EP0472982B1 - Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage - Google Patents

Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage Download PDF

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Publication number
EP0472982B1
EP0472982B1 EP91113401A EP91113401A EP0472982B1 EP 0472982 B1 EP0472982 B1 EP 0472982B1 EP 91113401 A EP91113401 A EP 91113401A EP 91113401 A EP91113401 A EP 91113401A EP 0472982 B1 EP0472982 B1 EP 0472982B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
working pressure
throttle valve
percussion
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
EP91113401A
Other languages
German (de)
English (en)
Other versions
EP0472982A3 (en
EP0472982A2 (fr
Inventor
Robert-Jan Dr. Ing. Bartels
Hans-Dieter Piotrowski
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.)
SIG Plastics GmbH and Co KG
Original Assignee
Krupp Maschinentechnik GmbH
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 Krupp Maschinentechnik GmbH filed Critical Krupp Maschinentechnik GmbH
Publication of EP0472982A2 publication Critical patent/EP0472982A2/fr
Publication of EP0472982A3 publication Critical patent/EP0472982A3/de
Application granted granted Critical
Publication of EP0472982B1 publication Critical patent/EP0472982B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • 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 invention relates to a hydraulically operated percussion drilling device, in particular for anchor hole drilling, with a percussion piston and a control which alternately switches its direction of movement and with a tool insertion end which is actuated by the percussion piston and is displaceable in the longitudinal direction and is driven by a rotating mechanism.
  • the document US-A-4 440 236 describes a generic percussion drilling device. As control elements of interest in this context, this has pressure limiting valves which can assume a closed or an open position.
  • the known device is designed in such a way that the working pressure of the striking mechanism is influenced indirectly as a function of the working pressure of the rotating mechanism, namely via the pressure difference between the feed line and the return line of the associated feed unit.
  • the pressure limiting valve which may switch off the working pressure of the striking mechanism, is connected directly to the lines of the feed unit already mentioned via control lines; the latter is assigned a further pressure relief valve, which may reduce the pressure difference in the lines of the feed unit.
  • the invention has for its object to design a hydraulically operated rotary hammer drilling device in such a way that - after exceeding a predetermined limit - the performance of the hammer mechanism is continuously reduced depending on the load on the rotating mechanism; at the same time, the impact rate of the striking mechanism is influenced in such a way that it drops less than would otherwise be the case.
  • the basic idea of the invention is to additionally equip the rotary impact drilling device with two throttle valves, via which the impact of the impact mechanism is reduced by influencing the working pressure driving the impact piston or by influencing the push-out pressure against which the impact piston can be traced against the direction of impact, whose impact rate changes leaves.
  • the pressure line for supplying the drive means to the percussion piston is equipped with a first throttle valve, which reduces the working pressure driving the percussion piston - after a limit value of the slewing gear working pressure has been exceeded - directly and more and more with its rise.
  • the second throttle valve which, like the first throttle valve, influences the size of an outlet cross section connected to a return line, changes the push-out pressure against which the percussion piston is returned against the direction of impact, after a limit value has been exceeded, either as a function of the size of the striking mechanism working pressure, that with increasing hammer mechanism working pressure the size of the push-out pressure increases or is changed in dependence on the size of the slewing gear working pressure such that the size of the push-out pressure decreases with increasing slewing gear working pressure.
  • the smaller return stroke area of the percussion piston, which causes the return stroke movement, is constantly subjected to working pressure and the control alternately switching the direction of movement of the percussion piston is designed as a control slide which, depending on the position of the percussion piston, alternately connects its larger working stroke area in the impact direction to the pressure line and a return line , wherein the second throttle valve is operatively arranged in the connecting channel between the controller and the return line.
  • At least the first throttle valve should be designed in such a way that its limit value setting can be influenced by changing the bias of its return spring (claim 2).
  • each throttle valve has at least one piston which is pushed against a restoring force under pressure under the working pressure in question (claim 3).
  • the first throttle valve is preferably equipped with a control piston which can be displaced against a restoring element and on which a throttle piston which limits the outlet cross section is resiliently supported (claim 4).
  • the restoring element for the control piston can in particular be designed as a mechanically effective spring element.
  • the displacement of the pressurized control piston has the consequence that the preload force acting on the throttle piston drops:
  • the working pressure limit value which can move the throttle piston against the preload and thus open an outlet cross-section, is accordingly lower.
  • the biasing force of the restoring element for the control piston is adjustable (claim 5). The control piston therefore only executes a corresponding movement when the working pressure of the slewing gear acting on it generates an adjusting force which exceeds the preloading force.
  • the design and the resulting mode of operation of the throttle valves must be adapted to the expected operating conditions, taking into account the design of the rotary hammer drilling device.
  • the main rotary drilling device has a striking mechanism 1 with a housing 2, a striking piston 3 which can be reciprocated therein and a control 4 as well as a rotating mechanism 5 with one on the Housing 2 flanged slewing gear housing 6 and an attached hydraulic motor 7, with which a drive pinion 8 supported in the slewing gear housing 6 can be driven in both directions of rotation.
  • the slewing gear housing further receives - supported on two axial bearings 9 and 10 - a counter bearing 11 designed as a gearwheel, in whose toothing 11a the drive pinion 8 engages.
  • An insertion end 12 for a drilling tool is movably connected to the thrust bearing 11 via a torque connection in the form of a spline profile 12a; the freedom of movement of the insertion end with respect to the slewing gear housing 6 and the counter bearing 11 is limited by a paragraph 12b.
  • the housing 2 there are three spaces separated from each other by the percussion piston, namely (viewed in sequence from the percussion piston tip 1a) a pressure space 13, a reversing space 14 and a space 15 into which the rear end of the percussion piston 1b protrudes more or less.
  • the latter space is kept depressurized in the illustrated embodiment; if necessary, however, it can also be filled with compressed gas.
  • the housing 2 is equipped on the side of the percussion piston tip 1a with two sealing elements 16 and in the area between the spaces 14 and 15 with two sealing elements 17, 18.
  • the range of motion of the percussion piston 3 is limited by an annular projection 1c located in the pressure space 13, which protrudes on the end of the percussion piston 1b facing side merges into a narrower cylinder section 1d.
  • the annular projection 1c In the direction of the percussion piston tip 1a, the annular projection 1c has a truncated cone section 1e, which enables the formation of a pressure cushion which brakes the percussion piston movement.
  • the diameter of the cylinder section 1d is such that it can shut off the bore section 19 against the pressure chamber 13, which adjoins the former in the direction of the piston end 1b.
  • the percussion piston 3 is pressurized under the action of the known control 4 in such a way that it alternately executes a working stroke in the direction of impact (arrow 20) or a return stroke in the opposite direction (arrow 21).
  • the smaller return stroke area 1f effective in the direction of the return stroke results from the difference in area between the cylinder section 1d and the percussion piston section 1h on the opposite side of the ring projection 1c.
  • the control essentially consists of a control slide 22 with a through bore 22a, which is held in a cylinder chamber 23 so that it can be pushed back and forth in the longitudinal direction and is connected via this to a pressure line 24 and via its extension 24a to the pressure chamber 13; the pressure line 24 is acted upon by a pressure oil source, not shown, during operation with the working pressure p S provided for the striking mechanism 1.
  • the pressure line 24 with its extension 24a is connected to a return line 26, which is kept pressureless, with the interposition of a first throttle valve 25 to be described;
  • a leakage channel 27 also opens into this, which drains leakage oil from the area between the two sealing elements 17, 18.
  • the reversing chamber 14 can be connected to the return line 26 via a reversing duct 28, the cylinder chamber 23 and a connecting duct 29 or to the pressure line 24 via the components 28 and 23.
  • the pressurization of the percussion piston 3 is designed in a manner known per se such that its return stroke surface 1f is acted upon by working pressure via the pressure line 24, 24a.
  • the larger working stroke area 1g which triggers the working stroke is only temporarily subjected to working pressure when the control slide 22 moves (by executing a movement to the left) into the other end position, not shown.
  • the movement of the control slide 22 to the left has the result that the connection between the channels 28 and 29 is interrupted by the section 22b and at the same time the reversing channel 28 is connected to the pressure line 24.
  • the control slide 22 is dimensioned with regard to the size of its two end faces 22c, 22d and the other two ring faces in such a way that it assumes the return stroke position shown in FIG. 1, as long as the annular face 22e adjacent to the end face 22c (as shown in the drawing) via the channel 30 ) is sufficiently pressurized. As soon as - depending on the position of the percussion piston 3 - the pressure in the channel 30 drops, the control slide 22 moves under the action of the then greater compressive force on the end face 22d to the left with the already mentioned consequence that by acting on the reversing chamber 14 with the working pressure the working stroke is triggered in the direction of arrow 20.
  • the already mentioned first throttle valve 25 for influencing the operating behavior of the rotary impact drilling device has a control piston 31 which is held in abutment against a stop surface 33 under the action of a prestressed return spring 32.
  • An essentially frustoconical throttle piston 35 is supported on the narrower front section 31a of the control piston with the interposition of a spring 34; its guide consists of a guide pin 35a held movably in the housing 2.
  • the stop surface 33 is part of an annular chamber 37, into which a control line 38 opens. This in turn is connected via a changeover valve 39 to the line (for example line 7a) which is subjected to the working pressure for the operation of the hydraulic motor 7. This can therefore work in both directions of rotation without influencing the function of the control line 38.
  • the chamber 40 receiving the parts 31 and 32 is connected to the return line 26 via a relief channel 41.
  • a second throttle valve 42 is provided. This consists of a control piston 43 which, in the rest position, bears against a stop surface 45 under the action of a prestressed return spring 44; in the area of which the control piston 43 can be acted upon by a control line 46 connected to the pressure line 24.
  • the control piston 43 On the side facing the return spring 44, the control piston 43 has a throttle pin 43a with a frustoconical end section 43b, which more or less closes the cross section of the connecting channel 29.
  • the chamber 47 receiving the control piston 43 is connected to the return line 26 via a relief channel 48 and is thus relieved of pressure.
  • the position of the end section 43b with respect to the connecting channel 29 determines the size of the outlet cross section in the return line 26 and thus the push-out pressure which the percussion piston during the return stroke must overcome, by moving the control piston 43 depending on the working pressure for the striking mechanism 1 against the action of the return spring 44, the number of strokes of the striking piston 3 can be changed. If the working pressure in the pressure line 24 exceeds a predetermined value (due to the prestressing of the return spring 44), the previously mentioned outlet cross section in the connecting channel 29 is reduced via the control piston 43, as a result of which the push-out pressure increases during the return stroke and the number of strokes decreases. Starting from an operating position of the control piston 43, which is caused by a working pressure above the associated limit value, a drop in the working pressure leads to an increase in the outlet cross section at the connecting channel 29 and thus to a relatively lower drop in the number of strokes.
  • the interaction of the two throttle valves 25 and 42 thus ensures that a reduction in the impact mechanism performance caused by the rotating mechanism working pressure may result in a desired, less severe reduction in the number of strokes, since a comparatively higher one automatically occurs due to the reduced impact mechanism working pressure Sets stroke rate.
  • the biasing force exerted by the return spring 32 on the control piston 31 can be changed continuously.
  • the component 32 is supported on the housing 2 by means of a threaded bushing 49 with an external hexagon head 49a.
  • the threaded bushing 49 By turning the threaded bushing 49 in the direction of the control piston 31 bearing against the stop surface 33, the pretension of the return spring 32 can be increased continuously, as a result of which the working pressure limit value rises, after which the throttle valve 25 responds.
  • the components 31 and 49 for receiving the return spring 32 are partially hollow; the relief channel 41 lies in the area between the named components 31 and 49.
  • the second throttle valve 42 shown in FIG. 3 is controlled - in contrast to the embodiment according to FIG. 1 - after a limit value has been exceeded (predetermined by the pretension of the return spring 44) as a function of the working pressure for the slewing gear;
  • the control piston 43 is accordingly connected to the control line 38, as is the first throttle valve 25 (shown in FIG. 1).
  • the return spring 44 is located on the side of the control piston 43 facing away from the throttle pin 43a, which is partially hollow.
  • the embodiment in question can - based on the design of the first throttle valve according to FIG. 2 - be easily changed by installing a threaded bushing in such a way that the biasing force of the return spring 44 can also be adjusted.
  • the connection of the control piston 43 to the control line 38 has the result that both throttle valves are actuated immediately after a predetermined limit value has been exceeded as a function of the size of the slewing gear working pressure.
  • the throttle valve 42 is designed and switched such that a sufficient pressure increase in the control line 38, the displacement of the control piston 43 counter to the action of the return spring 44, an increase in the outlet cross section in the connecting channel 29 and thus a reduction in the push-out pressure (with a relative increase in the number of strokes) has the consequence.
  • the advantage achieved by the invention is that under certain conditions the percussion performance is influenced as a function of the load on the slewing gear and at the same time the ejection pressure to be overcome by the percussion piston is changed in such a way that the number of impacts is not undesirable even when the percussion performance is reduced drops sharply.
  • the rotary impact drilling device designed in this way is particularly suitable for anchor hole drilling and applications with comparable working conditions.

Claims (5)

  1. Dispositif roto-percutant entraîné hydrauliquement, destiné en particulier à la foration de trous d'ancrage, comportant un piston de frappe (3) et une commande (4) inversant alternativement le sens de déplacement du piston, et comportant une extrémité d'emmanchement d'outil (12), frappée par le piston de frappe (3) et maintenue coulissante dans la direction longitudinale de ce piston, cette extrémité d'emmanchement étant entraînée par un mécanisme de rotation (5),
       caractérisé
       en ce que la conduite sous pression (24) alimentant le moyen d'entraînement du piston de frappe (3) est réalisée avec un première soupape d'étranglement (25), qui abaisse toujours plus la pression de fonctionnement entraînant le piston de frappe (3) - après dépassement d'une valeur limite de la pression de fonctionnement du mécanisme de rotation - au fur et à mesure de la montée de cette pression, et
       en ce qu'il existe une deuxième soupape d'étranglement (42), qui, de même que la première soupape d'étranglement (25), agit sur la grandeur d'une section de sortie (respectivement 35, 36 et 29, 43b) raccordée à une conduite de retour (26), et au moyen de laquelle la pression de refoulement, en s'opposant à laquelle le piston de frappe (3) est renvoyé en arrière dans le sens opposé au sens de frappe (flèche 20), ou bien est modifiée, après dépassement d'une valeur limite, en fonction de la grandeur de la pression de fonctionnement du mécanisme de frappe de telle façon que, lorsque la pression de fonctionnement du mécanisme de frappe augmente, la grandeur de la pression de refoulement augmente, ou bien cette pression de refoulement est modifiée en fonction de la pression de fonctionnement du mécanisme de rotation de telle façon que, lorsque la pression de fonctionnement du mécanisme de rotation augmente, la grandeur de la pression de refoulement s'abaisse;
       en ce que, sur la surface plus petite de recul du piston de frappe (3) provoquant le mouvement de recul, est constamment appliquée la pression de fonctionnement, et la commande (4) est réalisée sous la forme d'une vanne de commande (22), qui - en fonction de la position du piston de frappe (3) - relie la surface du piston, plus grande, commandant la course de travail, alternativement à la conduite (24) sous pression et à une conduite de retour (26),
       et en ce que la deuxième soupape d'étranglement (42) est disposée, pour son action, dans le canal de liaison (29) situé entre la commande (4) et la conduite de retour (26).
  2. Dispositif suivant la revendication 1, caractérisé en ce qu'on peut agir sur le réglage de la valeur limite, au moins de la première soupape d'étranglement (25), en modifiant la précontrainte de son ressort de rappel (32).
  3. Dispositif suivant la revendication 1, caractérisé en ce que chacune des soupapes d'étranglement (25, 42) présente au moins un piston (respectivement 31 et 43), qui, quand on applique la pression, est poussé en s'opposant à une force de recul d'un ressort de rappel (respectivement 32 et 44).
  4. Dispositif suivant au moins l'une des revendications 1 à 3, caractérisé en ce que la première soupape d'étranglement (25) présente un piston de commande (31) pouvant coulisser en s' opposant à un organe de rappel (32), piston de commande contre lequel s'appuie élastiquement un piston d'étranglement (35) limitant la section de sortie de la partie d'alésage (36).
  5. Dispositif suivant la revendication 4, caractérisé en ce que la force de précontrainte de l'organe de rappel (32) destiné au piston de commande (31) est réglable.
EP91113401A 1990-08-27 1991-08-09 Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage Expired - Lifetime EP0472982B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4027021 1990-08-27
DE4027021A DE4027021A1 (de) 1990-08-27 1990-08-27 Hydraulisch betriebene schlagdrehbohrvorrichtung, insbesondere zum ankerlochbohren

Publications (3)

Publication Number Publication Date
EP0472982A2 EP0472982A2 (fr) 1992-03-04
EP0472982A3 EP0472982A3 (en) 1992-04-08
EP0472982B1 true EP0472982B1 (fr) 1995-12-13

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ID=6412985

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91113401A Expired - Lifetime EP0472982B1 (fr) 1990-08-27 1991-08-09 Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage

Country Status (5)

Country Link
US (1) US5117921A (fr)
EP (1) EP0472982B1 (fr)
JP (1) JPH05131379A (fr)
AT (1) ATE131430T1 (fr)
DE (2) DE4027021A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102985230A (zh) * 2010-05-03 2013-03-20 阿特拉斯·科普柯凿岩设备有限公司 钻机

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3378029B2 (ja) * 1991-08-08 2003-02-17 丸善工業株式会社 油圧ブレーカ
EP0675233B1 (fr) * 1992-08-19 1998-12-16 Aktsionernoe Obschestvo Zakrytogo Tipa "Rossiiskaya Patentovannaya Tekhnika" (Ropat) Sonnette de battage hydraulique
DE4302755C2 (de) * 1993-02-01 2003-01-02 Mannesmann Rexroth Ag Steuereinrichtung zur Regelung einer von zwei zusammenwirkenden Hydraulik-Verbrauchern abhängigen Arbeitskenngröße
ZA932778B (en) * 1993-04-21 1994-09-30 Jarmo Uolevi Leppaenen Rock drill
CN2215384Y (zh) * 1994-12-30 1995-12-20 陈利钧 储能冲击控制机构
FI104960B (fi) * 1995-07-06 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
US5730230A (en) * 1995-08-15 1998-03-24 Sisler; John S. Rotary percussion drill
ATE217564T1 (de) * 1997-10-03 2002-06-15 Sig Produktionstechnik Ag Bohrhammer
US7073607B2 (en) * 2001-06-25 2006-07-11 Campbell Jr Paul B Operating system for hydraulic rock drill
DE10146023B4 (de) * 2001-09-18 2006-02-23 Tracto-Technik Gmbh Steuerung für einen Schlagantrieb
EP1567724A2 (fr) * 2002-12-02 2005-08-31 Bj Services Company Procede et dispositif pour le battage en rotation d'un pieu sous la mer
FI123740B (fi) * 2005-01-05 2013-10-15 Sandvik Mining & Constr Oy Menetelmä painenestekäyttöisen iskulaitteen ohjaamiseksi ja iskulaite
FI123634B (fi) * 2007-10-05 2013-08-30 Sandvik Mining & Constr Oy Kallionrikkomislaite, suojaventtiili sekä menetelmä kallionrikkomislaitteen käyttämiseksi
KR200449892Y1 (ko) * 2008-02-21 2010-08-18 주식회사 삼우기초기술 인장재 제거형 그라운드 앵커용 동력식 인장재 해체기
KR101135076B1 (ko) * 2009-03-10 2012-04-16 전평근 제거식 앵커의 강연선 제거공법
EP3085880B1 (fr) * 2013-12-18 2018-10-24 Nippon Pneumatic Manufacturing Co., Ltd. Outil entraîné par impact
US10493610B2 (en) * 2014-01-31 2019-12-03 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
CH711414A1 (de) * 2015-08-13 2017-02-15 Hatebur Umformmaschinen Ag Vorrichtung zur Erzeugung impulsdynamischer Prozesskräfte.
JP6588651B2 (ja) * 2016-08-31 2019-10-09 古河ロックドリル株式会社 液圧式打撃装置
CN109663946B (zh) * 2019-01-25 2020-04-17 东方电气集团东方汽轮机有限公司 一种燃气轮机阀座密封面加工便携式数控镗孔设备及应用
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커
FR3120248B1 (fr) * 2021-03-01 2023-02-10 Montabert Roger Perforateur hydraulique roto-percutant pourvu d’un piston de butée et d’une chambre de freinage

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE203282C (fr) * 1907-01-11
US4006783A (en) * 1975-03-17 1977-02-08 Linden-Alimak Ab Hydraulic operated rock drilling apparatus
FI56052C (fi) * 1975-01-16 1979-11-12 Tampella Oy Ab Hydraulisk bergborrmaskin
ZA761652B (en) * 1976-03-17 1977-06-29 Steel Eng Co Ltd Hydraulic percussive machines
ZA763344B (en) * 1976-06-04 1978-01-25 Steel Eng Co Ltd Hydraulic rotary-percussive machines
DE2658455C3 (de) * 1976-12-23 1981-01-22 Fried. Krupp Gmbh, 4300 Essen Druckmittelbetriebenes Schlagwerk
FI56723C (fi) * 1978-05-11 1980-03-10 Tampella Oy Ab Styrningssystem foer borrmaskin
FI58675C (fi) * 1979-06-26 1981-03-10 Tampella Oy Ab Hydraulisk borranordning
US4440236A (en) * 1979-09-20 1984-04-03 Toyo Kogyo Co. Ltd. Hydraulic control system for a rock drill
SE8207405L (sv) * 1982-12-27 1984-06-28 Atlas Copco Ab Bergborranordning och metod att optimera bergborrning
DE3518892C1 (de) * 1985-05-25 1987-02-26 Klemm Bohrtech Hydraulische Schlagbohrvorrichtung
HUT53193A (en) * 1988-04-26 1990-09-28 Karagandinskij Polt Institut Hydraulic borer
RU1778289C (ru) * 1988-05-04 1992-11-30 Карагандинский политехнический институт Гидравлическа бурильна машина
FR2647870B1 (fr) * 1989-06-06 1991-09-06 Eimco Secoma Appareil de percussion hydraulique avec dispositif d'amortissement des ondes de choc en retour

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102985230A (zh) * 2010-05-03 2013-03-20 阿特拉斯·科普柯凿岩设备有限公司 钻机
CN102985230B (zh) * 2010-05-03 2015-05-20 阿特拉斯·科普柯凿岩设备有限公司 钻机

Also Published As

Publication number Publication date
EP0472982A3 (en) 1992-04-08
ATE131430T1 (de) 1995-12-15
EP0472982A2 (fr) 1992-03-04
DE4027021A1 (de) 1992-03-05
US5117921A (en) 1992-06-02
DE59107065D1 (de) 1996-01-25
JPH05131379A (ja) 1993-05-28

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