US3620312A - Rock drill - Google Patents

Rock drill Download PDF

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Publication number
US3620312A
US3620312A US826923A US3620312DA US3620312A US 3620312 A US3620312 A US 3620312A US 826923 A US826923 A US 826923A US 3620312D A US3620312D A US 3620312DA US 3620312 A US3620312 A US 3620312A
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US
United States
Prior art keywords
hydraulic fluid
piston
hammer
cylinder
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US826923A
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English (en)
Inventor
Eugene L Krasnoff
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.)
Ingersoll Rand Co
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Ingersoll Rand Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ingersoll Rand Co filed Critical Ingersoll Rand Co
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Publication of US3620312A publication Critical patent/US3620312A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S173/00—Tool driving or impacting
    • Y10S173/04—Liquid operated

Definitions

  • Thomson ABSTRACT A hydraulically powered impact tool particularly useful for rock drilling.
  • the percussive tool is valveless with the hammer controlling the inflow and exhaust of motive liquid.
  • the drill is powered by liquid under pressure from an outside source and from energy stored in storage chambers. Tanks positioned in the inlet and exhaust lines of the tool reduce pressure surges in the inlet and exhaust lines of the tool.
  • This invention relates to a liquid pressure powered reciprocating machine and more particularly to a liquid pressure actuated rock drill.
  • liquid as a motive fluid
  • Conventional liquid actuated drills and impact tools use a separate valve such as a spool valve to direct high-pressure liquid to produce the reciprocating motion in the hammer. Too, the use of such valving tends to result in a rather complex machine.
  • the valving is likely to lead to pressure waves in the inlet and exhaust lines. This can result in poor and unstable valve and hammer motion, loss of energy and cavitation in both the inlet and exhaust lines and in the working cylinder. These problems are usually attributed to the low compressibility of the working fluid.
  • an impact tool which comprises a casing defining a cylinder; a hammer disposed for reciprocal movement within the cylinder and adapted to deliver an impact to a workpiece.
  • the hammer defines with the casing at least one chamber.
  • There is means for reciprocating the hammer including means for periodically pressurizing said chamber.
  • There is energy storage means containing hydraulic fluid and communicating with said chamber through a port separate from said means for pressurizing said chamber for alternately receiving energy from said chamber and releasing energy to said chamber.
  • FIG. I is a perspective view of a rock-drilling apparatus employing one embodiment ofthe present invention.
  • F IG. 2 is a longitudinal sectional view of a portion of a rock drilling embodying the present invention with the hammer shown in the impacting position;
  • FIG. 3 is a sectional view on an enlarged scale taken on the line 33 of FIG. 2 showing the hammer of the rock drill of the present invention at the beginning of the working stroke;
  • FIG. 5 is a fragmentary detail showing a modification of the present invention.
  • FIG. 1 shows a rock drill of a drifter type and is generally indicated at I.
  • the drill is suitably mounted on a supportingapparatus 2 of any desired type.
  • the drill 1 includes a casing 4 having a central portion 5 having a longitudinal passage 6 therethrough.
  • a sleeve 7 is mounted within the passage 6 and together with the casing 4 defines a cylinder 8.
  • a hammer or piston 10 is mounted for reciprocal movement within the cylinder 8.
  • the hammer 10 includes an enlarged diameter portion 11 which divides the cylinder 8 into a pair of chambers 8a and 8b.
  • a backhead 9 closes one end of the cylinder 8 and a fronthead 12 is mounted on the forward end of the drill.
  • a spacer 13 is positioned between the fronthead 12 and casing 4. The backhead 9 and fronthead 12 are held on the casing 4 by means of bolts 14.
  • a drill steel 15 having a drill bit 16 secured to one end is mounted in the fronthead 12 and extends into the forward end of the cylinder 8 where it is adapted to be struck by the hammer 10 as the hammer reciprocates.
  • a centralizer I7 is mounted on the supporting structure 2 for guiding the drill steel 15.
  • Suitable apparatus for rotating the drill steel 15 has been provided.
  • Such apparatus includes a rotary motor 20 mounted on the drill 1.
  • the drive shaft 21 of the motor 20 rotates a spur gear 22 suitably mounted by means of bearings in the fronthead 12 of the drill.
  • the spur gear 22 meshes with spur gear 23 which drives a spur gear 24.
  • the gear 24 meshes with gear teeth 25 on a chuck 27.
  • the chuck 27 is drivingly connected to a chuck jaw 29 which is provided with internal splines which mesh with splines 30 on the drill steel 15.
  • a retainer 32 holds the chuck jaw 29 and drill steel 15 in the fronthead of the machine.
  • a cap 33 is threadedly secured to the fronthead 12 to hold the retainer 32 in position.
  • Air passages have been provided in the fronthead of the machine for supplying air under pressure to the bottom of the hole being drilled for blowing cuttings out of the hole. Air under pressure is supplied from a conduit 35 to a passage 36 in the fronthead of the machine. The passage 36 leads to an annular space 38 in the fronthead of the machine. A plurality of radial passages 39 are provided in the retainer 32 and lead to an annular passage 40 surrounding the drill steel 15.
  • the drill steel 15 is provided with a longitudinal passage 41 and a radial passage 42 for receiving air from the annular passage 40 and conducting it to the bottom of the hole being drilled.
  • the central portion 5 of the casing 4 is provided with a plurality of annular passages. These passages have been designated by the numerals 50, SI, 52, 53, 54 and 55 proceeding from the back of the machine toward the front of the machine.
  • the sleeve 7 is provided with radial passages which communicate with the annular passages in the casing 6. These passages have been designated 70, 71, 72, 73, 74 and 75 proceeding from the back of the machine toward the front of the machine. Passages 72, 73, 74 and 75 each terminate in an annulus 60, 61, 62 and 63. respectively.
  • a second sleeve 78 is positioned within the sleeve 7 towards the back of the machine and is dimensioned to receive a portion of the hammer 10.
  • the sleeve 7 is provided with an enlarged portion 79 at its forward end dimensioned to receive the forward portion of the hammer 10.
  • the sleeve 78 is provided with radial passages 80 which terminate in an annulus 82 and radial passages 81 which terminate in an annulus 83.
  • the passages 80 and 81 communicate with the radial passages 70 and 71 in the sleeve 7 and annular passages 50 and SI in the casing 5.
  • the casing 4 includes a pair of outboard energy storage chambers and 91. These energy storage chambers are closed at their ends by plugs and 96.
  • Energy storage chamber 90 communicates with cylinder 8 through a port 94, annular passage 54 and radial passage 74.
  • Energy storage chamber 91 communicates with the cylinder 8 through a port 92, annular passage 52 and radial passage 72.
  • the hammer is provided with rows of circumferentially spaced longitudinal slots. These rows of slots have generally been indicated 64, 65, 66, 67 and 68 proceeding from the back of the hammer 10 toward the front. Although slots have been shown, the slots may be replaced by reduced diameter portions extending around the complete circumference of the hammer. The selection of slots as shown or a reduced diameter portion depends upon the particular machine and the fluid flow desired.
  • the drilling machine is further provided with pressure wave filtering tanks 100 and 101.
  • the second tank 101 is a duplicate of the tank 100 in size and, shape and is positioned next to the tank 100, as can be seen from FIG. 1.
  • the inlet tank 100 is provided with a conduit 103 for conducting hydraulic fluid under pressure from a suitable source'such as a reservoir and pump (not shown) to the interior of the tank 100.
  • a pair of conduits 110 and 111 are positioned in the tank 100 for conducting fluid from the tank 100 to opposite sides of the enlarged portion 11 of the hammer 10.
  • a conduit 121 is positioned in the tank 101 for exhausting fluid from both chambers formed on opposite sides of the enlarged portion 11 of the hammer 10.
  • the outlet tank 101 is provided with a conduit 104 for conducting the hydraulic fluid back to the reservoir.
  • Motive power for driving the hammer 10 forward to deliver an impact to the drill steel is supplied from energy stored in the chamber 91 and from the flow of hydraulic fluid through the inlet 103, filter wave tank 100 and inlet conduit 110.
  • Motive power for raising the hammer is supplied from energy stored in the chamber 90 and from the flow of fluid through inlet 103, filter wave tank 100 and inlet conduit 1 1 1.
  • Hydraulic fluid such as oil under pressure is supplied from the line 103 to the tank 100.
  • the oil under pressure flows through the conduit 111 in the tank 100 and through a port 1 15 in the casing portion 6 to the annular passage 55. From the annular passage 55, the fluid under pressure passes through the radial ports 75 and annulus 63 in the sleeve 7 to the row of slots 68.
  • Fluid passes through the slots 68 to the chamber 80 formed on the forward side of enlarged portion 11 and acts on a shoulder 11a defined by the enlarged diameter portion 11 to move the hammer 10 rearwardly; i.e., toward the backhead 9. Since energy storage chamber 90 is always in communication with chamber 8a through port 94 and passages 54, 74, and 62, fluid flows into the energy storage chamber 90 to pressurize it and thereby store energy.
  • Fluid under pressure now flows from tank through conduit 110, port 116, annular passage 51, passages 71, annulus 83 and through slots 65 to act on shoulder 11b.
  • the hammer 10 reverses its direction of movement and is driven forward by pressure in chamber 8b to deliver an impact to the drill steel 15.
  • energy storage chamber 91 is always in communication with chamber 8b, the fluid under pressure from the inlet tank 100 also serves to further increase the pressure in energy storage chamber 91 and hence further increase the energy stored in the chamber 91.
  • chamber 80 is exhausted through slots 67, annulus 61, port 73 and passage 53 to outlet port 122 which leads to conduit 121 positioned in outlet filter wave tank 101.
  • the motive fluid is then exhausted from tank 101 through conduit 104.
  • the cycle is repeated in rapid succession to deliver repeated impact blows to the workpiece.
  • a portion 131 of the cylinder 8 above the hammer may be filled with air or a hydraulic fluid.
  • a passage for supplying fluid to chamber 131 is opened upon delivering an impact to the workpiece so that a charge of whatever fluid fills chamber 131 will make up for any leakage which may occur.
  • the passage 130 is closed.
  • the fluid in the chamber 130 is compressed.
  • the energy stored in chamber 131 is transferred to the hammer to increase the impacting force at which the hammer strikes the workpiece.
  • an overtravel safety apparatus includes means for conducting fluid from the working side of the hammer to the accumulator 91 to thereby reduce the pressure on the working side of the hammer below that in the return side of the hammer. If overtravel occurs, the slots 64 will provide communication between inlet port 81 and port 80. Fluid under pressure will travel through radial port 70 and annular passage 50 to passage 135 which leads to the accumulator 91. The length and diameter of the passage 135 are important to the operation of the overtravel safety apparatus to insure that pressure fluctuations and cavitation do not occur.
  • an intensifier such as that shown in FIG. 5 may be used.
  • a chamber 150 is filled with hydraulic fluid.
  • An intensifier piston 151 has a first diameter portion 152 and a second enlarged diameter portion 153.
  • the enlarged diameter portion communicates with the cylinderB through a passage 154. If the passage 154 is in communication with annular passage 54, when the hammer moves forward, fluid under pressure acts on piston portion 153 causing the piston 151 to move downward and pressurize the chamber 150.
  • the stored energy in chamber 150 is released to the cylinder 3 by acting on reduced diameter end 152 to move the piston 151 up.
  • a charging port 155 may be provided to replace liquid which may leak from the chamber 150.
  • a hydraulically powered actuator comprising:
  • a piston mounted for reciprocal movement within the cylinder and having a pressure surface thereon;
  • supply means for supplying hydraulic fluid under pressure into the cylinder to act on such surface to move the piston in one direction and exhaust means for exhausting the hydraulic fluid from the cylinder;
  • hydraulic fluid energy storage means having constant com munication with a surface on said piston such that the pressure of hydraulic fluid therein continuously urges the piston in said direction and having communication with said supply means;
  • valve means operatively associated with said supply means and exhaust means and actuated so that hydraulic fluid is supplied into the cylinder to move the piston in said one direction and to pressurize the hydraulic fluid energy storage means during a first part of the piston travel from an initial position, then cuts off the supply of hydraulic fluid to the cylinder and the hydraulic fluid energy storage means during a second part of its travel from the initial position so that thereafter only the hydraulic fluid energy stored in the energy storage means moves the piston, and then during the last part of its travel, hydraulic fluid is exhausted from the hydraulic fluid energy storage means;
  • compression means adapted to be compressed by the piston as the piston travels in said one direction to its final positron.
  • a hydraulically powered actuator in accordance with claim 1 wherein the piston has a shoulder defining said pressure surface and said surface is continuously exposed to the pressure of hydraulic fluid in the energy storage means and said piston is provided with rows of circumferentially spaced slots and dimensioned to serve as the valve means so that the hydraulic fluid fed into the cylinder flows through one row of circumferentially spaced slots and against said shoulder surface during the first part of the travel of the piston from an initial position and hydraulic fluid is exhausted through another row of circumferentially spaced slots during the last part of the travel of the piston.
  • a hydraulically powered actuator in accordance with claim 1 in which said valve means is actuated when the piston is moved in the opposite direction to first continue the exhaust of hydraulic fluid, then close such exhaust so that hydraulic fluid in the energy storage means is pressurized by movement of the piston, and thereafter opens the supply means to further pressurize the hydraulic fluid in the energy storage means.
  • valve means is actuated to open the supply means in the event the piston during the last part of its travel is said one direction moves beyond a predetermined position.
  • a hydraulically powered actuator comprising:
  • first and second hydraulic fluid energy storage means located so that a first surface and a second surface of the piston are continuously exposed to hydraulic fluid in the first and second hydraulic fluid energy storage means, respectively; said piston being shaped so that hydraulic fluid fed into the cylinder to move the piston in one direction pressurizes the hydraulic fluid energy storage means during a first part of its travel from an initial position, then directly cuts off the flow of hydraulic fluid to the hydraulic fluid energy storage means during a second part of its travel from the initial position so that thereafter only the hydraulic fluid energy stored in the first energy storage means and acting against said first piston surface moves the piston, and after the beginning of said second part of its travel, permits hydraulic fluid to be fed into the cylinder to later move the piston in the other direction.
  • a hydraulically powered actuator in accordance with claim 6 wherein the surfaces of the piston continuously exposed to hydraulic fluid in the hydraulic fluid energy storage means are shoulders and said piston is provided with rows of circumferentially spaced slots located on the piston and dimensioned so that the hydraulic fluid fed into the cylinder flows through a row of circumferentially spaced slots and against a shoulder during the first part of the travel of the piston from an initial position.
  • Apparatus for delivering an impact to a workpiece comprising:
  • a casing defining a cylinder; a hammer disposed for reciprocal movement within the cylinder and adapted to deliver an impact to a workpiece;
  • said hammer defining with said cylinder a pair of chambers with one of said chambers containing hydraulic fluid to move the hammer in one direction and said casing having a port extending from the other of said chambers;
  • said hammer being shaped to directly control the supply of hydraulic fluid into said other chamber to thereby pressurize said other chamber and the energy storage means during a first part of its travel from an initial position and then to directly cut off the flow of hydraulic fluid to said other chamber so that energy stored in the energy storage means is applied against the hammer and is the only force moving the hammer during a second part of its travel from the initial position and to exhaust said other chamber during the last part of its travel in said other direction.
  • compression means are provided in the cylinder and adapted to be compressed by the hammer as the hammer travels from its initial position to its final position.
  • Apparatus for delivering an impact to a workpiece comprising:
  • a hammer disposed for reciprocal movement within the cylinder and adapted to deliver an impact to a workpiece
  • said hammer defining with said cylinder a pair of chambers and said casing having a port extending from each chamber;
  • said hammer being shaped to directly control the feeding of hydraulic fluid into each chamber to thereby pressurize said chamber and its associated energy storage means during a first part of its travel from an initial position and then to directly cut off the flow of hydraulic fluid to said chamber so that energy stored said energy storage means is applied against the hammer during a second part of its travel from the initial position.
  • Fig. 2 delete the passageway, the leading line, and identifying numeral 135.
  • Fig. 3 add a passageway through casing 4 connecting annulus 50 and energy storage chamber 91 giving it a leading line, and identifying numeral 135. Also in Fig. 3, correct the leading line from numeral 81 to the next port leftward. Column 4, line 33, "chamber 9b" should read chamber 8b Signed and sealed this 12th day of December 1972.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Percussive Tools And Related Accessories (AREA)
US826923A 1969-05-22 1969-05-22 Rock drill Expired - Lifetime US3620312A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US82692369A 1969-05-22 1969-05-22

Publications (1)

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US3620312A true US3620312A (en) 1971-11-16

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Application Number Title Priority Date Filing Date
US826923A Expired - Lifetime US3620312A (en) 1969-05-22 1969-05-22 Rock drill

Country Status (8)

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US (1) US3620312A (xx)
JP (1) JPS4932401B1 (xx)
CA (1) CA922208A (xx)
DE (1) DE2022490C3 (xx)
FR (1) FR2048623A5 (xx)
GB (1) GB1302759A (xx)
SE (1) SE363474B (xx)
ZA (1) ZA702286B (xx)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5039601A (xx) * 1973-08-02 1975-04-11
US3918532A (en) * 1974-05-10 1975-11-11 Chicago Pneumatic Tool Co Hydraulic tool
US3918531A (en) * 1974-06-14 1975-11-11 Chicago Pneumatic Tool Co Hydraulic rock drill having automatic carriage feed
US3995703A (en) * 1974-05-20 1976-12-07 Robert Bosch G.M.B.H. Electrohydraulically operated portable power tool
US4282937A (en) * 1976-04-28 1981-08-11 Joy Manufacturing Company Hammer
US4550785A (en) * 1976-04-28 1985-11-05 Consolidated Technologies Corporation Hammer
US4854394A (en) * 1986-05-09 1989-08-08 Oy Tampella Ab Arrangement for supporting of a shank of a drilling machine
US5161624A (en) * 1990-03-19 1992-11-10 Hilti Aktiengesellschaft Tool for driving fastening elements into hard receiving materials
US5662180A (en) * 1995-10-17 1997-09-02 Dresser-Rand Company Percussion drill assembly
US5957220A (en) * 1995-10-17 1999-09-28 Dresser-Rand Company Percussion drill assembly
US20020084110A1 (en) * 1999-07-02 2002-07-04 Jarmo Heinonen Rock drilling and mounting frame
US20030111240A1 (en) * 2001-12-14 2003-06-19 National Institute Of Advanced Industrial Downhole percussion drills
WO2014081372A1 (en) * 2012-11-21 2014-05-30 Atlas Copco Rock Drills Ab Device relating to a flushing head for a rock drilling machine and rock drilling machine
US9724813B2 (en) 2011-04-05 2017-08-08 Atlas Copco Rock Drills Ab Device for rock and-concrete machining

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103410439B (zh) * 2013-08-29 2015-12-02 潍坊天瑞重工凿岩机械有限公司 可冷却橡胶领盘钎肩式六方钎杆的凿岩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1703840A (en) * 1920-01-02 1929-02-26 Sullivan Machinery Co Percussive motor
US2743741A (en) * 1952-09-29 1956-05-01 Techron Ltd Hydraulic accumulator
US3183668A (en) * 1959-11-30 1965-05-18 Hydra Might Company Percussion type rock drills
US3192717A (en) * 1962-06-19 1965-07-06 Keclavite Hydraulics Ltd Hydraulically operated reciprocating apparatus
US3408897A (en) * 1964-11-18 1968-11-05 Champion Inc Fluid power hammer having accumulator means to drive the hammer through its working stroke independent of the system pump
US3468222A (en) * 1966-07-06 1969-09-23 Hugo H Cordes Control for a ramming hammer with hydraulic drive

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1703840A (en) * 1920-01-02 1929-02-26 Sullivan Machinery Co Percussive motor
US2743741A (en) * 1952-09-29 1956-05-01 Techron Ltd Hydraulic accumulator
US3183668A (en) * 1959-11-30 1965-05-18 Hydra Might Company Percussion type rock drills
US3192717A (en) * 1962-06-19 1965-07-06 Keclavite Hydraulics Ltd Hydraulically operated reciprocating apparatus
GB1033739A (en) * 1962-06-19 1966-06-22 Keelavite Hydraulics Ltd Hydraulically-operated reciprocating apparatus
US3408897A (en) * 1964-11-18 1968-11-05 Champion Inc Fluid power hammer having accumulator means to drive the hammer through its working stroke independent of the system pump
US3468222A (en) * 1966-07-06 1969-09-23 Hugo H Cordes Control for a ramming hammer with hydraulic drive

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5039601A (xx) * 1973-08-02 1975-04-11
JPS5410323B2 (xx) * 1973-08-02 1979-05-04
US3918532A (en) * 1974-05-10 1975-11-11 Chicago Pneumatic Tool Co Hydraulic tool
US3995703A (en) * 1974-05-20 1976-12-07 Robert Bosch G.M.B.H. Electrohydraulically operated portable power tool
US3918531A (en) * 1974-06-14 1975-11-11 Chicago Pneumatic Tool Co Hydraulic rock drill having automatic carriage feed
US4282937A (en) * 1976-04-28 1981-08-11 Joy Manufacturing Company Hammer
US4550785A (en) * 1976-04-28 1985-11-05 Consolidated Technologies Corporation Hammer
US4854394A (en) * 1986-05-09 1989-08-08 Oy Tampella Ab Arrangement for supporting of a shank of a drilling machine
AT396079B (de) * 1986-05-09 1993-05-25 Tampella Oy Ab Anordnung fuer eine bohrmaschine zur lagerung und abstuetzung eines einsteckendstuecks
US5161624A (en) * 1990-03-19 1992-11-10 Hilti Aktiengesellschaft Tool for driving fastening elements into hard receiving materials
US5662180A (en) * 1995-10-17 1997-09-02 Dresser-Rand Company Percussion drill assembly
US5957220A (en) * 1995-10-17 1999-09-28 Dresser-Rand Company Percussion drill assembly
US20020084110A1 (en) * 1999-07-02 2002-07-04 Jarmo Heinonen Rock drilling and mounting frame
US6705407B2 (en) * 1999-07-02 2004-03-16 Sandvik Tamrock Oy Rock drilling and mounting frame
US20030111240A1 (en) * 2001-12-14 2003-06-19 National Institute Of Advanced Industrial Downhole percussion drills
US6752222B2 (en) * 2001-12-14 2004-06-22 National Institute Of Advanced Industrial Science And Technology Downhole percussion drills
US9724813B2 (en) 2011-04-05 2017-08-08 Atlas Copco Rock Drills Ab Device for rock and-concrete machining
WO2014081372A1 (en) * 2012-11-21 2014-05-30 Atlas Copco Rock Drills Ab Device relating to a flushing head for a rock drilling machine and rock drilling machine
CN105026680A (zh) * 2012-11-21 2015-11-04 阿特拉斯·科普柯凿岩设备有限公司 与用于凿岩机的冲洗头相关的装置以及凿岩机
CN105026680B (zh) * 2012-11-21 2017-07-07 阿特拉斯·科普柯凿岩设备有限公司 与用于凿岩机的冲洗头相关的装置以及凿岩机
US10145189B2 (en) 2012-11-21 2018-12-04 Epiroc Rock Drills Aktiebolag Device relating to a flushing head for a rock drilling machine and rock drilling machine

Also Published As

Publication number Publication date
GB1302759A (xx) 1973-01-10
DE2022490A1 (de) 1970-11-26
CA922208A (en) 1973-03-06
ZA702286B (en) 1972-02-23
DE2022490C3 (de) 1974-01-10
JPS4932401B1 (xx) 1974-08-30
SE363474B (xx) 1974-01-21
FR2048623A5 (xx) 1971-03-19
DE2022490B2 (de) 1973-06-14

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