiment of Figure 1 ;
  • Figure 3 is a cross-sectional view of the embodiment of Figure 2, taken along the line A-A on Figure 2;
  • Figure 4 is a cross-sectional view of the embodiment of Figure 2, taken along the line B-B on Figure 2;
  • Figure 5 is a detail view of part of Figure 4.
  • Figure 6 is an exploded view of the embodiment of Figure 1 ;
  • Figure 7a is a sectional and schematic view of the impact piston and associated hydraulic driving circuit, in which the stroke adjustor is shown in a minimum stroke position;
  • Figure 7b is a sectional and schematic view of the impact piston and associated hydraulic driving circuit, in which the stroke adjustor is shown in an intermediate stroke position;
  • Figure 7c is a sectional and schematic view of the impact piston and associated hydraulic driving circuit, in which the stroke adjustor is shown in a maximum stroke position;
  • Figure 8 is a schematic of a hydraulic circuit according to an embodiment of the invention.
  • Figure 9 is a block diagram of a method according to an embodiment of the invention.
  • Figures 1 and 2 show a rock drill 2 in drill operation configuration, the drill 2 having a front head 20, cover plate 30, housing of a rotation generation mechanism or gear box 40, a percussive or back pressure damping mechanism for damping a drill rod (also known as back pressure damping body 50), stroke adjustor 90 for adjusting the stroke length of an impact piston 66 and impulse generating mechanism or impact body 60. They are supported on cradle assembly 1 10, which in operation moves longitudinally along a beam 120. A drill rod or shank adaptor 10 associated with the rock drill is also shown in the operational position. In use, drill rod 10 is connected to a drill string (not shown) for transmission of rotary motion and percussive force to a drill bit (not shown) working at a rock face.
  • a drill string not shown
  • percussive force to a drill bit (not shown) working at a rock face.
  • the rock drill 2 advances along the beam 120 to keep the tip of the drill bit (not shown) under pressure at the rock face. As rock is fluidised, the rock drill continues to move forward, drilling a hole in the rock. When the drill 2 has advanced to the forward end of the beam 120 it is repositioned at the rear end, and the beam and drill string reconfigured to recommence operations.
  • the drill rod or shank adaptor 10 is held by a drill chuck 42.
  • the drill chuck 42 is rotatable about the central drill axis 4, and can also move through a limited range longitudinally along the drill axis 4.
  • the drill chuck 42 moves in a limited range forwardly or rearwardly relative to the back pressure damping body 50 along the longitudinal axis 4, in response to the back pressure, i.e. the pressure at the working rock face.
  • the back pressure, and vibrational forces or percussive shock imparted to and reflecting from the working face are as far as possible isolated or damped from the rest of the drill by back pressure damping body 50. These vibrational forces may also be known as reflex waves.
  • a rotary drive shaft 46 drives gearbox 40 having cover plate 30, gears 48 and tapered thrust bearings 47,49. This in turn drives chuck 42 and drill rod 10.
  • the front head 20 has a flushing seal carrier 150 via which flushing medium is supplied to the hollow centre 12 of the drill rod 10.
  • Back pressure damping body 50 has or is associated with a back pressure damping fluid chamber 52, and a damping piston 54.
  • the damping piston 54 is longitudinally aligned with the drill chuck 42 and is driven by the drill chuck 42. As the drill chuck 42 moves rearwardly along the longitudinal axis 4 due to the back pressure transmitted through the drill rod 10, the damping piston 54 also moves rearwardly and compresses the cushioning hydraulic fluid in the back pressure damping fluid chamber 52. The greater the compression, the greater the pressure in the damping fluid chamber and the greater the resistance to further movement in a rearward direction. Where the back pressure is low or none, the damping piston 54 is driven to a forward position by the hydraulic fluid.
  • the longitudinal movement of the drill chuck 42 thus changes the position of the drill rod 10 relative to the impact body 60 and impact piston 66.
  • the back pressure damping fluid chamber 52 is a generally annular chamber extending around the impact piston 66, and that the damping piston 54 also extends in an annular manner around the impact piston 66.
  • the damping body 50 and its associated back pressure damping chamber 52 are not in fluid communication with any hydraulic circuits associated with the motor for driving the gear box 40.
  • the impact piston 66 is driven by fluid in a fluid circuit 70 which in this embodiment is a hydraulic circuit receiving pressure supply from a 'central' hydraulic system (not shown).
  • the terms “driving fluid circuit” 70 and “first fluid circuit” 70 are used herein to distinguish it from the “damping fluid circuit” 56 (also referred to as “second fluid circuit” 56) associated with the back pressure damping chamber 52.
  • the “damping fluid circuit” 56 is isolated from the driving fluid circuit and does not receive pressure supply from the 'central' hydraulic system, but rather pressure changes are due to movement of the damping piston 54, responding to the drill chuck holding drill rod 10.
  • Use of the term “driving fluid circuit” 70 should not be taken to require a particular fluid path of the paths within that circuit to drive an impact piston.
  • the hydraulic driving fluid circuit 70 has an associated control valve, being first spool valve 80 which is not visible in Figures 4 and 5.
  • the impact piston 66 is driven forward and rearward within impact piston housing 60 at around 60Hz. Fluid is supplied through the first control spool valve 80 into the impact piston housing 60 via ports 210 or 214 and drives the impact piston 66. Fluid is returned from the impact piston 66 via ports 210, 21 1 and/or 214.
  • the position of the 6 port, 2 position spool determines the path through which fluid is supplied and thus the direction of travel of the impact piston 66.
  • the control spool valve 80 has pressure supply port 202, and return or drain ports 201 and 203. It also has working side ports 204, 205 and 206, through which fluid is supplied to and returned from the impact piston 66.
  • the spool valve 80 is a directional valve in which a position change is triggered via fluid flow to end port 207 or 208.
  • a change in direction of the impact piston 66 is triggered by hydraulic feedback from the impact piston 66 caused by opening and closing of a forward and a rearward port such as forward ports 215, 216, 217, 218 and rearward ports 212, 213 due to movement of the impact piston 66.
  • the feedback to a respective end 207, 208 of the spool valve 80 causes the spool to move to another position.
  • a regulating pin can be used to block or open a fluid path to reconfigure the circuit, determines which port is connected and thus the impact piston stroke length.
  • the stroke adjustor 90 includes a stroke length control mechanism 91 , in this embodiment a hydraulic control valve also referred to herein as stroke length control valve 91 , second control valve 91 or switch 91.
  • the stroke length control valve 91 includes a stroke adjustor pin 92, residing in adjustor housing 98, an actuator or stroke adjustor piston 94 for driving the pin 92 and a return spring 95.
  • the stroke length control mechanism 91 is operable to reconfigure the driving fluid circuit. Movement of the pin 92 opens and / or closes the first fluid circuit feedback paths 72. The position of the hydraulically driven stroke adjustor pin 92 controls or switches the forward feedback fluid path through which hydraulic fluid will travel in the driving fluid circuit 70.
  • the four forward feedback ports 215, 216, 217, and 218 in impact housing 60 are spaced at a distance from the two rearward feedback ports 212, 213 that, in conjunction with the configuration of the impact piston 66, they provide an adjustment in the impact piston stroke length of 0mm, 9mm, 17.5mm, 31 mm respectively.
  • the impact piston 66 may have any of four stroke lengths corresponding to the four forward fluid ports 220, 221 , 222 and 223 in impact housing 98.
  • Each of the four forward feedback ports 215, 216, 217, and 218 has a respective fluid path connecting to respective ports 220, 221 , 222 and 223 in adjustor pin housing 98.
  • the adjustor pin position determines which of ports 220, 221 , 222 and 223 are open to connect to directional feedback take-off 224 and thus to fluid path 224-207 to supply pressure to the first control valve 80 at the forward end of the spool to trigger a spool position change and thus an impact piston direction change.
  • the impact piston 66 is triggered in a direction change when the fluid path connecting ports 215-220 is open at both ends, and thus has a shorter stroke length than in Figure 7b where a direction change is not triggered until the impact piston 66 has travelled far enough to open fluid path 216-221 , as in Figure 7b fluid path 215-220 is blocked by the stroke adjustor pin 92.
  • a maximum stroke length is obtained in Figure 7c as the impact piston 66 moves until it opens fluid path 218-224, as the adjustor pin 92 blocks fluid paths 215-220, 216-221 , and 217-222.
  • the stroke adjustor pin 92 is driven by an actuator or stroke adjustor piston 94, located in housing 96 (see Figure 5).
  • the stroke adjustor piston 94 has an associated return spring 95. Where the pressure in the damping fluid chamber 52 is increased, fluid from the damping fluid chamber 52 will flow through damping fluid path 56 into piston housing 96 at an end zone 97 via port 225, hydraulically driving the piston 94 against the return spring 95. This also drives the adjustor pin 92. Movement of adjustor pin
  • the stroke adjustor piston 94 has a working face which together with an end wall of the piston housing 96 defines an end zone 97, into which damping fluid path 56 enables passage of damping fluid from the damping chamber 52.
  • the working face of the piston 94 is prevented from "sticking" to the end wall of the housing by the left end of stroke adjustor pin 92 reaching its maximum travel within adjustor housing 98, preventing the piston 94 from contacting the end wall.
  • the stroke adjustor piston 94 has a return spring 95 which seats against piston shoulder 94a.
  • the piston 94 also has a balancing port 94b, being a hollow centre channel that functions as a passage through the piston 94, from the end zone 97 side of the piston 94 to the return spring 95 side of the piston 94.
  • the balancing port 94b allows equalisation of fluid pressure to either side of the piston 94, which can significantly reduce the force acting on the return spring 95. The fatigue life of the return spring 95 can thus be significantly increased.
  • the stroke adjustor piston housing 96 has seals 99 between it and the adjustor pin housing 98, which prevent damping fluid from exiting the housing 96 while allowing the piston 94 to extend into the adjustor pin housing 98 and drive the adjustor pin 92
  • the adjustor pin housing 98 has a small stepped shoulder 98a which defines a first end zone 93a.
  • the adjustor pin 92 also has a piston shoulder 92a which in the maximum stroke position shown in Figure 7c is seated against the end wall of the housing 98. When not in the maximum stroke position the shoulder 92a and housing 98 define a second end zone 93b, as viewed in Figures 7a and 7b.
  • the stroke adjustor pin 92 also has a balancing port 92b as shown in Figures 7a, 7b and 7c, being a hollow centre channel that functions as a passage through the pin 92 from the first end zone 93a side to the second end zone side 93b.
  • the balancing port 92b allows equalisation of fluid pressure to either side of the adjustor pin 92, which alleviates the effect of high percussion pressure in the driving or first fluid circuit acting on stroke adjustor pin 92 as the impact piston 66 is operated.
  • the stroke adjustor mechanism is primarily controlled or affected by pressure in the damping or second fluid circuit i.e. back pressure.
  • damping fluid circuit including damping fluid chamber 52 and damping fluid path 56 is a separate fluid circuit from the driving fluid circuit 70 - the stroke adjustor piston 94 and stroke adjustor pin 92 have associated seals preventing leaks from one system to the other.
  • hydraulically actuated stroke length control mechanism or switch 91 (including stroke adjustor pin 92), is directly responsive to changes in pressure in the damping fluid chamber, enabling the stroke length of the impact piston to be automatically and hydraulically adjusted during operations.
  • This can avoid the over- stroking feedback loop which causes problems in the prior art, since stroke length is continually adjusted according to back pressure.
  • the hydraulic operation avoids the need for expensive and delicate electronic instrumentation and controls to shut down the drill if it over-strokes.
  • the embodiment disclosed has four fluid paths defining four stroke length settings. However, greater or fewer fluid paths could be provided to change the number of stroke length settings available, and the difference in stroke length enabled by each path may be selected to suit particular requirements.
  • driving fluid circuit 70 stroke length control mechanism 91 , adjustor pin 92, impact piston 66 and spool valve 80 can be made in a variety of configurations.
  • size and location of cavities defined between the impact piston and its housing, or between the adjustor pin and its housing, type and configuration of the directional valve and the location of fluid ports may be varied in a number of ways to achieve the same or similar result. The above is thus a description of one embodiment of such a driving fluid circuit.
  • the arrangement of the damping fluid circuit 56 can also be made in a variety of configurations. Depending on mechanical configuration, the stroke length control mechanism 91 could be located directly adjacent the damping fluid chamber 52 and remove the need for a conduit, fluid channel or path between chamber 52 and piston 94. Nonetheless, in such a case the clamping chamber 52 is considered to comprise the second fluid circuit 56.
  • Figure 9 shows a block diagram of a method of adjusting the driveable stroke length of an impact piston.
  • fluid pressure in the damping chamber 52 alters in response to movement of the drill rod due to rock backpressure.
  • the fluid pressure change hydraulically actuates the stroke length control mechanism 92 to a new position via the damping fluid circuit 56.
  • movement of the adjustor pin 92 in the mechanism 92 opens and/or closes forward feedback paths 72 connected to ports 215, 216, 217 and 218 in the driving fluid circuit 70. This adjusts the paths and ports through which fluid is fed back to the control valve 80 that triggers a direction change to the impact piston, and thus the position of the impact piston when a direction change is triggered.
  • the driveable stroke length of the impact piston is hydraulically adjusted in response to rock face back pressure in the damping body.

Abstract

La présente invention concerne un fleuret de mine qui comprend une première vanne de commande (80), un premier circuit de fluide (70) qui peut être alimenté en fluide par l'intermédiaire de la première vanne de commande (80), un piston à percussion (66) qui peut être entraîné par une pression de fluide dans le premier circuit de fluide, une pluralité de trajets de retour du premier circuit de fluide (72) allant du piston à percussion (66) à la vanne de commande (80), un corps d'amortissement (50) pour amortir la contre-pression provenant d'une paroi rocheuse, une chambre de fluide d'amortissement (52), associée au corps d'amortissement (50). Ledit fleuret de mine est caractérisé par un second circuit de fluide (56) en communication fluidique avec la chambre de fluide d'amortissement (52) et un mécanisme de réglage de longueur de course (91) qui peut être actionné par une pression de fluide dans le second circuit de fluide (56), l'écoulement de fluide dans lesdits trajets de retour du premier circuit de fluide (72) pouvant être régulé par le mécanisme de réglage de longueur de course (91), la longueur de course sur laquelle peut avancer ledit piston à percussion (66) pouvant être réglée.
PCT/AU2011/000220 2010-09-10 2011-02-28 Fleuret de mine amélioré WO2012031311A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US13/819,389 US20140144660A1 (en) 2010-09-10 2011-02-28 Rock drill
EP11822919.4A EP2614217A4 (fr) 2010-09-10 2011-02-28 Fleuret de mine amélioré
AU2011301130A AU2011301130A1 (en) 2010-09-10 2011-02-28 Improved rock drill
CA2810914A CA2810914A1 (fr) 2010-09-10 2011-02-28 Fleuret de mine ameliore
JP2013527422A JP2013537266A (ja) 2010-09-10 2011-02-28 改良した削岩機
CN2011800433623A CN103097654A (zh) 2010-09-10 2011-02-28 改进的凿岩钻机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2010904066 2010-09-10
AU2010904066A AU2010904066A0 (en) 2010-09-10 Improved rock drill

Publications (1)

Publication Number Publication Date
WO2012031311A1 true WO2012031311A1 (fr) 2012-03-15

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Application Number Title Priority Date Filing Date
PCT/AU2011/000220 WO2012031311A1 (fr) 2010-09-10 2011-02-28 Fleuret de mine amélioré

Country Status (8)

Country Link
US (1) US20140144660A1 (fr)
EP (1) EP2614217A4 (fr)
JP (1) JP2013537266A (fr)
CN (1) CN103097654A (fr)
AU (1) AU2011301130A1 (fr)
CA (1) CA2810914A1 (fr)
CL (1) CL2013000658A1 (fr)
WO (1) WO2012031311A1 (fr)

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WO2015039162A1 (fr) * 2013-09-23 2015-03-26 Rockdrill Services Australia Pty Ltd Dispositif à percussion

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EP3100828B1 (fr) * 2014-01-31 2021-09-22 Furukawa Rock Drill Co., Ltd. Dispositif de martelage hydraulique
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US10370900B2 (en) 2015-07-31 2019-08-06 Tei Rock Drills, Inc. Remote control of stroke and frequency of percussion apparatus and methods thereof
EP3508308B1 (fr) * 2016-08-31 2022-08-17 Furukawa Rock Drill Co., Ltd. Dispositif de percussion hydraulique

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See also references of EP2614217A1 *

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WO2015039162A1 (fr) * 2013-09-23 2015-03-26 Rockdrill Services Australia Pty Ltd Dispositif à percussion

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CN103097654A (zh) 2013-05-08
JP2013537266A (ja) 2013-09-30
CL2013000658A1 (es) 2013-08-23
US20140144660A1 (en) 2014-05-29
AU2011301130A1 (en) 2013-03-07
EP2614217A4 (fr) 2015-10-07
CA2810914A1 (fr) 2012-03-15
EP2614217A1 (fr) 2013-07-17

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