EP0472982A2 - 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

Info

Publication number: EP0472982A2
Authority: EP; European Patent Office
Prior art keywords: piston; control; pressure; percussion; working pressure
Prior art date: 1990-08-27
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

EP91113401A

Other languages

German (de)

English (en)

Other versions

EP0472982A3 (en

EP0472982B1 (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.)

1990-08-27

Filing date

1991-08-09

Publication date

1992-03-04

1991-08-09 Application filed by Krupp Maschinentechnik GmbH filed Critical Krupp Maschinentechnik GmbH

1992-03-04 Publication of EP0472982A2 publication Critical patent/EP0472982A2/fr

1992-04-08 Publication of EP0472982A3 publication Critical patent/EP0472982A3/de

1995-12-13 Application granted granted Critical

1995-12-13 Publication of EP0472982B1 publication Critical patent/EP0472982B1/fr

2011-08-09 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

- 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
- 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 can be acted upon by the percussion piston and displaceable in the longitudinal direction and which can be driven by means of a rotating mechanism.
anchor hole drilling An important area of application for rotary impact drilling devices is so-called anchor hole drilling, in which work is carried out with large drilling diameters (possibly with a double rod consisting of drill pipes arranged one inside the other) and large drilling depths. It is problematic that with the percussion rotary drilling devices suitable for such stresses, the two work units (percussion mechanism and slewing gear) can each have the required high performance, but that a simultaneously occurring high decrease in power at both work units overloads the transmission elements of the slewing gear (drill sleeve and insertion end). has the consequence.
the invention has for its object to design a hydraulically operated rotary hammer drill 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; the stroke rate of the striking mechanism is influenced at the same time 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 control elements, 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.
This change can be brought about in two ways: Either by applying the working pressure to either the control element concerned, either of the slewing gear or the striking mechanism.
both control elements are actuated immediately as a function of the slewing gear working pressure after a working pressure limit value has been exceeded.
the second control element is actuated after a working pressure limit value has been exceeded as a function of the hammer mechanism working pressure, that is to say only indirectly as a function of the rotating mechanism working pressure.
the first control element is designed in such a way that, after a working pressure limit value is exceeded as a function of the slewing gear working pressure, when it increases, it reduces the striking mechanism working pressure. Via the second control element, the number of strokes of the percussion piston can be reduced or increased with the increase in the percussion mechanism or the rotating mechanism working pressure via an increase or a decrease in the push-out pressure.
the percussion rotary drilling device has a control in the form of a control slide in a known manner, which - with constant pressure being applied to the Return stroke movement causing smaller return stroke area of the percussion piston - alternately connecting the larger working stroke area of the percussion piston with the pressure line or a return line
the second control element is expediently designed such that it becomes effective in the connecting channel between the control and the return line (claim 2) .
At least the first control element should be designed in such a way that the working pressure limit value which triggers its actuation can be changed (claim 3). This can be achieved in a simple manner in that a restoring force counteracting the working pressure is increased or decreased.
the control members are preferably designed as throttle valves, by means of which the size of an outlet cross section connected to a return line can be influenced (claim 4). For example, an increase in the associated outlet cross-section results in a drop in the hammer mechanism working pressure or the already mentioned push-out pressure.
each throttle valve has at least one piston which can be displaced against a restoring force under pressure when the working pressure in question is applied (claim 5).
the throttle valve forming the first control member 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 supported resiliently (claim 6).
the reset element for the control piston can in particular be designed as a mechanically active 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 7). 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 pretensioning force.
control elements must be adapted to the expected operating conditions, taking into account the design of the rotary impact drilling device.
the main components of the rotary impact drilling device are a percussion mechanism 1 with a housing 2, a percussion piston 3 which can be reciprocated therein and a control 4, and a rotary 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 thrust 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 counter 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 (as 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 on the side of the percussion piston tip 1a is equipped 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 chamber 13, which is located 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 influence 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 annular projection 1c.
the control essentially consists of a control slide 22 with a through hole 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 control element 25 to be described;
a leakage channel 27 also opens into the latter and 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 respect to the size of its two end faces 22c, 22d and the other two ring faces such 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 control element 25 for influencing the operating behavior of the rotary impact drilling device is designed as a throttle valve. It has a control piston 31 which, in the rest position, is held 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 control element 42 also equipped as a throttle valve.
This consists of a control piston 43, which rests in the rest position under the action of a prestressed return spring 44 on a stop surface 45; 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, can be changed 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. If the working pressure in the pressure line 24 exceeds a predetermined value (due to the pretension of the return spring 44), the outlet cross-section in the connecting channel 29, which has already been mentioned, 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 duct 29 and thus to a relatively lower drop in the number of strokes.
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 via 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 preload of the return spring 32 can be increased continuously, as a result of which the working pressure limit value rises, after which the control member 25 responds.
the components 31 and 49 for receiving the return spring 32 are partially hollow; the relief channel 41 lies in the range between the above-mentioned components 31 and 49.
the second control element 42 shown in FIG. 3 is controlled 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; Accordingly, the control piston 43 is connected to the control line 38 as well as the first control element 25 (shown in FIG. 1).
the return spring 44 lies on the side of the control piston 43 which faces away from the throttle pin 43a and which is partially hollow.
the embodiment in question can be easily modified in accordance with the design of the first control element according to FIG. 2 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 control elements are actuated immediately after a predetermined limit value has been exceeded as a function of the size of the slewing gear working pressure.
the control member 42 is designed and switched in such a way 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 strokes 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.

Landscapes

Engineering & Computer Science (AREA)
Fluid Mechanics (AREA)
Physics & Mathematics (AREA)
Mechanical Engineering (AREA)
Geology (AREA)
Mining & Mineral Resources (AREA)
Life Sciences & Earth Sciences (AREA)
Environmental & Geological Engineering (AREA)
General Life Sciences & Earth Sciences (AREA)
Geochemistry & Mineralogy (AREA)
Automation & Control Theory (AREA)
Percussive Tools And Related Accessories (AREA)
Earth Drilling (AREA)
Drilling And Exploitation, And Mining Machines And Methods (AREA)

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
DE4027021A DE4027021A1 (de)	1990-08-27	1990-08-27	Hydraulisch betriebene schlagdrehbohrvorrichtung, insbesondere zum ankerlochbohren
DE4027021		1990-08-27

Publications (3)

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

Family

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 (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0527395A3 (fr) *	1991-08-08	1994-01-26	Maruzen Kogyo Co Ltd
EP0752297A3 (fr) *	1995-07-06	1998-01-14	Bretec Oy	Marteau à percussion hydraulique
EP0906811A1 (fr) *	1997-10-03	1999-04-07	SIG Schweizerische Industrie-Gesellschaft	Marteau de forage

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE69227925T2 (de) *	1992-08-19	1999-05-12	Akcionernoe Obsestivo Zakrytogo Tipa " Rossiiskaja Patentovannaja Technika" (Ropat), Novosibirsk	Hydraulische pfahlramme
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
US5730230A (en) *	1995-08-15	1998-03-24	Sisler; John S.	Rotary percussion drill
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
WO2004051004A2 (fr) *	2002-12-02	2004-06-17	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
SE534815C2 (sv)	2010-05-03	2012-01-10	Atlas Copco Rock Drills Ab	Bergborrmaskin med dämpkolv
EP3085880B1 (fr) *	2013-12-18	2018-10-24	Nippon Pneumatic Manufacturing Co., Ltd.	Outil entraîné par impact
WO2015115106A1 (fr) *	2014-01-31	2015-08-06	古河ロックドリル株式会社	Dispositif de martelage hydraulique
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.
WO2018043175A1 (fr) *	2016-08-31	2018-03-08	古河ロックドリル株式会社	Dispositif de percussion hydraulique
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
FR3108931B1 (fr) *	2020-04-02	2022-04-08	Montabert Roger	Perforateur hydraulique roto-percutant pourvu d’un emmanchement équipé de cannelures d’accouplement
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

1990
- 1990-08-27 DE DE4027021A patent/DE4027021A1/de not_active Withdrawn
1991
- 1991-08-09 EP EP91113401A patent/EP0472982B1/fr not_active Expired - Lifetime
- 1991-08-09 DE DE59107065T patent/DE59107065D1/de not_active Expired - Fee Related
- 1991-08-09 AT AT91113401T patent/ATE131430T1/de not_active IP Right Cessation
- 1991-08-23 JP JP3211811A patent/JPH05131379A/ja active Pending
- 1991-08-27 US US07/750,270 patent/US5117921A/en not_active Expired - Fee Related

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0527395A3 (fr) *	1991-08-08	1994-01-26	Maruzen Kogyo Co Ltd
EP0752297A3 (fr) *	1995-07-06	1998-01-14	Bretec Oy	Marteau à percussion hydraulique
US5890548A (en) *	1995-07-06	1999-04-06	Bretec Oy	Hydraulic percussion hammer
EP0906811A1 (fr) *	1997-10-03	1999-04-07	SIG Schweizerische Industrie-Gesellschaft	Marteau de forage
US6119793A (en) *	1997-10-03	2000-09-19	Sig Rocktools Ag	Rock drill

Also Published As

Publication number	Publication date
JPH05131379A (ja)	1993-05-28
DE4027021A1 (de)	1992-03-05
ATE131430T1 (de)	1995-12-15
US5117921A (en)	1992-06-02
EP0472982A3 (en)	1992-04-08
EP0472982B1 (fr)	1995-12-13
DE59107065D1 (de)	1996-01-25

Legal Events

Date	Code	Title	Description
1992-01-17	PUAI	Public reference made under article 153(3) epc to a published international application that has entered the european phase	Free format text: ORIGINAL CODE: 0009012
1992-02-18	PUAL	Search report despatched	Free format text: ORIGINAL CODE: 0009013
1992-03-04	AK	Designated contracting states	Kind code of ref document: A2 Designated state(s): AT CH DE FR GB IT LI
1992-04-08	AK	Designated contracting states	Kind code of ref document: A3 Designated state(s): AT CH DE FR GB IT LI
1992-12-02	17P	Request for examination filed	Effective date: 19921007
1993-01-20	17Q	First examination report despatched	Effective date: 19921207
1995-10-27	GRAA	(expected) grant	Free format text: ORIGINAL CODE: 0009210
1995-12-13	AK	Designated contracting states	Kind code of ref document: B1 Designated state(s): AT CH DE FR GB IT LI
1995-12-13	REF	Corresponds to:	Ref document number: 131430 Country of ref document: AT Date of ref document: 19951215 Kind code of ref document: T
1996-01-25	REF	Corresponds to:	Ref document number: 59107065 Country of ref document: DE Date of ref document: 19960125
1996-02-09	ET	Fr: translation filed
1996-02-15	REG	Reference to a national code	Ref country code: CH Ref legal event code: NV Representative=s name: TROESCH SCHEIDEGGER WERNER AG
1996-03-08	ITF	It: translation for a ep patent filed
1996-04-24	GBT	Gb: translation of ep patent filed (gb section 77(6)(a)/1977)	Effective date: 19960321
1996-10-18	PLBE	No opposition filed within time limit	Free format text: ORIGINAL CODE: 0009261
1996-10-18	STAA	Information on the status of an ep patent application or granted ep patent	Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT
1996-12-04	26N	No opposition filed
1998-07-23	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: AT Payment date: 19980723 Year of fee payment: 8
1998-08-04	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: CH Payment date: 19980804 Year of fee payment: 8
1999-08-09	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 19990809
1999-08-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 19990831 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 19990831
2000-04-14	REG	Reference to a national code	Ref country code: CH Ref legal event code: PL
2000-11-17	REG	Reference to a national code	Ref country code: FR Ref legal event code: CD
2000-11-29	REG	Reference to a national code	Ref country code: GB Ref legal event code: 732E
2000-12-29	REG	Reference to a national code	Ref country code: FR Ref legal event code: TP
2002-01-01	REG	Reference to a national code	Ref country code: GB Ref legal event code: IF02
2002-07-30	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: GB Payment date: 20020730 Year of fee payment: 12
2002-08-12	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: FR Payment date: 20020812 Year of fee payment: 12
2003-08-05	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: DE Payment date: 20030805 Year of fee payment: 13
2003-08-09	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20030809
2004-03-31	GBPC	Gb: european patent ceased through non-payment of renewal fee	Effective date: 20030809
2004-04-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20040430
2004-06-04	REG	Reference to a national code	Ref country code: FR Ref legal event code: ST
2005-03-01	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050301
2005-08-09	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20050809

Publication	Publication Date	Title
EP0472982B1 (fr)	1995-12-13	Appareil de forage tournant et frappant actionné hydrauliquement, spécialement pour le forage d'ancrage
EP0475171B1 (fr)	1995-10-11	Mécanisme à coup actionné hydrauliquement
DE69411383T2 (de)	1999-04-01	Hydraulischer bohrlochschlagschieber mit wartezeitreduzierung
DE2443800A1 (de)	1975-03-20	Hydraulisch betriebene schlagvorrichtung
CH597500A5 (en)	1978-04-14	Rotary percussive rock drill
DE2705191A1 (de)	1977-08-11	Schlagbohrwerkzeug
DE19636659C2 (de)	2000-11-23	Fluidbetriebenes Schlagwerk mit automatischer Hubumschaltung
EP0203282B1 (fr)	1989-06-28	Réglage d'un dispositif hydraulique de perforation à percussion
DE2449023A1 (de)	1975-04-30	Hydraulisch betaetigte schlagbohrvorrichtung
DE2461633C2 (de)	1982-05-06	Hydraulische Schlagvorrichtung
EP2345495B1 (fr)	2017-01-11	Dispositif de serrage d'une pièce ou d'un outil sur une broche de travail
DE3842891A1 (de)	1989-08-24	Rotationsbohrverfahren und rotationsbohreinrichtung zur durchfuehrung des verfahrens
EP0847836B1 (fr)	2001-02-28	Appareil à percussion mû par un fluide sous pression
DE4028304C2 (fr)	1993-08-12
EP0577545A1 (fr)	1994-01-05	Trépan de forage
DE69622020T2 (de)	2003-01-02	Metallblecharbeitsstation
DE3034211C2 (de)	1983-03-17	Mit einer Druckflüssigkeit beaufschlagbare Schlag- und Bohrvorrichtung
DE2346519A1 (de)	1974-04-11	Hydraulisch betriebene schlagvorrichtung
EP0933169A2 (fr)	1999-08-04	Dispositif de percussion actionné par un fluide
DE69620156T2 (de)	2002-11-14	Verfahren zur metallblechbearbeitung in einer metallblecharbeitsstation und diese metallblecharbeitsstation
DE3343565A1 (de)	1985-06-13	Tieflochhammer
DE69721954T2 (de)	2004-05-19	Federgespannter, mechanischer Expander mit festgelegter Vorspannung und konstanter Referenz- Position
DE4312171C1 (de)	1994-08-04	Hydraulisches Schlaggerät für eine Bohrvorrichtung
EP0074496A1 (fr)	1983-03-23	Dispositif de vanne, en particulier pour machine à moulage sous pression
DE2536143C2 (de)	1982-01-28	Hydraulisches Schlaggerät