EP0203282A1 - Réglage d'un dispositif hydraulique de perforation à percussion - Google Patents

Réglage d'un dispositif hydraulique de perforation à percussion Download PDF

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Publication number
EP0203282A1
EP0203282A1 EP86103012A EP86103012A EP0203282A1 EP 0203282 A1 EP0203282 A1 EP 0203282A1 EP 86103012 A EP86103012 A EP 86103012A EP 86103012 A EP86103012 A EP 86103012A EP 0203282 A1 EP0203282 A1 EP 0203282A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
hydraulic
inlet
rotary motor
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.)
Granted
Application number
EP86103012A
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German (de)
English (en)
Other versions
EP0203282B1 (fr
Inventor
Günter W. Klemm
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.)
Ing G Klemm Bohrtechnik GmbH
Original Assignee
Ing G Klemm Bohrtechnik GmbH
ING GUNTER KLEMM SPEZIALUNTERNEHMEN fur BOHRTECHNIK
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 Ing G Klemm Bohrtechnik GmbH, ING GUNTER KLEMM SPEZIALUNTERNEHMEN fur BOHRTECHNIK filed Critical Ing G Klemm Bohrtechnik GmbH
Priority to AT86103012T priority Critical patent/ATE44303T1/de
Publication of EP0203282A1 publication Critical patent/EP0203282A1/fr
Application granted granted Critical
Publication of EP0203282B1 publication Critical patent/EP0203282B1/fr
Expired 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
    • B25D9/14—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
    • B25D9/265—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof with arrangements for automatic stopping when the tool is lifted from the working face or suffers excessive bore resistance
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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

Definitions

  • the invention relates to a hydraulic hammer drill device with a hydraulic hammer drill, the number of strokes of which can be changed by a control pressure, a hydraulic rotary motor for rotating the drill string acted upon by the hammer drill and with a hydraulic feed device for advancing the drill string, the control pressure being derived from the working pressure of the feed device .
  • the resistance that the rock presents to the drilling device differs. This resistance depends on numerous factors such as the type of rock, the depth of the borehole and the force exerted by the borehole wall on the drill string. If the drilling resistance is low, the hammer drill is operated with a high number of impacts per minute and with relatively low impact energy per individual impact. With high drilling resistance is a low impact rate with high single impact energy appropriate.
  • a known percussion drilling device of the type mentioned at the beginning (DE-OS 31 15 361) automatically changes the percussion frequency and thus also the individual percussion energy as a function of the load condition of the drill string or as a function of the available pressure.
  • the control pressure supplied to the hammer drill is derived either from the pressure of a feed device acting on the drill string. If the drilling resistance is high, the pressure of the feed device increases and thus also the control pressure. This automatically reduces the number of strokes of the hammer drill and increases the single impact energy.
  • the control pressure is generated as a function of the pressure or the load on the rotary motor. In any case, the control pressure depends solely on a single parameter (either the pressure of the feed device or that of the rotary motor).
  • the invention has for its object to design a percussion drilling device of the type mentioned in such a way that the number of impacts is changed depending on the drilling resistance actually occurring, regardless of whether this drilling resistance affects the drilling feed or the rotary drive.
  • the invention provides that the control line carrying the control pressure is connected to a shuttle valve which is the largest of passes through several pending inlet pressures, and that a first inlet pressure of the shuttle valve is derived from the pressure of the feed device and a second inlet pressure is derived from the pressure of the rotary motor.
  • the shuttle valve allows the greater of two pressures present to pass, so that the control pressure which changes the number of strokes of the hammer drill is determined by the greatest of the pressures supplied to the shuttle valve.
  • the rotational resistance increases without the feed resistance increasing accordingly. This is the case, for example, when drilling in tough soils and with a long drill string with a correspondingly high level of friction. In such a situation, the load on the rotary motor increases, so that the increased pressure of the rotary motor takes over the control of the number of strokes.
  • the pressure of the feed device automatically takes over the control of the number of strokes of the hammer drill.
  • the hydraulic percussion drilling device adjusts itself to the type of drilling resistance.
  • the control in the control of the stroke rate is carried out by the drive which is exposed to the greatest load.
  • the inlet pressure of the shuttle valve is supplied by the auxiliary pressure source, which is controlled as a function of the pressure of the one unit by the pressure relief valve.
  • the pressure relief valve can either set the pressure as a linear function of the pressure of the drive unit in question.
  • the pressure which is made available by the auxiliary pressure source and which is greater than the pressure of the controlling drive unit essentially follows the pressure of this antirebs unit linearly.
  • linearity is not absolutely necessary. It is also possible to switch the pressure relief valve between a lower value and an upper value so that the relevant inlet pressure of the shuttle valve is either at the lower or at the upper value.
  • the rotary hammer 10 shown in FIG. 1 has a working cylinder in which the working piston 12 is arranged to be longitudinally displaceable.
  • the front end of the working piston 12 periodically strikes the anvil 13, which is an insertion end connected to a drill string (not shown).
  • the pressure line 15 through which the hydraulic fluid under pressure is supplied to the hammer drill 10 is constantly connected to the front chamber 16 of the working cylinder 11, so that the hydraulic pressure always acts on the control edge 17 of the working piston 12 delimiting the chamber 16.
  • the working piston 12 In the area 18 lying in front of the control edge 17, the working piston 12 has a smaller diameter than the working cylinder 11, while in the area 19 lying behind the control edge 17 the diameter of the working piston corresponds to the diameter of the bore of the working cylinder 11.
  • a region 20 of a smaller diameter adjoins the region 19 and this region is in turn followed by a region of a larger diameter 21.
  • the section 21 of the working piston 12 delimits the rear chamber 22 of the working cylinder towards the front.
  • the chamber 22 is connected via a line 23 to the control cylinder 24, in which the control piston 25, which is designed as a sleeve or hollow piston, can be displaced between two end positions.
  • the inner channel of the control piston 25 is in constant communication with the pressure line 15.
  • the control piston 25 also has an outer annular groove 26 which connects the line 23 to a return line 27 in the one (not shown) end position of the control piston 25 and in which (in Figure 1 shown) position of the control piston 25 is blocked.
  • the control piston 25 connects the line 23 alternately to the pressure line 15 and to the return line 27.
  • the front face 28 of the control piston 25 is constantly exposed to the pressure of the pressure line 15. Since the area of the front end face 28 is larger than that of the rear end face 29, the control piston 25 receives a hydraulic preload in the direction of the left end position (not shown) according to FIG. 1.
  • the control piston 25 also has a circumferential ring 30 whose rear boundary forms a control surface 31 and whose front boundary forms a relief surface 32.
  • the control surface 31 is larger in area than the relief surface 32.
  • the circumferential ring 30 is longitudinally displaceable in a groove 33 of the control cylinder 24.
  • the control line 34 leads into the rear part of this groove, the pressure of which acts on the control surface 31.
  • the front region of the groove 33 is connected to the return line 27 via a line 35.
  • the control line 34 is connected to a plurality of branch lines 340 to 346 which, distributed over the circumference and axially 'staggered', open into the working cylinder 11 at different points.
  • the mouth openings are denoted by 36. If the openings 36 of all branch lines are closed by the section 19 of the working piston 12, the pressure of the front chamber 16 can no longer reach the control line 34, so that the pressure acting on the control surface 31 of the control piston 25 is reduced. The control piston 25 is thereby moved to the left in accordance with FIG. 1.
  • the line 23 is connected to the return line 27 through the annular groove 26, so that the rear chamber 22 of the working cylinder 11 is depressurized. The pressure acting on the control edge 17 now brings about the return stroke of the working piston 12. During the return stroke, the openings 36 of the branch lines 340 to 346 are exposed one after the other.
  • the branch lines 340 to 346 are transverse bores which open into a further cylinder 37 in which a piston 38 can be displaced.
  • the piston 38 has two piston parts 381 and 382 which are arranged at a mutual spacing and whose diameter corresponds to the diameter of the bore of the cylinder 37.
  • the piston parts 381 and 382 are separated from one another by a rod 383 with a smaller diameter.
  • the length of the piston part 381 corresponds approximately to the length of the area in which the branch lines 340 to 346 are in the longitudinal direction merge into cylinder 37.
  • the cylinder 37 is so long that the piston part 381 can be pushed fully out of the region of the branch lines 340 to 346.
  • all branch lines are interconnected by the area of the piston 38 surrounding the rod 383 inside the cylinder 37.
  • the piston 38 is pressed into its front end position by a spring 39, in which it connects the branch lines 340 to 346 to one another.
  • the spring 39 is supported at its rear end on an adjusting slide 40.
  • the adjusting slide 40 is provided with a threaded bolt 41 which projects through an end threaded hole in the housing and can be rotated from the outside.
  • the threaded bolt 41 is secured against inadvertent rotation by a lock nut 42.
  • a control line 43 leads into the cylinder 37.
  • the pressure in the control line 43 thus counteracts the pressure of the spring 39.
  • the piston 38 adjusts to a position in which there is a balance between the force of the spring 39 and the pressure of the control line 43.
  • the shutoff begins at the branch line 346, which is the most forward in the impact direction of the working piston 12, and ends at the most distant branch line 340.
  • a flushing pipe 45 is provided which passes through the housing and through bores in the working piston 12 and the anvil 13 and serves to introduce flushing liquid into the drill string.
  • the hammer drill 10 described is part of an impact drilling device 46, which contains a hydraulic rotary motor 47, as shown in FIG. 2.
  • the rotary motor 47 drives a gearwheel 48 which meshes with a gearwheel 49 which is connected to the drill string 50 in a rotationally fixed manner.
  • the feed device 51 which is a piston-cylinder unit, in the direction of the borehole under constant pressure.
  • the feed device 51 is supported on a stationary abutment.
  • a pressure line 52 leads into the cylinder of the feed device 52 and is pressurized by a pump 54 via a control block 53.
  • the control block 53 is a manually operable changeover valve via which either the pressure line 52 or the pressure line 55 is connected to the pump 54 to advance or retract the impact drill 46.
  • the pressure line 52 for the drilling feed is connected to the one inlet 56 of the shuttle valve 57.
  • the other inlet 58 of the shuttle valve 57 is connected via the further shuttle valve 61 to the hydraulic supply lines 59, 60 of the rotary motor 47.
  • the outlet of the shuttle valve 57 is connected to the control line 43 of the hammer drill 10.
  • the shuttle valve 57 passes the greatest of the pressures of its two inlets 56 and 58 to the control line 43.
  • the shuttle valve 61 has the task of transmitting the respectively greater pressure which prevails in one of these lines to the inlet 58.
  • the purpose of the shuttle valve 61 is to transmit the working pressure of the rotary motor 47 to the shuttle valve 57 when the reversible rotary motor rotates clockwise and counterclockwise.
  • the lines 59, 60 are connected to a pump 63 via a control block 62 for manually switching the direction of rotation of the rotary motor.
  • the pressure in the pressure line 52 is approximately 100 bar during normal drilling operations. If the drilling resistance is higher, the pressure can rise to the maximum delivery pressure of the pump 54, for example to 250 bar.
  • the pressure of the rotary motor 47 is about 80 bar with a normal drilling resistance and with an increased drilling resistance this pressure can rise to the maximum delivery pressure of the pump 63, for example to 175 bar.
  • the spring 39 (Fig. 1) of the piston 38 is set so that the branch lines 340 to 346 are released by the piston 38 when the pressure of the control line 43 exceeds 120 bar.
  • FIG. 3 shows the curve of the control pressure P of the control line 43 with increasing pressure P D of the rotary drive 47 and increasing pressure P v of the feed device 51.
  • the pressures P D and P v have normal values, ie the Device for changing the stroke rate need not respond.
  • the rotational resistance initially increases, so that the pressure P D increases.
  • the response pressure of the piston 38 here: 120 bar
  • it begins to move the piston 38 and thereby reduce the number of strokes of the hammer drill 10.
  • This control range is shown in Fig. 3 by the thick line.
  • the diagram assumes that the feed resistance also increases at time t 2 , so that the pressure P v increases.
  • FIG. 4 largely corresponds to that of FIG. 2, so that the following description can be limited to the differences.
  • the pump 63 according to FIG. 4 has a maximum delivery pressure of 120 bar. This delivery pressure is so low that it is not sufficient as a response pressure for the piston 38 of the hammer drill 10 or is in any case insufficient for a noticeable adjustment of the number of strokes. Therefore, the outlet line 64 of the shuttle valve 61 is not directly connected to the inlet 58 of the shuttle valve 57, but to the control input of the pressure relief valve 65, which connects an auxiliary pressure source 66 (pump) to the tank. The maximum delivery pressure of the auxiliary pressure source 66 is above that of the pump 63. The pressure supplied to the inlet 58 of the shuttle valve 57 is determined by the pressure relief valve 65.
  • This pressure is 50 bar when the control pressure on line 64 is low and 150 bar when the control pressure on line 64 is high.
  • the switchover from 50 bar to 150 bar takes place when the control pressure on line 64 reaches a value (e.g. 80 bar) at which the rotary drive 47 is already subjected to a high load, but which is not sufficient to adjust the number of strokes on the hammer drill 10 to effect.
  • the pressure respectively set by the pressure relief valve 65 is fed to the inlet 58. If this pressure exceeds the pressure at inlet 56 and is so high that it exceeds the response threshold of the stroke rate control, it causes a reduction in the stroke rate.
  • P D the pressure of the rotary drive 47.
  • This pressure assumes a maximum value of 120 bar, which is not sufficient for effective control of the stroke rate.
  • P H denotes the Auxiliary pressure generated by the pressure relief valve 165.
  • the auxiliary pressure P H goes from 50 bar to 150 bar. This value lies above the response threshold of the stroke rate control (here: 120 bar), so that the stroke rate control starts and the stroke rate is reduced. If the feed resistance subsequently rises, the pressure P exceeds the auxiliary pressure P H , so that it takes over the further reduction in the number of strokes above the pressure of 150 bar.
  • the pressure relief valve 65 acts as a kind of amplifier - in the present embodiment with two-point behavior. Depending on the pressure of line 64, it generates an auxiliary pressure P H which is greater than the control pressure and which takes over the control of the stroke rate.
  • the auxiliary pressure source 66 must be able to deliver a relatively high pressure, but it can have a small delivery rate since, with the exception of the energy for adjusting the piston 38 (FIG. 1), it does not have to apply any drive energy.
  • the amplifier formed by the auxiliary pressure source 66 and the controllable pressure relief valve 65 does not act linearly in the exemplary embodiment in FIG. 4, namely as a two-point amplifier.
  • a pressure limiting valve which continuously, preferably linearly, changes the auxiliary pressure P H as a function of the pressure of the line 64.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Automation & Control Theory (AREA)
  • Mechanical Engineering (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
EP86103012A 1985-05-25 1986-03-06 Réglage d'un dispositif hydraulique de perforation à percussion Expired EP0203282B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86103012T ATE44303T1 (de) 1985-05-25 1986-03-06 Regelung einer hydraulischen schlagbohrvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3518892A DE3518892C1 (de) 1985-05-25 1985-05-25 Hydraulische Schlagbohrvorrichtung
DE3518892 1985-05-25

Publications (2)

Publication Number Publication Date
EP0203282A1 true EP0203282A1 (fr) 1986-12-03
EP0203282B1 EP0203282B1 (fr) 1989-06-28

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ID=6271661

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103012A Expired EP0203282B1 (fr) 1985-05-25 1986-03-06 Réglage d'un dispositif hydraulique de perforation à percussion

Country Status (3)

Country Link
EP (1) EP0203282B1 (fr)
AT (1) ATE44303T1 (fr)
DE (2) DE3518892C1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989010465A1 (fr) * 1988-04-26 1989-11-02 Karagandinsky Politekhnichesky Institut Machine de forage hydraulique
EP0384888A1 (fr) * 1989-02-23 1990-08-29 SIG Schweizerische Industrie-Gesellschaft Dispositif de forage
EP0472982A2 (fr) * 1990-08-27 1992-03-04 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage
DE4424081A1 (de) * 1994-07-08 1996-01-11 Klemm Bohrtech Fluidbetätigter Schlaghammer
EP0764502A1 (fr) * 1995-09-20 1997-03-26 HILTI Aktiengesellschaft Appareil manuel de perçage assisté par percussion
CN103089148A (zh) * 2013-01-23 2013-05-08 浙江纪超自动化技术有限公司 一种潜孔钻车专用控制系统
CN107191636A (zh) * 2016-03-14 2017-09-22 卡特彼勒公司 锤保护系统和方法
CN107336198A (zh) * 2017-07-24 2017-11-10 苏州艾乐蒙特机电科技有限公司 一种变行程的冲击电锤
CN110725816A (zh) * 2019-10-18 2020-01-24 金川集团股份有限公司 一种凿岩液压系统
CN111677490A (zh) * 2020-06-19 2020-09-18 中国铁建重工集团股份有限公司 一种水锤与取芯钻两用钻机的控制系统及多功能钻机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4019016A1 (de) * 1990-06-14 1991-06-13 Krupp Maschinentechnik Verfahren zur beeinflussung des betriebsverhaltens eines schlagwerks und einrichtung zur durchfuehrung des verfahrens
DE4424080C1 (de) * 1994-07-08 1996-01-18 Klemm Bohrtech Hydraulischer Schlaghammer
DE4424078C2 (de) * 1994-07-08 1996-10-10 Klemm Bohrtech Hydraulischer Schlaghammer
DE4424079C1 (de) * 1994-07-08 1996-02-15 Klemm Bohrtech Hydraulischer Schlaghammer
US9074352B2 (en) 2006-03-27 2015-07-07 John R. Ramun Universal control scheme for mobile hydraulic equipment and method for achieving the same

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2008880A1 (de) * 1969-02-26 1970-09-24 K.K. Tadano Tekkosho, Takamatsu-City, Kagawa (Japan) Hydraulischer Druckregler für die Verwendung mit einem hydraulischen Druckerzeuger
US3823784A (en) * 1973-06-08 1974-07-16 Dresser Ind Method and apparatus for controlling hydraulic drifters
US4023626A (en) * 1975-03-17 1977-05-17 Oy Tampella Ab Self-adaptive hydraulic rock drill
FR2345578A1 (fr) * 1976-03-25 1977-10-21 Joy Mfg Co Perfectionnements relatifs a des engins de forage
DE2838940A1 (de) * 1978-09-07 1980-03-13 Danfoss As Vorrichtung zur stabilisierung und/oder daempfung eines hydraulischen systems
FR2504049A1 (fr) * 1981-04-16 1982-10-22 Hydroc Gmbh Dispositif hydraulique de percussion

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI56722C (fi) * 1975-07-24 1980-03-10 Tampella Oy Ab Hydraulisk borrmaskin speciellt bergborrmaskin

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2008880A1 (de) * 1969-02-26 1970-09-24 K.K. Tadano Tekkosho, Takamatsu-City, Kagawa (Japan) Hydraulischer Druckregler für die Verwendung mit einem hydraulischen Druckerzeuger
US3823784A (en) * 1973-06-08 1974-07-16 Dresser Ind Method and apparatus for controlling hydraulic drifters
US4023626A (en) * 1975-03-17 1977-05-17 Oy Tampella Ab Self-adaptive hydraulic rock drill
FR2345578A1 (fr) * 1976-03-25 1977-10-21 Joy Mfg Co Perfectionnements relatifs a des engins de forage
DE2838940A1 (de) * 1978-09-07 1980-03-13 Danfoss As Vorrichtung zur stabilisierung und/oder daempfung eines hydraulischen systems
FR2504049A1 (fr) * 1981-04-16 1982-10-22 Hydroc Gmbh Dispositif hydraulique de percussion

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989010465A1 (fr) * 1988-04-26 1989-11-02 Karagandinsky Politekhnichesky Institut Machine de forage hydraulique
US5064003A (en) * 1988-04-26 1991-11-12 Neroznikov Jury I Hydraulic drilling machine
EP0384888A1 (fr) * 1989-02-23 1990-08-29 SIG Schweizerische Industrie-Gesellschaft Dispositif de forage
EP0472982A2 (fr) * 1990-08-27 1992-03-04 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage
EP0472982A3 (en) * 1990-08-27 1992-04-08 Krupp Maschinentechnik Gesellschaft Mit Beschraenkter Haftung Hydraulically operated impact drilling device, especially for boltdrilling
DE4424081A1 (de) * 1994-07-08 1996-01-11 Klemm Bohrtech Fluidbetätigter Schlaghammer
EP0764502A1 (fr) * 1995-09-20 1997-03-26 HILTI Aktiengesellschaft Appareil manuel de perçage assisté par percussion
US6044918A (en) * 1995-09-20 2000-04-04 Hilti Aktiengesellschaft Percussion blow added manually operable drilling tool
CN103089148A (zh) * 2013-01-23 2013-05-08 浙江纪超自动化技术有限公司 一种潜孔钻车专用控制系统
CN107191636A (zh) * 2016-03-14 2017-09-22 卡特彼勒公司 锤保护系统和方法
CN107191636B (zh) * 2016-03-14 2019-12-20 卡特彼勒公司 锤保护系统和方法
CN107336198A (zh) * 2017-07-24 2017-11-10 苏州艾乐蒙特机电科技有限公司 一种变行程的冲击电锤
CN107336198B (zh) * 2017-07-24 2021-01-12 苏州艾乐蒙特机电科技有限公司 一种变行程的冲击电锤
CN110725816A (zh) * 2019-10-18 2020-01-24 金川集团股份有限公司 一种凿岩液压系统
CN111677490A (zh) * 2020-06-19 2020-09-18 中国铁建重工集团股份有限公司 一种水锤与取芯钻两用钻机的控制系统及多功能钻机
CN111677490B (zh) * 2020-06-19 2023-07-14 中国铁建重工集团股份有限公司 一种水锤与取芯钻两用钻机的控制系统及多功能钻机

Also Published As

Publication number Publication date
EP0203282B1 (fr) 1989-06-28
DE3664146D1 (en) 1989-08-03
ATE44303T1 (de) 1989-07-15
DE3518892C1 (de) 1987-02-26

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