EP0473968A2 - 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
EP0473968A2
EP0473968A2 EP91113444A EP91113444A EP0473968A2 EP 0473968 A2 EP0473968 A2 EP 0473968A2 EP 91113444 A EP91113444 A EP 91113444A EP 91113444 A EP91113444 A EP 91113444A EP 0473968 A2 EP0473968 A2 EP 0473968A2
Authority
EP
European Patent Office
Prior art keywords
percussion piston
pressure
impact
stop element
control
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
EP91113444A
Other languages
German (de)
English (en)
Other versions
EP0473968A3 (en
EP0473968B1 (fr
Inventor
Robert-Jan Dr.-Ing. Bartels
Hans-Dieter Ing. 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 EP0473968A2 publication Critical patent/EP0473968A2/fr
Publication of EP0473968A3 publication Critical patent/EP0473968A3/de
Application granted granted Critical
Publication of EP0473968B1 publication Critical patent/EP0473968B1/fr
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
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons

Definitions

  • the invention relates to a hydraulically operated percussion drilling device, in particular for anchor hole drilling, with a percussion piston and a control alternately switching its direction of movement, with a tool insertion end which can be acted upon by the percussion piston and is displaceable in the longitudinal direction and which can be driven by means of a rotating mechanism, and with a pressure chamber,
  • the working pressure for the operation of the percussion piston is applied to the percussion piston return-lifting surface, which causes the return stroke movement, and the one attached to the percussion piston, which absorbs its freedom of movement in the longitudinal direction.
  • Drilling work to be carried out in this context is, for example, rock drilling, ramming, screw drilling and core drilling, in which the two main components of the percussion rotary drilling device - namely the percussion mechanism driving the percussion piston and the rotating mechanism - can be used individually or together. If only the slewing gear is in operation, the undesirable contact between the leads Percussion piston and the tool insertion end to increased wear and possibly damage, in particular to the percussion piston and the associated sealing elements.
  • the invention is therefore based on the object of further developing an impact rotary drilling device in such a way that the slewing gear can be operated alone without impairing or stressing the components of the impact mechanism in question.
  • a rotary impact drilling device which has the features of claim 1.
  • the main idea of the invention is to provide the percussion piston with a projection which can be supported on a stop element which can be displaced in the longitudinal direction of the percussion piston. This is designed and switched in such a way that it assumes an impact operating position or a rotary operating position when pressure is applied differently: in the first-mentioned position, the projection is movable with respect to the stop element in such a way that the impact piston can act as intended on the tool insertion end; If the stop element - after switching off the working pressure for the operation of the percussion piston and applying a control pressure - is brought into the second position against the direction of impact, the projection gripped by the stop element is carried in this direction and the percussion piston tip is thereby lifted off the tool insertion end. This ensures that the slewing gear can be operated without influencing the percussion piston.
  • the control pressure causing the lifting movement of the stop element can be switched on by actuating a valve.
  • the stop element has effective control surfaces in the opposite direction, which can be acted upon with the working pressure for operating the percussion piston or with the control pressure (claim 2).
  • the impact operation control surface of the stop element effective in the direction of the impact operation position is dimensioned such that the force emanating from it is greater than the lifting force emanating from the at least one rotary operation control surface under the action of the control pressure (claim 3). This ensures that the lifting process can only be initiated after the striking mechanism has been stopped (after the working pressure has been switched off to operate the striking piston).
  • the stop element can be displaced into the rotary operating position as a control pressure under the influence of the working pressure for the operation of the rotating mechanism (claim 4). Accordingly, when the slewing gear is put into operation, the lifting process is initiated automatically, regardless of the operator's attention, if the stop element is only subjected to the slewing gear working pressure.
  • the stop element can be designed in a simple manner as a sliding sleeve which is movably supported on the percussion piston (claim 5). Your turning operation control surface can be connected via an annular groove to a control line which is connected to the pressure line of the slewing gear (claim 6).
  • control line expediently merges into a changeover valve which is simultaneously connected to the pressure and return lines of the slewing gear.
  • the object of the invention can be further developed in that the end face of the sliding sleeve, which faces the percussion piston tip, is kept depressurized via a relief channel (claim 7).
  • This pressure relief prevents the build-up of a pressure cushion in the area of the end face, which could impair the function of the sliding sleeve.
  • the sliding sleeve On the side facing the projection, the sliding sleeve preferably has a recess which is shorter than the longitudinal extent of the sliding sleeve and whose diameter is slightly larger than the outer diameter of the projection designed as a ring shoulder (claim 8).
  • the recess serves to brake the percussion piston in the event of an empty stroke in cooperation with the ring shoulder and to carry it over its end surface during the lifting process.
  • the percussion rotary drilling device has as its main component a percussion mechanism 1 with a housing 2, a percussion piston 3 which can be reciprocated therein and a control 4 as well as a rotating mechanism 5 with a rotating mechanism housing 6 which - composed of the components 6a and 6b - has the latter component is flanged to the striking mechanism housing 2.
  • a hydraulic motor 7 is fastened to the component 6b, with which a drive pinion 8 supported in the rotating mechanism 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.
  • a tool insertion end 12 is movably connected to the counter bearing 11 via a torque connection in the form of a spline profile 12a in the longitudinal direction of the percussion piston 3; the freedom of movement of the tool insertion end with respect to the slewing gear housing 6 and the counter bearing 11 is limited by a shoulder 12b.
  • the tool insertion end 12 set in rotation under the action of the hydraulic motor 7, the drive pinion 8 and the counter bearing 11 transmits the single impact energy generated by the percussion piston 3 the drilling tool, not shown; the percussion piston tip 3a, the impact surface 12c of the tool insertion end interacting with this, and the torque connection between the parts 11 and 12 may be exposed to considerable stress.
  • the percussion mechanism housing 2 there are three spaces separated from each other by the percussion piston, namely (as viewed in sequence from the percussion piston tip 3a) a pressure space 13, a reversing space 14 and a space 15 into which the rear end of the percussion piston 3b protrudes more or less far.
  • the latter space is kept depressurized in the illustrated embodiment; if necessary, however, it can also be filled with compressed gas.
  • the percussion mechanism housing 2 is equipped on the side of the percussion piston tip 3a with two sealing elements 16 and in the area between the spaces 14 and 15 with two sealing elements 17 and 18.
  • the freedom of movement of the percussion piston 3 in the longitudinal direction is determined by an annular shoulder 3c located in the pressure chamber 13, which merges into a narrower cylinder section 3d on the side facing the percussion piston end 3b.
  • the ring shoulder 3c In the direction of the percussion piston tip 3a, the ring shoulder 3c has a truncated cone section 3e, which enables the formation of a pressure cushion that brakes the percussion piston movement.
  • the diameter of the cylinder section 3d is designed such that it can shut off the bore section 19 against the pressure chamber 13, which adjoins the former in the direction of the percussion piston end 3b.
  • the percussion piston 3 becomes such under the influence of the control 4 known per se pressurized that it alternately performs 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 3f effective in the direction of the return stroke results from the area difference between the cylinder section 3d and the percussion piston section 3h on the opposite side of the ring shoulder 3c.
  • the controller 4 consists essentially 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 provided for the striking mechanism 1.
  • the reversing chamber 14 can be connected via a reversing duct 25, the cylinder chamber 23 and a connecting duct 26 to a pressure-free return line 27 or via the components 25 and 23 to the pressure line 24.
  • a leakage channel 28 also opens into the return line 27, which leads leakage oil from the area between the two sealing elements 17 and 18.
  • the pressurization of the percussion piston 3 is known in such a way that its return stroke surface 3f is acted upon by the percussion work pressure via the pressure line 24, 24a.
  • the larger working stroke area 3g which triggers the working stroke (which delimits the reversing space 14 in the direction of the percussion piston tip 3a) is only then temporarily supplied with 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 its section 22b interrupts the connection between the channels 25 and 26, and at the same time the reversing channel 25 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 further annular surface 22e in such a way that it assumes the return stroke position shown in FIG. 1, as long as the annular surface 22e adjacent to the end face 22c is sufficiently pressurized via the channel 29. As soon as - depending on the position of the percussion piston 3 - the pressure in the channel 29 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.
  • a stop element in the form of an essentially cylindrical sliding sleeve 31, which is movably supported on the percussion piston in the longitudinal direction and in the percussion mechanism housing 2.
  • the Sliding sleeve 31 On the side facing the ring shoulder 3c, the Sliding sleeve 31 has a recess 31a which is shorter than the longitudinal extension of the sliding sleeve and whose diameter is slightly larger than the outer diameter of the ring shoulder 3c.
  • the inner end surface 31b limits the freedom of movement of the ring shoulder 3c and thus the percussion piston 3 in the direction of the working stroke (arrow 20).
  • the sliding sleeve 31 is equipped on its outside with a rotary control surface 31d; this can be pressurized via an annular groove 32a into which a control line 32 opens.
  • the control line is in turn connected via a changeover valve 33 to line 34 or 35, which is acted upon by the working pressure for the operation of the rotating mechanism 5, ie the hydraulic motor 7.
  • the latter can therefore work in both directions of rotation without influencing the function of the control line 32.
  • the end face 31e of the sliding sleeve 31 facing the percussion piston tip 3a is connected via an annular groove 36a to a leakage channel 36 which opens into the return line 27, which is kept pressureless.
  • control surfaces (31b, 31c) and 31d - taking into account the working pressure in question - dimensioned such that the force emanating from the blow operation control surface (31b, 31c) in the direction of the working stroke (arrow 20) is greater than that under the action of the control pressure from the turning operation control surface 31d outgoing lifting force in the direction of arrow 21. Accordingly, the sliding sleeve can only leave the striking operating position shown in FIG. 1 after the pressure chamber 13 has become depressurized by switching off the striking mechanism 1.
  • the sliding sleeve 31 moves under the influence of the control pressure in the control line 32 in the direction of the arrow 21 to the right, finally grips the ring shoulder 3c together with component 3e over the end face 31b and thereby guides the striking piston 3 until the end face 31c comes to rest against the end wall 13a of the pressure chamber 13 (FIG. 2).
  • the lifting process associated with this movement leads to the fact that the percussion piston tip 3a and the impact surface 12c of the tool insertion end 12 lie opposite one another at a distance a:
  • the tool insertion end 12 can therefore be turned by means of the rotating mechanism 5 without influencing the impact piston driven in both directions.
  • the advantage achieved with the invention is that - due to the action of the rotary operating control surface 31d with the working pressure for the slewing gear 5 - the lifting operation described is automatically triggered without outside intervention as soon as the striking mechanism 1 is switched off.
  • Fig. 3 it can be seen that the hammer mechanism 1 with the interposition of a two-position valve 37 with a pressure oil source in the form of a Pump unit 38 communicates; the slewing gear 5 can be supplied with pressure oil via a pump unit 40 by actuating a three-position valve 39 - which also enables a change in the direction of rotation.
  • the changeover valve 33 serves to connect the control line 32 to the line 34 or 35 to which the working pressure is applied, regardless of the direction of rotation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
EP91113444A 1990-09-06 1991-08-10 Appareil de forage tournant et frappant, actionné hydrauliquement, spécialement pour le forage d'ancrage Expired - Lifetime EP0473968B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4028304 1990-09-06
DE4028304A DE4028304A1 (de) 1990-09-06 1990-09-06 Hydraulich betriebene schlagdrehbohrvorrichtung, insbesondere zum ankerlochbohren

Publications (3)

Publication Number Publication Date
EP0473968A2 true EP0473968A2 (fr) 1992-03-11
EP0473968A3 EP0473968A3 (en) 1992-05-27
EP0473968B1 EP0473968B1 (fr) 1994-10-19

Family

ID=6413739

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91113444A Expired - Lifetime EP0473968B1 (fr) 1990-09-06 1991-08-10 Appareil de forage tournant et frappant, actionné hydrauliquement, spécialement pour le forage d'ancrage

Country Status (3)

Country Link
EP (1) EP0473968B1 (fr)
AT (1) ATE112998T1 (fr)
DE (2) DE4028304A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013072878A1 (fr) * 2011-11-18 2013-05-23 Gien Bernard L Forage de roches à percussion
CN104329019A (zh) * 2014-10-24 2015-02-04 徐梓辰 一种高频钻井冲击器
WO2021198605A1 (fr) * 2020-04-02 2021-10-07 Montabert Perforateur hydraulique roto-percutant pourvu d'un emmanchement équipé de cannelures d'accouplement
CN114000822A (zh) * 2021-10-23 2022-02-01 江西沃斯德凿岩液压有限公司 凿岩机的冲击机构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010008819B4 (de) 2010-02-22 2015-07-30 Eurodrill Gmbh Schlagdrehbohrvorrichtung und Verfahren zum Betrieb

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2344378A1 (fr) * 1976-03-15 1977-10-14 Hydroacoustic Inc Outil a percussion
EP0394765A1 (fr) * 1989-04-27 1990-10-31 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Mécanisme à coup hydraulique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE652171A (fr) * 1963-08-21
FI50307C (fi) * 1974-04-20 1976-02-10 Xandor Ag Hydraulisesti käytetty iskulaite

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2344378A1 (fr) * 1976-03-15 1977-10-14 Hydroacoustic Inc Outil a percussion
EP0394765A1 (fr) * 1989-04-27 1990-10-31 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Mécanisme à coup hydraulique

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013072878A1 (fr) * 2011-11-18 2013-05-23 Gien Bernard L Forage de roches à percussion
CN104329019A (zh) * 2014-10-24 2015-02-04 徐梓辰 一种高频钻井冲击器
WO2021198605A1 (fr) * 2020-04-02 2021-10-07 Montabert Perforateur hydraulique roto-percutant pourvu d'un emmanchement équipé de cannelures d'accouplement
FR3108931A1 (fr) * 2020-04-02 2021-10-08 Montabert Perforateur hydraulique roto-percutant pourvu d’un emmanchement équipé de cannelures d’accouplement
US11866997B2 (en) 2020-04-02 2024-01-09 Montabert Rotary percussive hydraulic drill provided with a shank equipped with coupling splines
EP4127374B1 (fr) * 2020-04-02 2024-09-11 Montabert Perforateur hydraulique roto-percutant pourvu d'un emmanchement équipé de cannelures d'accouplement
CN114000822A (zh) * 2021-10-23 2022-02-01 江西沃斯德凿岩液压有限公司 凿岩机的冲击机构

Also Published As

Publication number Publication date
EP0473968A3 (en) 1992-05-27
ATE112998T1 (de) 1994-11-15
DE4028304A1 (de) 1992-03-12
DE4028304C2 (fr) 1993-08-12
DE59103273D1 (de) 1994-11-24
EP0473968B1 (fr) 1994-10-19

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