EP3752325B1 - Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator - Google Patents

Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator Download PDF

Info

Publication number
EP3752325B1
EP3752325B1 EP19705982.7A EP19705982A EP3752325B1 EP 3752325 B1 EP3752325 B1 EP 3752325B1 EP 19705982 A EP19705982 A EP 19705982A EP 3752325 B1 EP3752325 B1 EP 3752325B1
Authority
EP
European Patent Office
Prior art keywords
piston
control chamber
stop piston
stop
pressure fluid
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.)
Active
Application number
EP19705982.7A
Other languages
German (de)
French (fr)
Other versions
EP3752325A1 (en
Inventor
Jean-Sylvain Comarmond
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.)
Montabert SAS
Original Assignee
Montabert SAS
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 Montabert SAS filed Critical Montabert SAS
Publication of EP3752325A1 publication Critical patent/EP3752325A1/en
Application granted granted Critical
Publication of EP3752325B1 publication Critical patent/EP3752325B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • B25D17/24—Damping the reaction force
    • 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
    • B25D17/24—Damping the reaction force
    • B25D17/245—Damping the reaction force using a fluid
    • 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
    • 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
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • E21B6/02—Drives for drilling with combined rotary and percussive action the rotation being continuous
    • E21B6/04—Separate drives for percussion and rotation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D2209/002—Pressure accumulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons

Definitions

  • the present invention relates to a rotapercutant hydraulic drill more specifically used on a drilling rig.
  • a drilling rig comprises, in a known manner, a roto-percussive hydraulic drill mounted sliding on a slide and driving one or more drill bars, the last of these drill bars carrying a tool called a cutting tool which comes into contact with the rock.
  • a perforator generally aims to drill more or less deep holes in order to be able to place explosive charges there.
  • the perforator is therefore the main element of a drilling installation which, on the one hand, gives the cutting edge rotation and percussion via the drill bars so as to penetrate the rock, and on the other hand, provides an injection fluid so as to extract the debris from the drilled hole.
  • a roto-percussive hydraulic perforator comprises more particularly on the one hand a striking system which is driven by one or more flow rates of hydraulic fluid coming from a main hydraulic supply circuit and which comprises a striking piston configured to strike, each operating cycle of the drill, a fitting coupled to the drill bars, and on the other hand a rotation system provided with a hydraulic rotary motor and configured to rotate the fitting and the drill bars.
  • the force of support of the roto-percussive hydraulic perforator on the drill bars, and therefore of the cutter on the rock, is generated by the slide, thanks to a cable or a drive chain moved by a hydraulic cylinder or a hydraulic motor. More precisely, the bearing force is transmitted from the body of the perforator to the fitting via an abutment element incorporated in the body of the perforator.
  • This stop element can consist, for powerful perforators, of a stop piston, at least one surface of which is hydraulically supplied so as to ensure transmission of the bearing force by means of a fluid.
  • WO2010/082871 discloses a roto-percussive hydraulic drill according to the preamble of claim 1, in which, under operating conditions of the striking system, the stop piston is positioned in an equilibrium position, conforming to a stroke desired impact of the impact piston, via a hydraulic control chamber delimited by the impact piston and the body of the perforator and permanently connected to a high-pressure fluid supply conduit, the hydraulic control being configured on the one hand to urge the stopper piston forwards and on the other hand to be connected to a low-pressure fluid return conduit when the rear face of the stopper piston is located at a predetermined distance of the rear wall of the cavity receiving the stop piston.
  • the present invention aims to remedy all or part of these drawbacks.
  • the technical problem underlying the invention therefore consists in providing a hydraulic drill which is of simple and economical structure, while having improved performance.
  • Such a configuration of the second control chamber makes it possible, due to the permanent connection of the latter with the low pressure accumulator, to ensure a high speed movement of the stop piston forwards when the rock gives way under the impact of the impact piston and that the fitting is suddenly free to move forward. This makes it possible to quickly restore a normal bearing force of the tool of the drill bar on the rock, and this despite the movements due to the penetration of the drill bar into the ground and the various vibrations of the body of the perforator.
  • the particular configuration of the first control chamber and of the connecting channel makes it possible to position the stop piston hydraulically in an approximately stable equilibrium position corresponding to an optimal striking stroke of the striking piston.
  • the particular configuration of the roto-percussion hydraulic perforator according to the present invention gives it improved performance compared to the roto-percussion hydraulic perforators of the prior art.
  • the hydraulic drill may additionally have one or more of the following characteristics, taken alone or in combination.
  • the low pressure accumulator is a membrane accumulator, such as a hydropneumatic accumulator.
  • the membrane accumulator advantageously comprises a flexible membrane, a first face of which is subjected to the pressure of a volume of compressible gas contained in the membrane accumulator and the second face of which is subjected to the pressure of the low-pressure fluid coming from the low pressure fluid return line.
  • the second control chamber is connected to the low pressure accumulator by a return channel.
  • the stop piston comprises a first annular control surface extending transversely to the displacement axis and delimiting at least in part the first control chamber and a second annular control surface s 'extending transversely to the axis of movement and delimiting at least in part the second control chamber, the second annular control surface having a surface greater than the surface of the first annular control surface.
  • the first control chamber has a cross section smaller than the cross section of the second control chamber.
  • each of the first and second annular control surfaces extends substantially perpendicular to the axis of displacement.
  • the first annular control surface is closer to the front face of the stop piston than the second annular control surface.
  • the body and the stop piston also at least partly delimit a third control chamber permanently connected to the low-pressure fluid return conduit, the third control chamber being antagonistic to the first and second control chambers.
  • the third control chamber is permanently connected to the low pressure accumulator.
  • the third control chamber is configured to urge the stop piston towards the rear, that is to say towards the rear wall of the cavity and therefore opposite the fitting.
  • the third control chamber is connected to the low-pressure fluid return conduit by a fluid communication channel provided with a calibrated orifice.
  • the return channel comprises a nozzle comprising the calibrated orifice.
  • the third control chamber has a cross section smaller than the cross section of the second control chamber.
  • the stop piston includes the connecting channel, and the connecting channel includes a first end portion opening into the third control chamber and a second end portion opposite the first end portion and opening into an outer surface of the stopper piston, the second end portion being able to be fluidically connected to the first control chamber when the rear face of the stopper piston is located at a distance from the rear wall of the cavity greater than the predetermined value.
  • the stop piston comprises the connecting channel.
  • the connecting channel comprises a first end portion opening into the first control chamber and a second end portion opposite the first end portion and opening into an outer surface of the stopper piston, the second end portion of the connecting channel being able to be fluidically connected to the low-pressure fluid return conduit when the rear face of the stopper piston is located at a distance from the rear wall of the upper cavity to the predetermined value.
  • the body comprises an annular groove opening into the cavity and permanently connected to the low-pressure fluid return conduit, the second end portion of the connecting channel being able to be fluidically connected to the annular groove when the rear face of the stop piston is located at a distance from the rear wall of the cavity greater than the predetermined value.
  • the annular groove is connected to the low pressure accumulator.
  • the rotary-percussive hydraulic drill comprises a supply channel connecting the first control chamber to the high-pressure fluid supply conduit.
  • the supply channel is provided with a calibrated orifice.
  • the supply channel comprises a nozzle comprising the calibrated orifice.
  • the stop piston is slidably mounted around the striking piston.
  • the main hydraulic supply circuit comprises a high pressure accumulator connected to the high pressure fluid supply conduit.
  • the high pressure accumulator is a membrane accumulator, such as a hydropneumatic accumulator.
  • the membrane accumulator forming the high-pressure accumulator advantageously comprises a flexible membrane, a first face of which is subjected to the pressure of a volume of compressible gas contained in the membrane accumulator and the second face of which is subjected to the pressure of the high pressure fluid from the high pressure fluid supply line.
  • the roto-percussive hydraulic perforator further comprises an annular stop member arranged between the fitting and the front face of the stop piston.
  • the annular stop member is a stop ring.
  • the roto-percussive hydraulic drill comprises a thrust bearing arranged between the rear face of the thrust piston and the rear wall of the cavity.
  • the thrust bearing can for example be a roller thrust bearing.
  • the abutment piston comprises an annular bearing surface configured to come into abutment against an annular abutment surface of the body.
  • the annular bearing surface is configured to come into abutment against the annular abutment surface of the body when the rear face of the stop piston is located at a predetermined distance from the rear wall of the cavity, the predetermined distance being greater than the predetermined value.
  • the annular bearing surface is inclined relative to the axis of movement.
  • the stop piston comprises an annular flange comprising the annular bearing surface.
  • the annular collar at least partly delimits the third control chamber.
  • the annular flange comprises the first annular control surface.
  • the body comprises a piston cylinder in which the striking piston is slidably mounted in an alternating manner, the cavity being made in the body coaxially with the piston cylinder.
  • the fitting extends longitudinally along the strike axis.
  • the fitting comprises a first end portion facing the striking piston and provided with an end face against which the striking piston is intended to strike, and a second portion end, opposite the first end portion, intended to be coupled to the at least one drill bar.
  • the high pressure fluid supply conduit is a high pressure incompressible fluid supply conduit
  • the low pressure fluid return conduit is a fluid return conduit incompressible at low pressure
  • the rotapercutant hydraulic perforator 2 comprises more particularly a body 3 comprising a piston cylinder 4.
  • the body 1 comprises a main body 3.1 partly delimiting the piston cylinder 4, as well as a front liner 3.2 and a rear liner 3.3 force-fitted in a bore 3.4 delimited by the main body 3.1.
  • the striking system of the rotapercutant hydraulic perforator 2 comprises a striking piston 5 mounted to slide alternately in the piston cylinder 4 along a striking axis A. As shown more particularly in the figure 2 , the striking piston 5 and the piston cylinder 4 delimit a primary control chamber 6 which is annular, and a secondary control chamber 7 which has a larger section than that of the primary control chamber 6 and which is antagonistic to the primary control chamber 6.
  • the striking system of the rotapercutant hydraulic perforator 2 further comprises a control valve 8 arranged to control an alternating movement of the striking piston 5 inside the piston cylinder 4 alternately following a striking stroke and a return stroke.
  • the control distributor 8 is configured to place the secondary control chamber 7, alternately in relation with a high pressure fluid supply conduit 9, such as a high pressure incompressible fluid supply conduit, during the striking stroke of the striking piston 5, and with a low-pressure fluid return conduit 11, such as a low-pressure incompressible fluid return conduit, during the return stroke of the striking piston 5.
  • the conduit high pressure fluid supply 9 and the low pressure fluid return conduit 11 belong to a main hydraulic supply circuit with which the striking system is provided.
  • the main hydraulic supply circuit can advantageously include a high pressure accumulator 12 connected to the high pressure fluid supply conduit 9.
  • the control distributor 8 is more particularly movably mounted in a bore made in the body 3 between a first position (see the figure 2 ) in which the control distributor 8 is configured to place the secondary control chamber 7 in relation to the high-pressure fluid supply conduit. pressure 9 and a second position in which the control valve 8 is configured to place the secondary control chamber 7 in relation to the low pressure fluid return conduit 11.
  • the primary control chamber 6 is advantageously permanently supplied with high-pressure fluid via a supply channel (not shown in the figures), so that each position of the control valve 8 causes the striking stroke of the strike 5, then the return stroke of strike piston 5.
  • the striking system of the rotapercutant hydraulic perforator 2 also comprises a stop piston 13 which is tubular and which is slidably mounted in a cavity 14 of the body 3 along an axis of movement parallel to the striking axis A and preferably coinciding with the striking axis A.
  • the stop piston 13 is slidably mounted around the striking piston 5, and the cavity 14 is made in the body 3 coaxially with the piston cylinder 4.
  • the rotapercutant hydraulic perforator 2 further comprises a fitting 15 intended to be coupled, in known manner, to at least one drill bar (not shown in the figures) equipped with a tool.
  • the fitting 15 extends longitudinally along the striking axis A, and comprises a first end portion 16 facing the striking piston 5 and provided with an end face 17 against which the piston is intended to strike. 5 during each operating cycle of the rotapercutant hydraulic drill 2, and a second end portion (not shown in the figures), opposite the first end portion 16, intended to be coupled to at least a drill bar.
  • the stop piston 13 comprising a front face 18 facing the fitting 15 and intended to position the fitting 15 in a predetermined position of equilibrium with respect to the striking piston 5, and a rear face 19 opposite the front face 18 and located opposite a rear wall 21 of cavity 14.
  • the body 3 and the stop piston 13 delimit, with the strike piston 5, a first control chamber 22 permanently connected to the high-pressure fluid supply conduit 9 and configured to urge the stop piston 13 towards the forward, that is to say towards the fitting 15 and therefore opposite the rear wall 21 of the cavity 14.
  • the roto-percussive hydraulic perforator 2 advantageously comprises a supply channel 23 connecting the first chamber control 22 to the high pressure fluid supply conduit 9.
  • the supply channel 23 is provided with a calibrated orifice 24, which can for example be provided on a nozzle incorporated in the supply channel 23.
  • the body 3 and the stop piston 13 delimit, with the striking piston 5, also a second control chamber 25 connected to a low pressure accumulator 26 which belongs to the main hydraulic supply circuit of the striking system and which is connected to the low-pressure fluid return conduit 11.
  • the second control chamber 25 is, like the first control chamber 22, also configured to urge the stop piston 13 forwards.
  • the roto-percussive hydraulic perforator 2 comprises a return channel 27 connecting the second control chamber 25 to the low pressure accumulator 26.
  • the stop piston 13 comprises a first annular control surface 28, also called first annular active surface, extending perpendicularly to the axis of movement and partly delimiting the first control chamber 22, and a second annular control surface 29, also called the second annular active surface, extending perpendicularly to the axis of movement and partly delimiting the second control chamber 25.
  • the second annular control surface 29 advantageously has a surface greater than the surface of the first surface of annular control 28.
  • the second control chamber 25 advantageously has a cross section greater than the cross section of the first control chamber 22.
  • the body 3 and the stop piston 15 also delimit a third control chamber 31 permanently connected to the low-pressure fluid return conduit 11, via a fluid communication channel 32 opening into the third control chamber.
  • control 31 and the return channel 27 which connects the fluidic communication channel 32 to the low-pressure fluid return conduit 11.
  • the third control chamber 31 is antagonistic to the first and second control chambers 22, 25, and is thus configured to urge the stop piston 13 rearward.
  • the second control chamber 25 is sized to have an active surface on the stop piston 13 that is much greater than the active surface of the third control chamber 31.
  • the second and third control chambers 25, 31 being connected to the channel return 27 and to the low pressure accumulator 26, the calculation of the difference of the two active surfaces of the second and third control chambers 25, 31 gives a resulting active surface pushing the stop piston 13 forwards and subjected to the pressure of the low pressure accumulator 26.
  • Rotary-percussive hydraulic drill 2 further comprises a connecting channel 33 configured to fluidically connect the first control chamber 22 to the low-pressure fluid return conduit 11 when the rear face 19 of the stop piston 13 is located at a distance of the rear wall 21 of the cavity 14 which is greater than a predetermined value.
  • the stop piston 13 includes the connecting channel 33
  • the connecting channel 33 includes a first end portion 33.1 opening into the first control chamber 22 and a second end portion 33.2 opposite the first portion of end 33.1 and opening into an outer surface of the stop piston 13.
  • the second end portion 33.2 of the connecting channel 33 is adapted to be fluidically connected to an annular groove 34, which opens into the cavity 14 and which is connected permanently to the low-pressure fluid return conduit 11, when the rear face 19 of the stop piston 13 is located at a distance from the rear wall 21 of the cavity 14 which is greater than the predetermined value.
  • the calibrated orifice 24 is advantageously of very small size by ra pport to the connecting channel 33 and to the return channel 27 so that the pressure which is established in the first control chamber 22 drops very rapidly when the connecting channel 33 opens in the annular groove 34.
  • the flow which passes through the calibrated orifice 24 must preferably remain low because it is taken from the high-pressure fluid supply conduit 9.
  • the flow rate of fluid supplying the first control chamber 22 is low, and therefore the speed of movement of the stop piston 13, resulting from this flow rate of fluid, is also low.
  • the second control chamber 25 is freely supplied by the low pressure accumulator 26, and will make it possible to push the stop piston 13 forwards and at high speed, for example when the rock yields under the impact of the striking piston 5 and the fitting 15 is suddenly free to move forward.
  • the roto-percussion hydraulic drill 2 also comprises a rotation system comprising a hydraulic motor 35 driving a motor pinion 36 and a driven pinion 37, so as to ensure a rotational movement of the fitting 15.
  • the hydraulic motor 35 is advantageously powered hydraulically by an external hydraulic supply circuit.
  • the fitting 15 When the roto-percussive hydraulic drill 2 is in operation, the fitting 15 is set in rotation thanks to the hydraulic motor 35, and the fitting 15 receives on its end face 17 the cyclic shocks of the striking piston 5, ensured by the striking system supplied by the main hydraulic supply circuit.
  • the carrier machine on which the rotary-percussion hydraulic drill 2 is mounted applies a thrust force on the drill bar, via the body 3 of the rotary-percussion hydraulic drill 2 and the fitting 15. Inside of the perforator, between the body 3 and the fitting 15, this force is transmitted via the abutment piston 13 and a stop member 38, such as a stop ring, arranged between the fitting 15 and the front face 18 of the stop piston 13.
  • the positioning of the stop piston 13 is thus purely hydraulic and is arranged so that the striking stroke C of the striking piston 5 is respected.
  • the stop piston 13 further comprises an annular bearing surface 39 configured to come into abutment against an annular stop surface 41 of the body 3, so as to limit the stroke of movement of the stop piston 13 forwards, c that is to say towards the fitting 15.
  • the annular bearing surface 39 is configured to come into abutment against the annular abutment surface 41 of the body 3 when the rear face 19 of the abutment piston 13 is located at a predetermined distance from the rear wall 21 of the cavity 14, the predetermined distance being greater than the predetermined value.
  • the annular bearing surface 39 is inclined with respect to the axis of movement, and partly delimits the third control chamber 31.
  • the picture 3 shows a second embodiment of the rotary-percussion hydraulic drill 2 which differs from the first embodiment essentially in that the fluidic communication channel 32 is provided with a calibrated orifice 42, which can for example be provided on a nozzle incorporated in the fluid communication 32, and in that the first end portion 33.1 of the connecting channel 33 opens into the third control chamber 31 and the second end portion 33.2 of the connecting channel 33 opens into an outer surface of the stop piston 13, the second end portion 33.2 of the connecting channel 33 being adapted to be fluidically connected to the first control chamber 22 when the rear face 19 of the stop piston 13 is located at a distance from the rear wall 21 of the cavity 14 which is greater than the predetermined value.
  • the first control chamber 22 When the roto-percussive hydraulic drill 2 according to the second embodiment of the invention is in operation, the first control chamber 22 is subjected to high pressure, the stop piston 13 moves forward until that the second end portion 33.2 of the connecting channel 33 opens into the first control chamber 22.
  • the high-pressure oil then flows into the third control chamber 31 whose connection with the return channel 27 is throttled by the calibrated orifice 42.
  • the first and third control chambers 22, 31 then take fairly close pressures, which reduces or cancels the forward thrust of the stop piston 13. Consequently, the stop piston 13 will find a stable operating position around this position of the second end portion 33.2 of the connecting channel 33.
  • the second control chamber 25 is freely supplied by the low pressure accumulator 26, and will make it possible to push the stop piston 13 forwards and at high speed, for example when the rock yields under the impact of the impact piston 5. This makes it possible to quickly return to a normal pressing force of the drill bar tool on the rock, despite the movements due to the penetration of the drill bar drilling in the ground and the various vibrations of the body 3 of the perforator, while ensuring, thanks to the first and third control chambers 22, 31, an average position of the stop piston 13 which respects the planned striking stroke C of the striking piston 5.
  • the stop piston 13 comprises an annular flange 43, also called annular shoulder, which comprises the annular bearing surface 39 and the first annular control surface 28.
  • annular flange 43 advantageously partly delimits the first control chamber 22 and partly the third control chamber 31.
  • the supply channel 23 advantageously has no calibrated orifice, or any other specific throttle element.
  • the figure 4 shows a third embodiment of rotary-percussion hydraulic drill 2 which differs from the first embodiment essentially in that the rotary-percussion hydraulic drill 2 comprises a thrust bearing 44, such as a roller thrust bearing, disposed between the face rear 19 of the stop piston 13 and the rear wall 21 of the cavity 14.
  • a thrust bearing 44 such as a roller thrust bearing
  • the fitting 15 is in rotation as well as the stop member 38 and the stop piston 13. Since the positioning of the stop piston 13 in the predetermined equilibrium position is only done when the striking system is in operation (thus providing the necessary fluid in the first, second and third control chambers 22, 25 , 31), then the stop piston 13 is pressed, by the reaction force of the ground, against not the rear wall 21 of the cavity 14 (which could induce a rotary friction of the stop piston 13 against the body 3 and therefore generate damage to various component parts of the perforator), but against the thrust bearing 44 (which greatly limits the wear of the roto-percussive hydraulic perforator 2, and this without addition of external fluid at the level of the thrust piston 13) .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (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)
  • Earth Drilling (AREA)
  • Percussive Tools And Related Accessories (AREA)

Description

La présente invention se rapporte à un perforateur hydraulique rotopercutant plus spécialement utilisé sur une installation de forage.The present invention relates to a rotapercutant hydraulic drill more specifically used on a drilling rig.

Une installation de forage comprend de façon connue un perforateur hydraulique roto-percutant monté coulissant sur une glissière et entraînant une ou plusieurs barres de forage, la dernière de ces barres de forage portant un outil appelé taillant qui au contact de la roche. Un tel perforateur a généralement pour objectif de forer des trous plus ou moins profonds afin de pouvoir y placer des charges explosives. Le perforateur est donc l'élément principal d'une installation de forage qui, d'une part, confère au taillant la mise en rotation et la mise en percussion par l'intermédiaire des barres de forage de façon à pénétrer la roche, et d'autre part, fournit un fluide d'injection de manière à extraire les débris du trou foré.A drilling rig comprises, in a known manner, a roto-percussive hydraulic drill mounted sliding on a slide and driving one or more drill bars, the last of these drill bars carrying a tool called a cutting tool which comes into contact with the rock. Such a perforator generally aims to drill more or less deep holes in order to be able to place explosive charges there. The perforator is therefore the main element of a drilling installation which, on the one hand, gives the cutting edge rotation and percussion via the drill bars so as to penetrate the rock, and on the other hand, provides an injection fluid so as to extract the debris from the drilled hole.

Un perforateur hydraulique roto-percutant comprend plus particulièrement d'une part un système de frappe qui est animé par un ou plusieurs débits de fluide hydraulique provenant d'un circuit principal d'alimentation hydraulique et qui comprend un piston de frappe configuré pour frapper, à chaque cycle de fonctionnement du perforateur, un emmanchement couplé aux barres de forage, et d'autre part un système de rotation pourvu d'un moteur rotatif hydraulique et configuré pour mettre en rotation l'emmanchement et les barres de forage.A roto-percussive hydraulic perforator comprises more particularly on the one hand a striking system which is driven by one or more flow rates of hydraulic fluid coming from a main hydraulic supply circuit and which comprises a striking piston configured to strike, each operating cycle of the drill, a fitting coupled to the drill bars, and on the other hand a rotation system provided with a hydraulic rotary motor and configured to rotate the fitting and the drill bars.

L'effort d'appui du perforateur hydraulique roto-percutant sur les barres de forage, et donc du taillant sur la roche, est généré par la glissière, grâce à un câble ou une chaîne d'entraînement mu(e) par un vérin hydraulique ou un moteur hydraulique. Plus précisément, l'effort d'appui est transmis du corps du perforateur à l'emmanchement par l'intermédiaire d'un élément de butée incorporé dans le corps du perforateur. Cet élément de butée peut être constitué, pour des perforateurs puissants, d'un piston de butée dont au moins une surface est alimentée hydrauliquement de façon à assurer une transmission de l'effort d'appui au moyen d'un fluide.The force of support of the roto-percussive hydraulic perforator on the drill bars, and therefore of the cutter on the rock, is generated by the slide, thanks to a cable or a drive chain moved by a hydraulic cylinder or a hydraulic motor. More precisely, the bearing force is transmitted from the body of the perforator to the fitting via an abutment element incorporated in the body of the perforator. This stop element can consist, for powerful perforators, of a stop piston, at least one surface of which is hydraulically supplied so as to ensure transmission of the bearing force by means of a fluid.

La stabilité et la performance en vitesse de pénétration d'un perforateur hydraulique roto-percutant, lorsqu'il fonctionne, dépendent notamment de la façon dont ce piston de butée est disposé et alimenté hydrauliquement.The stability and the penetration rate performance of a roto-percussive hydraulic drill, when it is operating, depend in particular on the way in which this stop piston is arranged and hydraulically powered.

Le document WO2010/082871 divulgue un perforateur hydraulique roto-percutant selon le préambule de la revendication 1, dans lequel, en conditions de fonctionnement du système de frappe, le piston de butée est positionné dans une position d'équilibre, conforme à une course de frappe souhaitée du piston de frappe, par l'intermédiaire d'une chambre de commande hydraulique délimitée par le piston de frappe et le corps du perforateur et reliée de façon permanente à un conduit d'alimentation en fluide à haute pression, la chambre de commande hydraulique étant configurée d'une part pour solliciter le piston de butée vers l'avant et d'autre part pour être reliée à un conduit de retour de fluide à basse pression lorsque la face arrière du piston de butée est située à une distance prédéterminée de la paroi arrière de la cavité recevant le piston de butée.The document WO2010/082871 discloses a roto-percussive hydraulic drill according to the preamble of claim 1, in which, under operating conditions of the striking system, the stop piston is positioned in an equilibrium position, conforming to a stroke desired impact of the impact piston, via a hydraulic control chamber delimited by the impact piston and the body of the perforator and permanently connected to a high-pressure fluid supply conduit, the hydraulic control being configured on the one hand to urge the stopper piston forwards and on the other hand to be connected to a low-pressure fluid return conduit when the rear face of the stopper piston is located at a predetermined distance of the rear wall of the cavity receiving the stop piston.

La configuration du piston de butée et du corps décris dans le document WO2010/082871 permet d'assurer un positionnement approximativement stable du piston de butée pendant le fonctionnement du système de frappe.The configuration of the thrust piston and the body described in the document WO2010/082871 makes it possible to ensure an approximately stable positioning of the stop piston during the operation of the striking system.

Cependant, les vibrations et réactions de la roche aux chocs répétés du taillant rendent instable la force d'appui de l'outil de la barre de forage sur la roche, en particulier lors des mouvements de l'outil dus à la pénétration de la barre de forage dans le terrain et aux vibrations diverses du corps du perforateur. Or, une telle instabilité de la force d'appui du taillant sur la roche nuit au positionnement de l'emmanchement par rapport au piston de frappe et donc aux performances du perforateur hydraulique.However, the vibrations and reactions of the rock to the repeated shocks of the bit make the bearing force of the drill bar tool unstable on the rock, in particular during movements of the tool due to the penetration of the bar. drilling in the ground and to the various vibrations of the body of the drill. However, such instability of the pressing force of the bit on the rock is detrimental to the positioning of the fitting relative to the striking piston and therefore to the performance of the hydraulic drill.

La présente invention vise à remédier à tout ou partie de ces inconvénients.The present invention aims to remedy all or part of these drawbacks.

Le problème technique à la base de l'invention consiste donc à fournir un perforateur hydraulique qui soit de structure simple et économique, tout en ayant des performances améliorées.The technical problem underlying the invention therefore consists in providing a hydraulic drill which is of simple and economical structure, while having improved performance.

A cet effet, la présente invention concerne un perforateur hydraulique roto-percutant comprenant :

  • un corps,
  • un emmanchement destinĂ© Ă  ĂŞtre couplĂ© Ă  au moins une barre de forage Ă©quipĂ©e d'un outil,
  • un piston de frappe montĂ© coulissant Ă  l'intĂ©rieur du corps suivant un axe de frappe et configurĂ© pour frapper l'emmanchement,
  • un piston de butĂ©e qui est tubulaire et qui est montĂ© coulissant dans une cavitĂ© du corps selon un axe de dĂ©placement sensiblement parallèle Ă  l'axe de frappe, le piston de butĂ©e comportant une face avant tournĂ©e vers l'emmanchement et destinĂ©e Ă  positionner l'emmanchement dans une position d'Ă©quilibre prĂ©dĂ©terminĂ©e par rapport au piston de frappe, et une face arrière opposĂ©e Ă  la face avant et situĂ©e en regard d'une paroi arrière de la cavitĂ©, et
  • un circuit principal d'alimentation hydraulique configurĂ© pour commander un coulissement alternatif du piston de frappe selon l'axe de frappe et pour commander un coulissement du piston de butĂ©e selon l'axe de dĂ©placement, le circuit principal d'alimentation hydraulique comportant un conduit d'alimentation en fluide Ă  haute pression et un conduit de retour de fluide Ă  basse pression,
le corps et le piston de butée délimitant au moins en partie une première chambre de commande reliée de façon permanente au conduit d'alimentation en fluide à haute pression et configurée pour solliciter le piston de butée vers l'avant, c'est-à-dire vers l'emmanchement et donc à l'opposé de la paroi arrière de la cavité, le perforateur hydraulique roto-percutant comprenant en outre un canal de liaison configuré pour relier fluidiquement la première chambre de commande au conduit de retour de fluide à basse pression lorsque la face arrière du piston de butée est située à une distance de la paroi arrière de la cavité qui est supérieure à une valeur prédéterminée,
caractérisé en ce que le circuit principal d'alimentation hydraulique comporte en outre un accumulateur basse pression relié au conduit de retour de fluide à basse pression, et en ce que le corps et le piston de butée délimitent en outre au moins en partie une deuxième chambre de commande reliée en permanence à l'accumulateur basse pression et configurée pour solliciter le piston de butée vers l'avant.To this end, the present invention relates to a roto-percussive hydraulic drill comprising:
  • a body,
  • a fitting intended to be coupled to at least one drill bar equipped with a tool,
  • a striking piston mounted to slide inside the body along a striking axis and configured to strike the fitting,
  • a stop piston which is tubular and which is slidably mounted in a cavity of the body along an axis of movement substantially parallel to the striking axis, the stop piston comprising a front face turned towards the fitting and intended to position the fitting in a predetermined equilibrium position with respect to the striking piston, and a rear face opposite the front face and located facing a rear wall of the cavity, and
  • a main hydraulic supply circuit configured to control an alternating sliding of the striking piston along the striking axis and to control a sliding of the stop piston along the axis of displacement, the main hydraulic supply circuit comprising a conduit high pressure fluid supply and a low pressure fluid return conduit,
the body and the stop piston delimiting at least in part a first control chamber permanently connected to the high-pressure fluid supply conduit and configured to urge the stop piston forwards, that is to say say towards the fitting and therefore opposite the rear wall of the cavity, the roto-percussive hydraulic perforator further comprising a connection channel configured to fluidically connect the first control chamber to the low pressure fluid return conduit when the rear face of the stop piston is located at a distance from the rear wall of the cavity which is greater than a predetermined value,
characterized in that the main hydraulic supply circuit further comprises a low pressure accumulator connected to the low pressure fluid return conduit, and in that the body and the stop piston further define at least in part a second chamber control permanently connected to the low pressure accumulator and configured to urge the stop piston forward.

Une telle configuration de la deuxième chambre de commande permet, du fait de la liaison permanente de cette dernière avec l'accumulateur basse pression, d'assurer un déplacement à grande vitesse du piston de butée vers l'avant lorsque la roche cède sous l'impact du piston de frappe et que l'emmanchement est brutalement libre d'avancer. Ceci permet de rétablir rapidement une force d'appui normale de l'outil de la barre de forage sur la roche, et ce malgré les mouvements dus à la pénétration de la barre de forage dans le terrain et les vibrations diverses du corps du perforateur.Such a configuration of the second control chamber makes it possible, due to the permanent connection of the latter with the low pressure accumulator, to ensure a high speed movement of the stop piston forwards when the rock gives way under the impact of the impact piston and that the fitting is suddenly free to move forward. This makes it possible to quickly restore a normal bearing force of the tool of the drill bar on the rock, and this despite the movements due to the penetration of the drill bar into the ground and the various vibrations of the body of the perforator.

En outre, la configuration particulière de la première chambre de commande et du canal de liaison permet de positionner le piston de butée hydrauliquement dans une position d'équilibre approximativement stable correspondant à une course de frappe optimale du piston de frappe.In addition, the particular configuration of the first control chamber and of the connecting channel makes it possible to position the stop piston hydraulically in an approximately stable equilibrium position corresponding to an optimal striking stroke of the striking piston.

Ainsi, la configuration particulière du perforateur hydraulique rotopercutant selon la présente invention lui confère des performances améliorées par rapport aux perforateurs hydrauliques roto-percutants de l'art antérieur.Thus, the particular configuration of the roto-percussion hydraulic perforator according to the present invention gives it improved performance compared to the roto-percussion hydraulic perforators of the prior art.

Le perforateur hydraulique peut en outre présenter une ou plusieurs des caractéristiques suivantes, prises seules ou en combinaison.The hydraulic drill may additionally have one or more of the following characteristics, taken alone or in combination.

Selon un mode de réalisation de l'invention, l'accumulateur basse pression est un accumulateur à membrane, tel qu'un accumulateur hydropneumatique. L'accumulateur à membrane comporte avantageusement une membrane flexible dont une première face est soumise à la pression d'un volume de gaz compressible contenu dans l'accumulateur à membrane et dont la seconde face est soumise à la pression du fluide à basse pression provenant du conduit de retour de fluide à basse pression.According to one embodiment of the invention, the low pressure accumulator is a membrane accumulator, such as a hydropneumatic accumulator. The membrane accumulator advantageously comprises a flexible membrane, a first face of which is subjected to the pressure of a volume of compressible gas contained in the membrane accumulator and the second face of which is subjected to the pressure of the low-pressure fluid coming from the low pressure fluid return line.

Selon un mode de réalisation de l'invention, la deuxième chambre de commande est reliée à l'accumulateur basse pression par un canal de retour.According to one embodiment of the invention, the second control chamber is connected to the low pressure accumulator by a return channel.

Selon un mode de réalisation de l'invention, le piston de butée comporte une première surface de commande annulaire s'étendant transversalement à l'axe de déplacement et délimitant au moins en partie la première chambre de commande et une deuxième surface de commande annulaire s'étendant transversalement à l'axe de déplacement et délimitant au moins en partie la deuxième chambre de commande, la deuxième surface de commande annulaire présentant une surface supérieure à la surface de la première surface de commande annulaire.According to one embodiment of the invention, the stop piston comprises a first annular control surface extending transversely to the displacement axis and delimiting at least in part the first control chamber and a second annular control surface s 'extending transversely to the axis of movement and delimiting at least in part the second control chamber, the second annular control surface having a surface greater than the surface of the first annular control surface.

Selon un mode de réalisation de l'invention, la première chambre de commande présente une section transversale inférieure à la section transversale de la deuxième chambre de commande.According to one embodiment of the invention, the first control chamber has a cross section smaller than the cross section of the second control chamber.

Selon un mode de réalisation de l'invention, chacune des première et deuxième surfaces de commande annulaires s'étend sensiblement perpendiculairement à l'axe de déplacement.According to one embodiment of the invention, each of the first and second annular control surfaces extends substantially perpendicular to the axis of displacement.

Selon un mode de réalisation de l'invention, la première surface de commande annulaire est plus proche de la face avant du piston de butée que la deuxième surface de commande annulaire.According to one embodiment of the invention, the first annular control surface is closer to the front face of the stop piston than the second annular control surface.

Selon un mode de réalisation de l'invention, le corps et le piston de butée délimitent au moins en partie en outre une troisième chambre de commande reliée de façon permanente au conduit de retour de fluide à basse pression, la troisième chambre de commande étant antagoniste aux première et deuxième chambres de commande.According to one embodiment of the invention, the body and the stop piston also at least partly delimit a third control chamber permanently connected to the low-pressure fluid return conduit, the third control chamber being antagonistic to the first and second control chambers.

Selon un mode de réalisation de l'invention, la troisième chambre de commande est reliée de façon permanente à l'accumulateur basse pression.According to one embodiment of the invention, the third control chamber is permanently connected to the low pressure accumulator.

Selon un mode de réalisation de l'invention, la troisième chambre de commande est configurée pour solliciter le piston de butée vers l'arrière, c'est-à-dire vers la paroi arrière de la cavité et donc à l'opposé de l'emmanchement.According to one embodiment of the invention, the third control chamber is configured to urge the stop piston towards the rear, that is to say towards the rear wall of the cavity and therefore opposite the fitting.

Selon un mode de réalisation de l'invention, la troisième chambre de commande est reliée au conduit de retour de fluide à basse pression par un canal de communication fluidique pourvu d'un orifice calibré.According to one embodiment of the invention, the third control chamber is connected to the low-pressure fluid return conduit by a fluid communication channel provided with a calibrated orifice.

Selon un mode de réalisation de l'invention, le canal de retour comporte un gicleur comprenant l'orifice calibré.According to one embodiment of the invention, the return channel comprises a nozzle comprising the calibrated orifice.

Selon un mode de réalisation de l'invention, la troisième chambre de commande présente une section transversale inférieure à la section transversale de la deuxième chambre de commande.According to one embodiment of the invention, the third control chamber has a cross section smaller than the cross section of the second control chamber.

Selon un mode de réalisation de l'invention, le piston de butée comporte le canal de liaison, et le canal de liaison comporte une première portion d'extrémité débouchant dans la troisième chambre de commande et une deuxième portion d'extrémité opposée à la première portion d'extrémité et débouchant dans une surface extérieure du piston de butée, la deuxième portion d'extrémité étant apte à être reliée fluidiquement à la première chambre de commande lorsque la face arrière du piston de butée est située à une distance de la paroi arrière de la cavité supérieure à la valeur prédéterminée.According to one embodiment of the invention, the stop piston includes the connecting channel, and the connecting channel includes a first end portion opening into the third control chamber and a second end portion opposite the first end portion and opening into an outer surface of the stopper piston, the second end portion being able to be fluidically connected to the first control chamber when the rear face of the stopper piston is located at a distance from the rear wall of the cavity greater than the predetermined value.

Selon un mode de réalisation de l'invention, le piston de butée comporte le canal de liaison.According to one embodiment of the invention, the stop piston comprises the connecting channel.

Selon un mode de réalisation de l'invention, le canal de liaison comporte une première portion d'extrémité débouchant dans la première chambre de commande et une deuxième portion d'extrémité opposée à la première portion d'extrémité et débouchant dans une surface extérieure du piston de butée, la deuxième portion d'extrémité du canal de liaison étant apte à être reliée fluidiquement au conduit de retour de fluide à basse pression lorsque la face arrière du piston de butée est située à une distance de la paroi arrière de la cavité supérieure à la valeur prédéterminée.According to one embodiment of the invention, the connecting channel comprises a first end portion opening into the first control chamber and a second end portion opposite the first end portion and opening into an outer surface of the stopper piston, the second end portion of the connecting channel being able to be fluidically connected to the low-pressure fluid return conduit when the rear face of the stopper piston is located at a distance from the rear wall of the upper cavity to the predetermined value.

Selon un mode de réalisation de l'invention, le corps comporte une gorge annulaire débouchant dans la cavité et reliée en permanence au conduit de retour de fluide à basse pression, la deuxième portion d'extrémité du canal de liaison étant apte à être reliée fluidiquement à la gorge annulaire lorsque la face arrière du piston de butée est située à une distance de la paroi arrière de la cavité supérieure à la valeur prédéterminée.According to one embodiment of the invention, the body comprises an annular groove opening into the cavity and permanently connected to the low-pressure fluid return conduit, the second end portion of the connecting channel being able to be fluidically connected to the annular groove when the rear face of the stop piston is located at a distance from the rear wall of the cavity greater than the predetermined value.

Selon un mode de réalisation de l'invention, la gorge annulaire est reliée à l'accumulateur basse pression.According to one embodiment of the invention, the annular groove is connected to the low pressure accumulator.

Selon un mode de réalisation de l'invention, le perforateur hydraulique roto-percutant comporte un canal d'alimentation reliant la première chambre de commande au conduit d'alimentation en fluide à haute pression.According to one embodiment of the invention, the rotary-percussive hydraulic drill comprises a supply channel connecting the first control chamber to the high-pressure fluid supply conduit.

Selon un mode de réalisation de l'invention, le canal d'alimentation est pourvu d'un orifice calibré.According to one embodiment of the invention, the supply channel is provided with a calibrated orifice.

Selon un mode de réalisation de l'invention, le canal d'alimentation comporte un gicleur comprenant l'orifice calibré.According to one embodiment of the invention, the supply channel comprises a nozzle comprising the calibrated orifice.

Selon un mode de réalisation de l'invention, le piston de butée est monté coulissant autour du piston de frappe.According to one embodiment of the invention, the stop piston is slidably mounted around the striking piston.

Selon un mode de réalisation de l'invention, le circuit principal d'alimentation hydraulique comporte un accumulateur haute pression relié au conduit d'alimentation en fluide à haute pression.According to one embodiment of the invention, the main hydraulic supply circuit comprises a high pressure accumulator connected to the high pressure fluid supply conduit.

Selon un mode de réalisation de l'invention, l'accumulateur haute pression est un accumulateur à membrane, tel qu'un accumulateur hydropneumatique. L'accumulateur à membrane formant l'accumulateur haute pression comporte avantageusement une membrane flexible dont une première face est soumise à la pression d'un volume de gaz compressible contenu dans l'accumulateur à membrane et dont la seconde face est soumise à la pression du fluide à haute pression provenant du conduit d'alimentation en fluide à haute pression.According to one embodiment of the invention, the high pressure accumulator is a membrane accumulator, such as a hydropneumatic accumulator. The membrane accumulator forming the high-pressure accumulator advantageously comprises a flexible membrane, a first face of which is subjected to the pressure of a volume of compressible gas contained in the membrane accumulator and the second face of which is subjected to the pressure of the high pressure fluid from the high pressure fluid supply line.

Selon un mode de réalisation de l'invention, le perforateur hydraulique roto-percutant comporte en outre un organe de butée annulaire disposé entre l'emmanchement et la face avant du piston de butée.According to one embodiment of the invention, the roto-percussive hydraulic perforator further comprises an annular stop member arranged between the fitting and the front face of the stop piston.

Selon un mode de réalisation de l'invention, l'organe de butée annulaire est une bague de butée.According to one embodiment of the invention, the annular stop member is a stop ring.

Selon un mode de réalisation de l'invention, le perforateur hydraulique roto-percutant comporte un palier de butée disposé entre la face arrière du piston de butée et la paroi arrière de la cavité. Le palier de butée peut par exemple être un palier de butée à rouleaux.According to one embodiment of the invention, the roto-percussive hydraulic drill comprises a thrust bearing arranged between the rear face of the thrust piston and the rear wall of the cavity. The thrust bearing can for example be a roller thrust bearing.

Selon un mode de réalisation de l'invention, le piston de butée comporte une surface d'appui annulaire configurée pour venir en butée contre une surface de butée annulaire du corps.According to one embodiment of the invention, the abutment piston comprises an annular bearing surface configured to come into abutment against an annular abutment surface of the body.

Selon un mode de réalisation de l'invention, la surface d'appui annulaire est configurée pour venir en butée contre la surface de butée annulaire du corps lorsque la face arrière du piston de butée est située à une distance prédéterminée de la paroi arrière de la cavité, la distance prédéterminée étant supérieure à la valeur prédéterminée.According to one embodiment of the invention, the annular bearing surface is configured to come into abutment against the annular abutment surface of the body when the rear face of the stop piston is located at a predetermined distance from the rear wall of the cavity, the predetermined distance being greater than the predetermined value.

Selon un mode de réalisation de l'invention, la surface d'appui annulaire est inclinée par rapport à l'axe de déplacement.According to one embodiment of the invention, the annular bearing surface is inclined relative to the axis of movement.

Selon un mode de réalisation de l'invention, le piston de butée comporte une collerette annulaire comportant la surface d'appui annulaire.According to one embodiment of the invention, the stop piston comprises an annular flange comprising the annular bearing surface.

Selon un mode de réalisation de l'invention, la collerette annulaire délimite au moins en partie la troisième chambre de commande.According to one embodiment of the invention, the annular collar at least partly delimits the third control chamber.

Selon un mode de réalisation de l'invention, la collerette annulaire comporte la première surface de commande annulaire.According to one embodiment of the invention, the annular flange comprises the first annular control surface.

Selon un mode de réalisation de l'invention, le corps comporte un cylindre de piston dans lequel le piston de frappe est monté coulissant de façon alternative, la cavité étant ménagée dans le corps coaxialement au cylindre de piston.According to one embodiment of the invention, the body comprises a piston cylinder in which the striking piston is slidably mounted in an alternating manner, the cavity being made in the body coaxially with the piston cylinder.

Selon un mode de réalisation de l'invention, l'emmanchement s'étend longitudinalement selon l'axe de frappe.According to one embodiment of the invention, the fitting extends longitudinally along the strike axis.

Selon un mode de réalisation de l'invention, l'emmanchement comporte une première portion d'extrémité tournée vers le piston de frappe et pourvue d'une face d'extrémité contre laquelle est destiné à frapper le piston de frappe, et une deuxième portion d'extrémité, opposée à la première portion d'extrémité, destinée à être couplée à l'au moins une barre de forage.According to one embodiment of the invention, the fitting comprises a first end portion facing the striking piston and provided with an end face against which the striking piston is intended to strike, and a second portion end, opposite the first end portion, intended to be coupled to the at least one drill bar.

Selon un mode de réalisation de l'invention, le conduit d'alimentation en fluide à haute pression est un conduit d'alimentation en fluide incompressible à haute pression, et le conduit de retour de fluide à basse pression est un conduit de retour de fluide incompressible à basse pression.According to one embodiment of the invention, the high pressure fluid supply conduit is a high pressure incompressible fluid supply conduit, and the low pressure fluid return conduit is a fluid return conduit incompressible at low pressure.

De toute façon l'invention sera bien comprise à l'aide de la description qui suit en référence aux dessins schématiques annexés représentant, à titre d'exemples non limitatifs, plusieurs formes d'exécution de ce perforateur hydraulique.

  • La figure 1 est une vue en coupe longitudinale d'un perforateur hydraulique rotopercutant selon un premier mode de rĂ©alisation de l'invention.
  • La figure 2 est une vue en coupe longitudinale, Ă  l'Ă©chelle agrandie, d'un dĂ©tail de la figure 1.
  • La figure 3 est une vue en coupe longitudinale d'un perforateur hydraulique rotopercutant selon un deuxième mode de rĂ©alisation de l'invention.
  • La figure 4 est une vue en coupe longitudinale d'un perforateur hydraulique rotopercutant selon un troisième mode de rĂ©alisation de l'invention.
  • Les figures 1 et 2 reprĂ©sentent un premier mode de rĂ©alisation d'un perforateur hydraulique rotopercutant 2 qui est destinĂ© Ă  la perforation de trous de mine, et qui est pourvu notamment d'un système de frappe et d'un système de rotation.
In any event, the invention will be better understood with the aid of the following description with reference to the appended diagrammatic drawings representing, by way of non-limiting examples, several embodiments of this hydraulic perforator.
  • The figure 1 is a view in longitudinal section of a rotapercutant hydraulic drill according to a first embodiment of the invention.
  • The figure 2 is a longitudinal sectional view, to an enlarged scale, of a detail of the figure 1 .
  • The picture 3 is a view in longitudinal section of a rotapercutant hydraulic drill according to a second embodiment of the invention.
  • The figure 4 is a view in longitudinal section of a rotapercutant hydraulic drill according to a third embodiment of the invention.
  • The figures 1 and 2 represent a first embodiment of a rotapercutant hydraulic perforator 2 which is intended for the perforation of blast holes, and which is provided in particular with a striking system and a rotation system.

Le perforateur hydraulique rotopercutant 2 comporte plus particulièrement un corps 3 comportant un cylindre de piston 4. Selon le mode de réalisation représenté sur les figures 1 et 2, le corps 1 comporte un corps principal 3.1 délimitant en partie le cylindre de piston 4, ainsi qu'une chemise avant 3.2 et une chemise arrière 3.3 montées en force dans un alésage 3.4 délimité par le corps principal 3.1.The rotapercutant hydraulic perforator 2 comprises more particularly a body 3 comprising a piston cylinder 4. According to the embodiment shown in the figures 1 and 2 , the body 1 comprises a main body 3.1 partly delimiting the piston cylinder 4, as well as a front liner 3.2 and a rear liner 3.3 force-fitted in a bore 3.4 delimited by the main body 3.1.

Le système de frappe du perforateur hydraulique rotopercutant 2 comporte un piston de frappe 5 monté coulissant de façon alternative dans le cylindre de piston 4 suivant un axe de frappe A. Comme montré plus particulièrement sur la figure 2, le piston de frappe 5 et le cylindre de piston 4 délimitent une chambre de commande primaire 6 qui est annulaire, et une chambre de commande secondaire 7 qui a une section plus importante que celle de la chambre de commande primaire 6 et qui est antagoniste à la chambre de commande primaire 6.The striking system of the rotapercutant hydraulic perforator 2 comprises a striking piston 5 mounted to slide alternately in the piston cylinder 4 along a striking axis A. As shown more particularly in the figure 2 , the striking piston 5 and the piston cylinder 4 delimit a primary control chamber 6 which is annular, and a secondary control chamber 7 which has a larger section than that of the primary control chamber 6 and which is antagonistic to the primary control chamber 6.

Le système de frappe du perforateur hydraulique rotopercutant 2 comprend en outre un distributeur de commande 8 agencé pour commander un mouvement alternatif du piston de frappe 5 à l'intérieur du cylindre de piston 4 alternativement suivant une course de frappe et une course de retour. Le distributeur de commande 8 est configuré pour mettre la chambre de commande secondaire 7, alternativement en relation avec un conduit d'alimentation en fluide à haute pression 9, tel qu'un conduit d'alimentation en fluide incompressible à haute pression, lors de la course de frappe du piston de frappe 5, et avec un conduit de retour de fluide à basse pression 11, tel qu'un conduit de retour de fluide incompressible à basse pression, lors de la course de retour du piston de frappe 5. Le conduit d'alimentation en fluide à haute pression 9 et le conduit de retour de fluide à basse pression 11 appartiennent à un circuit principal d'alimentation hydraulique dont est pourvu le système de frappe. Le circuit principal d'alimentation hydraulique peut avantageusement comporter un accumulateur haute pression 12 relié au conduit d'alimentation en fluide à haute pression 9.The striking system of the rotapercutant hydraulic perforator 2 further comprises a control valve 8 arranged to control an alternating movement of the striking piston 5 inside the piston cylinder 4 alternately following a striking stroke and a return stroke. The control distributor 8 is configured to place the secondary control chamber 7, alternately in relation with a high pressure fluid supply conduit 9, such as a high pressure incompressible fluid supply conduit, during the striking stroke of the striking piston 5, and with a low-pressure fluid return conduit 11, such as a low-pressure incompressible fluid return conduit, during the return stroke of the striking piston 5. The conduit high pressure fluid supply 9 and the low pressure fluid return conduit 11 belong to a main hydraulic supply circuit with which the striking system is provided. The main hydraulic supply circuit can advantageously include a high pressure accumulator 12 connected to the high pressure fluid supply conduit 9.

Le distributeur de commande 8 est plus particulièrement monté mobile dans un alésage ménagé dans le corps 3 entre une première position (voir la figure 2) dans laquelle le distributeur de commande 8 est configuré pour mettre la chambre de commande secondaire 7 en relation avec le conduit d'alimentation en fluide à haute pression 9 et une deuxième position dans laquelle le distributeur de commande 8 est configuré pour mettre la chambre de commande secondaire 7 en relation avec le conduit de retour de fluide à basse pression 11.The control distributor 8 is more particularly movably mounted in a bore made in the body 3 between a first position (see the figure 2 ) in which the control distributor 8 is configured to place the secondary control chamber 7 in relation to the high-pressure fluid supply conduit. pressure 9 and a second position in which the control valve 8 is configured to place the secondary control chamber 7 in relation to the low pressure fluid return conduit 11.

La chambre de commande primaire 6 est avantageusement alimentée en permanence en fluide à haute pression par un canal d'alimentation (non représenté sur les figures), de manière à ce que chaque position du distributeur de commande 8 provoque la course de frappe du piston de frappe 5, puis la course de retour du piston de frappe 5.The primary control chamber 6 is advantageously permanently supplied with high-pressure fluid via a supply channel (not shown in the figures), so that each position of the control valve 8 causes the striking stroke of the strike 5, then the return stroke of strike piston 5.

Le système de frappe du perforateur hydraulique rotopercutant 2 comprend également un piston de butée 13 qui est tubulaire et qui est monté coulissant dans une cavité 14 du corps 3 selon un axe de déplacement parallèle à l'axe de frappe A et de préférence confondu avec l'axe de frappe A. Selon le mode de réalisation représenté sur les figures 1 et 2, le piston de butée 13 est monté coulissant autour du piston de frappe 5, et la cavité 14 est ménagée dans le corps 3 coaxialement au cylindre de piston 4.The striking system of the rotapercutant hydraulic perforator 2 also comprises a stop piston 13 which is tubular and which is slidably mounted in a cavity 14 of the body 3 along an axis of movement parallel to the striking axis A and preferably coinciding with the striking axis A. According to the embodiment represented on the figures 1 and 2 , the stop piston 13 is slidably mounted around the striking piston 5, and the cavity 14 is made in the body 3 coaxially with the piston cylinder 4.

Le perforateur hydraulique rotopercutant 2 comporte en outre un emmanchement 15 destiné à être couplé, de manière connue, à au moins une barre de forage (non représentée sur les figures) équipée d'un outil. L'emmanchement 15 s'étend longitudinalement selon l'axe de frappe A, et comporte une première portion d'extrémité 16 tournée vers le piston de frappe 5 et pourvue d'une face d'extrémité 17 contre laquelle est destiné à frapper le piston de frappe 5 au cours de chaque cycle de fonctionnement du perforateur hydraulique rotopercutant 2, et une deuxième portion d'extrémité (non représentée sur les figures), opposée à la première portion d'extrémité 16, destinée à être couplée à l'au moins une barre de forage.The rotapercutant hydraulic perforator 2 further comprises a fitting 15 intended to be coupled, in known manner, to at least one drill bar (not shown in the figures) equipped with a tool. The fitting 15 extends longitudinally along the striking axis A, and comprises a first end portion 16 facing the striking piston 5 and provided with an end face 17 against which the piston is intended to strike. 5 during each operating cycle of the rotapercutant hydraulic drill 2, and a second end portion (not shown in the figures), opposite the first end portion 16, intended to be coupled to at least a drill bar.

Comme montré plus particulièrement sur la figure 2, le piston de butée 13 comportant une face avant 18 tournée vers l'emmanchement 15 et destinée à positionner l'emmanchement 15 dans une position d'équilibre prédéterminée par rapport au piston de frappe 5, et une face arrière 19 opposée à la face avant 18 et située en regard d'une paroi arrière 21 de la cavité 14.As shown more particularly on the figure 2 , the stop piston 13 comprising a front face 18 facing the fitting 15 and intended to position the fitting 15 in a predetermined position of equilibrium with respect to the striking piston 5, and a rear face 19 opposite the front face 18 and located opposite a rear wall 21 of cavity 14.

Le corps 3 et le piston de butée 13 délimitent, avec le piston de frappe 5, une première chambre de commande 22 reliée de façon permanente au conduit d'alimentation en fluide à haute pression 9 et configurée pour solliciter le piston de butée 13 vers l'avant, c'est-à-dire vers l'emmanchement 15 et donc à l'opposé de la paroi arrière 21 de la cavité 14. Le perforateur hydraulique roto-percutant 2 comporte avantageusement un canal d'alimentation 23 reliant la première chambre de commande 22 au conduit d'alimentation en fluide à haute pression 9. Selon le premier mode de réalisation représenté sur les figures 1 et 2, le canal d'alimentation 23 est pourvu d'un orifice calibré 24, qui peut par exemple être prévu sur un gicleur incorporé au canal d'alimentation 23.The body 3 and the stop piston 13 delimit, with the strike piston 5, a first control chamber 22 permanently connected to the high-pressure fluid supply conduit 9 and configured to urge the stop piston 13 towards the forward, that is to say towards the fitting 15 and therefore opposite the rear wall 21 of the cavity 14. The roto-percussive hydraulic perforator 2 advantageously comprises a supply channel 23 connecting the first chamber control 22 to the high pressure fluid supply conduit 9. According to the first embodiment shown on the figures 1 and 2 , the supply channel 23 is provided with a calibrated orifice 24, which can for example be provided on a nozzle incorporated in the supply channel 23.

Le corps 3 et le piston de butée 13 délimitent, avec le piston de frappe 5, également une deuxième chambre de commande 25 reliée à un accumulateur basse pression 26 qui appartient au circuit principal d'alimentation hydraulique du système de frappe et qui est relié au conduit de retour de fluide à basse pression 11. La deuxième chambre de commande 25 est, comme la première chambre de commande 22, également configurée pour solliciter le piston de butée 13 vers l'avant. Avantageusement, le perforateur hydraulique roto-percutant 2 comporte un canal de retour 27 reliant la deuxième chambre de commande 25 à l'accumulateur basse pression 26.The body 3 and the stop piston 13 delimit, with the striking piston 5, also a second control chamber 25 connected to a low pressure accumulator 26 which belongs to the main hydraulic supply circuit of the striking system and which is connected to the low-pressure fluid return conduit 11. The second control chamber 25 is, like the first control chamber 22, also configured to urge the stop piston 13 forwards. Advantageously, the roto-percussive hydraulic perforator 2 comprises a return channel 27 connecting the second control chamber 25 to the low pressure accumulator 26.

Selon le mode de réalisation représenté sur les figures 1 et 2, le piston de butée 13 comporte une première surface de commande annulaire 28, également nommée première surface active annulaire, s'étendant perpendiculairement à l'axe de déplacement et délimitant en partie la première chambre de commande 22, et une deuxième surface de commande annulaire 29, également nommée deuxième surface active annulaire, s'étendant perpendiculairement à l'axe de déplacement et délimitant en partie la deuxième chambre de commande 25. La deuxième surface de commande annulaire 29 présente avantageusement une surface supérieure à la surface de la première surface de commande annulaire 28. En d'autres termes, la deuxième chambre de commande 25 présente avantageusement une section transversale supérieure à la section transversale de la première chambre de commande 22.According to the embodiment shown in the figures 1 and 2 , the stop piston 13 comprises a first annular control surface 28, also called first annular active surface, extending perpendicularly to the axis of movement and partly delimiting the first control chamber 22, and a second annular control surface 29, also called the second annular active surface, extending perpendicularly to the axis of movement and partly delimiting the second control chamber 25. The second annular control surface 29 advantageously has a surface greater than the surface of the first surface of annular control 28. In other words, the second control chamber 25 advantageously has a cross section greater than the cross section of the first control chamber 22.

Le corps 3 et le piston de butée 15 délimitent également une troisième chambre de commande 31 reliée de façon permanente au conduit de retour de fluide à basse pression 11, par l'intermédiaire d'un canal de communication fluidique 32 débouchant dans la troisième chambre de commande 31 et du canal de retour 27 qui relie le canal de communication fluidique 32 au conduit de retour de fluide à basse pression 11. La troisième chambre de commande 31 est antagoniste aux première et deuxième chambres de commande 22, 25, et est ainsi configurée pour solliciter le piston de butée 13 vers l'arrière.The body 3 and the stop piston 15 also delimit a third control chamber 31 permanently connected to the low-pressure fluid return conduit 11, via a fluid communication channel 32 opening into the third control chamber. control 31 and the return channel 27 which connects the fluidic communication channel 32 to the low-pressure fluid return conduit 11. The third control chamber 31 is antagonistic to the first and second control chambers 22, 25, and is thus configured to urge the stop piston 13 rearward.

De façon avantageuse, la deuxième chambre de commande 25 est dimensionnée pour avoir une surface active sur le piston de butée 13 largement supérieure à la surface active de la troisième chambre de commande 31. Les deuxième et troisième chambres de commande 25, 31 étant reliées au canal de retour 27 et à l'accumulateur basse pression 26, le calcul de la différence des deux surfaces actives des deuxième et troisième chambres de commande 25, 31 donne une surface active résultante poussant le piston de butée 13 vers l'avant et soumise à la pression de l'accumulateur basse pression 26.Advantageously, the second control chamber 25 is sized to have an active surface on the stop piston 13 that is much greater than the active surface of the third control chamber 31. The second and third control chambers 25, 31 being connected to the channel return 27 and to the low pressure accumulator 26, the calculation of the difference of the two active surfaces of the second and third control chambers 25, 31 gives a resulting active surface pushing the stop piston 13 forwards and subjected to the pressure of the low pressure accumulator 26.

Le perforateur hydraulique roto-percutant 2 comprend de plus un canal de liaison 33 configuré pour relier fluidiquement la première chambre de commande 22 au conduit de retour de fluide à basse pression 11 lorsque la face arrière 19 du piston de butée 13 est située à une distance de la paroi arrière 21 de la cavité 14 qui est supérieure à une valeur prédéterminée. Selon le premier mode de réalisation représenté sur les figures 1 et 2, le piston de butée 13 comporte le canal de liaison 33, et le canal de liaison 33 comporte une première portion d'extrémité 33.1 débouchant dans la première chambre de commande 22 et une deuxième portion d'extrémité 33.2 opposée à la première portion d'extrémité 33.1 et débouchant dans une surface extérieure du piston de butée 13. Avantageusement, la deuxième portion d'extrémité 33.2 du canal de liaison 33 est apte à être reliée fluidiquement à une gorge annulaire 34, qui débouche dans la cavité 14 et qui est reliée en permanence au conduit de retour de fluide à basse pression 11, lorsque la face arrière 19 du piston de butée 13 est située à une distance de la paroi arrière 21 de la cavité 14 qui est supérieure à la valeur prédéterminée.Rotary-percussive hydraulic drill 2 further comprises a connecting channel 33 configured to fluidically connect the first control chamber 22 to the low-pressure fluid return conduit 11 when the rear face 19 of the stop piston 13 is located at a distance of the rear wall 21 of the cavity 14 which is greater than a predetermined value. According to the first embodiment shown in the figures 1 and 2 , the stop piston 13 includes the connecting channel 33, and the connecting channel 33 includes a first end portion 33.1 opening into the first control chamber 22 and a second end portion 33.2 opposite the first portion of end 33.1 and opening into an outer surface of the stop piston 13. Advantageously, the second end portion 33.2 of the connecting channel 33 is adapted to be fluidically connected to an annular groove 34, which opens into the cavity 14 and which is connected permanently to the low-pressure fluid return conduit 11, when the rear face 19 of the stop piston 13 is located at a distance from the rear wall 21 of the cavity 14 which is greater than the predetermined value.

Lorsque le système de frappe du perforateur hydraulique roto-percutant 2 est alimenté, la pression établie dans la première chambre de commande 22, grâce au débit d'huile qui s'est écoulé par l'orifice calibré 24, sollicite vers l'avant le piston de butée 13 jusqu'à une position telle que le canal de liaison 33 débouche dans la gorge annulaire 34 reliée en permanence au conduit de retour de fluide à basse pression 11. A ce moment-là, le piston de butée 13, qui est soumis, par la roche, à une force réactive à la force de poussée exercée par le perforateur hydraulique rotopercutant 2, cesse d'avancer, et trouve une position d'équilibre sur l'arête du débouché du canal de liaison 33 dans la gorge annulaire 34. Par construction, cette position d'équilibre permet de situer l'emmanchement 15 à une distance du piston de frappe 5 qui correspond à une course de frappe C prévue pour le piston de frappe 5. Il est à noter que l'orifice calibré 24 est avantageusement de dimension très faible par rapport au canal de liaison 33 et au canal de retour 27 de façon à ce que la pression qui s'établit dans la première chambre de commande 22 chute très rapidement lorsque le canal de liaison 33 s'ouvre dans la gorge annulaire 34. De plus, le débit qui passe par l'orifice calibré 24 doit de préférence rester faible car il est prélevé sur le conduit d'alimentation en fluide à haute pression 9.When the striking system of the roto-percussive hydraulic perforator 2 is powered, the pressure established in the first control chamber 22, thanks to the flow of oil which has flowed through the calibrated orifice 24, urges the stop piston 13 to a position such that the connecting channel 33 opens into the annular groove 34 permanently connected to the low-pressure fluid return conduit 11. At this moment, the stop piston 13, which is subjected, by the rock, to a force reactive to the thrust force exerted by the rotary-percussion hydraulic drill 2, stops advancing, and finds a position of equilibrium on the edge of the outlet of the connecting channel 33 in the annular groove 34. By construction, this equilibrium position makes it possible to locate the fitting 15 at a distance from the striking piston 5 which corresponds to a striking stroke C provided for the striking piston 5. It should be noted that the calibrated orifice 24 is advantageously of very small size by ra pport to the connecting channel 33 and to the return channel 27 so that the pressure which is established in the first control chamber 22 drops very rapidly when the connecting channel 33 opens in the annular groove 34. In addition , the flow which passes through the calibrated orifice 24 must preferably remain low because it is taken from the high-pressure fluid supply conduit 9.

Comme décrit précédemment, le débit de fluide alimentant la première chambre de commande 22 est faible, et donc, la vitesse de déplacement du piston de butée 13, issue de ce débit de fluide, est également faible. Par contre, la deuxième chambre de commande 25 est librement alimentée par l'accumulateur basse pression 26, et va permettre de pousser vers l'avant et à grande vitesse le piston de butée 13, par exemple lorsque la roche cède sous l'impact du piston de frappe 5 et que l'emmanchement 15 est brutalement libre d'avancer. Ceci permet de rétablir rapidement une force d'appui normale de l'outil de la barre de forage sur la roche, malgré les mouvements dus à la pénétration de la barre de forage dans le terrain et les vibrations diverses du corps 3 du perforateur, tout en assurant, grâce à la première chambre de commande 22, une position moyenne du piston de butée 13 qui respecte la course de frappe C prévue du piston de frappe 5.As described above, the flow rate of fluid supplying the first control chamber 22 is low, and therefore the speed of movement of the stop piston 13, resulting from this flow rate of fluid, is also low. On the other hand, the second control chamber 25 is freely supplied by the low pressure accumulator 26, and will make it possible to push the stop piston 13 forwards and at high speed, for example when the rock yields under the impact of the striking piston 5 and the fitting 15 is suddenly free to move forward. This makes it possible to quickly restore a normal bearing force of the tool of the drill bar on the rock, despite the movements due to the penetration of the drill bar into the ground and the various vibrations of the body 3 of the perforator, while by ensuring, thanks to the first control chamber 22, an average position of the stop piston 13 which respects the striking stroke C provided for the striking piston 5.

Le perforateur hydraulique roto-percutant 2 comprend également un système de rotation comportant un moteur hydraulique 35 entrainant un pignon moteur 36 et un pignon récepteur 37, de façon à assurer un mouvement de rotation de l'emmanchement 15. Le moteur hydraulique 35 est avantageusement alimenté hydrauliquement par un circuit externe d'alimentation hydraulique.The roto-percussion hydraulic drill 2 also comprises a rotation system comprising a hydraulic motor 35 driving a motor pinion 36 and a driven pinion 37, so as to ensure a rotational movement of the fitting 15. The hydraulic motor 35 is advantageously powered hydraulically by an external hydraulic supply circuit.

Lorsque le perforateur hydraulique roto-percutant 2 est en fonctionnement, l'emmanchement 15 est mis en rotation grâce au moteur hydraulique 35, et l'emmanchement 15 reçoit sur sa face d'extrémité 17 les chocs cycliques du piston de frappe 5, assurés par le système de frappe alimenté par le circuit principal d'alimentation hydraulique. Dans le même temps, l'engin porteur sur lequel est monté le perforateur hydraulique roto-percutant 2 applique une force de poussée sur la barre de forage, via le corps 3 du perforateur hydraulique rotopercutant 2 et l'emmanchement 15. A l'intérieur du perforateur, entre le corps 3 et l'emmanchement 15, cette force se transmet par l'intermédiaire du piston de butée 13 et d'un organe de butée 38, tel qu'une bague de butée, disposé entre l'emmanchement 15 et la face avant 18 du piston de butée 13. Le positionnement du piston de butée 13 est ainsi purement hydraulique et est agencé de façon à ce que la course de frappe C du piston de frappe 5 soit respectée.When the roto-percussive hydraulic drill 2 is in operation, the fitting 15 is set in rotation thanks to the hydraulic motor 35, and the fitting 15 receives on its end face 17 the cyclic shocks of the striking piston 5, ensured by the striking system supplied by the main hydraulic supply circuit. At the same time, the carrier machine on which the rotary-percussion hydraulic drill 2 is mounted applies a thrust force on the drill bar, via the body 3 of the rotary-percussion hydraulic drill 2 and the fitting 15. Inside of the perforator, between the body 3 and the fitting 15, this force is transmitted via the abutment piston 13 and a stop member 38, such as a stop ring, arranged between the fitting 15 and the front face 18 of the stop piston 13. The positioning of the stop piston 13 is thus purely hydraulic and is arranged so that the striking stroke C of the striking piston 5 is respected.

Le piston de butée 13 comporte en outre une surface d'appui annulaire 39 configurée pour venir en butée contre une surface de butée annulaire 41 du corps 3, de manière à limiter la course de déplacement du piston de butée 13 vers l'avant, c'est-à-dire vers l'emmanchement 15. Avantageusement, la surface d'appui annulaire 39 est configurée pour venir en butée contre la surface de butée annulaire 41 du corps 3 lorsque la face arrière 19 du piston de butée 13 est située à une distance prédéterminée de la paroi arrière 21 de la cavité 14, la distance prédéterminée étant supérieure à la valeur prédéterminée. Selon le premier mode de réalisation de l'invention, la surface d'appui annulaire 39 est inclinée par rapport à l'axe de déplacement, et délimite en partie la troisième chambre de commande 31.The stop piston 13 further comprises an annular bearing surface 39 configured to come into abutment against an annular stop surface 41 of the body 3, so as to limit the stroke of movement of the stop piston 13 forwards, c that is to say towards the fitting 15. Advantageously, the annular bearing surface 39 is configured to come into abutment against the annular abutment surface 41 of the body 3 when the rear face 19 of the abutment piston 13 is located at a predetermined distance from the rear wall 21 of the cavity 14, the predetermined distance being greater than the predetermined value. According to the first embodiment of the invention, the annular bearing surface 39 is inclined with respect to the axis of movement, and partly delimits the third control chamber 31.

La figure 3 représente un deuxième mode de réalisation du perforateur hydraulique rotopercutant 2 qui diffère du premier mode de réalisation essentiellement en ce que le canal de communication fluidique 32 est pourvu d'un orifice calibré 42, qui peut par exemple être prévu sur un gicleur incorporé au canal de communication fluidique 32, et en ce que la première portion d'extrémité 33.1 du canal de liaison 33 débouche dans la troisième chambre de commande 31 et la deuxième portion d'extrémité 33.2 du canal de liaison 33 débouche dans une surface extérieure du piston de butée 13, la deuxième portion d'extrémité 33.2 du canal de liaison 33 étant apte à être reliée fluidiquement à la première chambre de commande 22 lorsque la face arrière 19 du piston de butée 13 est située à une distance de la paroi arrière 21 de la cavité 14 qui est supérieure à la valeur prédéterminée.The picture 3 shows a second embodiment of the rotary-percussion hydraulic drill 2 which differs from the first embodiment essentially in that the fluidic communication channel 32 is provided with a calibrated orifice 42, which can for example be provided on a nozzle incorporated in the fluid communication 32, and in that the first end portion 33.1 of the connecting channel 33 opens into the third control chamber 31 and the second end portion 33.2 of the connecting channel 33 opens into an outer surface of the stop piston 13, the second end portion 33.2 of the connecting channel 33 being adapted to be fluidically connected to the first control chamber 22 when the rear face 19 of the stop piston 13 is located at a distance from the rear wall 21 of the cavity 14 which is greater than the predetermined value.

Lorsque le perforateur hydraulique roto-percutant 2 selon le deuxième mode de réalisation de l'invention est en fonctionnement, la première chambre de commande 22 est soumise à la haute pression, le piston de butée 13 se déplace vers l'avant jusqu'à ce que la deuxième portion d'extrémité 33.2 du canal de liaison 33 s'ouvre dans la première chambre de commande 22. L'huile sous haute pression s'écoule alors dans la troisième chambre de commande 31 dont la liaison avec le canal de retour 27 est étranglée par l'orifice calibré 42. Les première et troisième chambres de commande 22, 31 prennent alors des pressions assez proches, ce qui réduit ou annule la poussée vers l'avant du piston de butée 13. En conséquence, le piston de butée 13 va trouver une position de fonctionnement stable autour de cette position de la deuxième portion d'extrémité 33.2 du canal de liaison 33.When the roto-percussive hydraulic drill 2 according to the second embodiment of the invention is in operation, the first control chamber 22 is subjected to high pressure, the stop piston 13 moves forward until that the second end portion 33.2 of the connecting channel 33 opens into the first control chamber 22. The high-pressure oil then flows into the third control chamber 31 whose connection with the return channel 27 is throttled by the calibrated orifice 42. The first and third control chambers 22, 31 then take fairly close pressures, which reduces or cancels the forward thrust of the stop piston 13. Consequently, the stop piston 13 will find a stable operating position around this position of the second end portion 33.2 of the connecting channel 33.

Comme dans le premier mode de réalisation de l'invention, la deuxième chambre de commande 25 est librement alimentée par l'accumulateur basse pression 26, et va permettre de pousser vers l'avant et à grande vitesse le piston de butée 13, par exemple lorsque la roche cède sous l'impact du piston de frappe 5. Ceci permet de revenir rapidement à une force d'appui normale de l'outil de la barre de forage sur la roche, malgré les mouvements dus à la pénétration de la barre de forage dans le terrain et les vibrations diverses du corps 3 du perforateur, tout en assurant, grâce aux première et troisième chambres de commande 22, 31, une position moyenne du piston de butée 13 qui respecte la course de frappe C prévue du piston de frappe 5.As in the first embodiment of the invention, the second control chamber 25 is freely supplied by the low pressure accumulator 26, and will make it possible to push the stop piston 13 forwards and at high speed, for example when the rock yields under the impact of the impact piston 5. This makes it possible to quickly return to a normal pressing force of the drill bar tool on the rock, despite the movements due to the penetration of the drill bar drilling in the ground and the various vibrations of the body 3 of the perforator, while ensuring, thanks to the first and third control chambers 22, 31, an average position of the stop piston 13 which respects the planned striking stroke C of the striking piston 5.

Selon le deuxième mode de réalisation de l'invention, le piston de butée 13 comporte une collerette annulaire 43, également appelée épaulement annulaire, qui comporte la surface d'appui annulaire 39 et la première surface de commande annulaire 28. Ainsi, la collerette annulaire 43 délimite avantageusement en partie la première chambre de commande 22 et en partie la troisième chambre de commande 31.According to the second embodiment of the invention, the stop piston 13 comprises an annular flange 43, also called annular shoulder, which comprises the annular bearing surface 39 and the first annular control surface 28. Thus, the annular flange 43 advantageously partly delimits the first control chamber 22 and partly the third control chamber 31.

Selon le deuxième mode de réalisation de l'invention, le canal d'alimentation 23 est avantageusement dépourvu d'orifice calibré, ou de tout autre élément d'étranglement spécifique.According to the second embodiment of the invention, the supply channel 23 advantageously has no calibrated orifice, or any other specific throttle element.

La figure 4 représente un troisième mode de réalisation du perforateur hydraulique rotopercutant 2 qui diffère du premier mode de réalisation essentiellement en ce que le perforateur hydraulique roto-percutant 2 comporte un palier de butée 44, tel qu'un palier de butée à rouleaux, disposé entre la face arrière 19 du piston de butée 13 et la paroi arrière 21 de la cavité 14.The figure 4 shows a third embodiment of rotary-percussion hydraulic drill 2 which differs from the first embodiment essentially in that the rotary-percussion hydraulic drill 2 comprises a thrust bearing 44, such as a roller thrust bearing, disposed between the face rear 19 of the stop piston 13 and the rear wall 21 of the cavity 14.

Lorsque le système de frappe du perforateur hydraulique roto-percutant 2 n'est pas alimenté et que le système de rotation de ce dernier est en fonctionnement, l'emmanchement 15 est en rotation ainsi que l'organe de butée 38 et le piston de butée 13. Etant donné que le positionnement du piston de butée 13 dans la position d'équilibre prédéterminée ne se fait que lorsque le système de frappe est en marche (procurant ainsi le fluide nécessaire dans les première, deuxième et troisième chambres de commande 22, 25, 31), alors le piston de butée 13 est plaqué, par la force de réaction du terrain, contre non pas la paroi arrière 21 de la cavité 14 (ce qui pourrait induire une friction rotative du piston de butée 13 contre le corps 3 et donc générer des dommages à différentes pièces constitutives du perforateur), mais contre le palier de butée 44 (ce qui limite grandement l'usure du perforateur hydraulique roto-percutant 2, et ce sans addition de fluide externe au niveau du piston de butée 13).When the striking system of the roto-percussive hydraulic perforator 2 is not powered and the rotation system of the latter is in operation, the fitting 15 is in rotation as well as the stop member 38 and the stop piston 13. Since the positioning of the stop piston 13 in the predetermined equilibrium position is only done when the striking system is in operation (thus providing the necessary fluid in the first, second and third control chambers 22, 25 , 31), then the stop piston 13 is pressed, by the reaction force of the ground, against not the rear wall 21 of the cavity 14 (which could induce a rotary friction of the stop piston 13 against the body 3 and therefore generate damage to various component parts of the perforator), but against the thrust bearing 44 (which greatly limits the wear of the roto-percussive hydraulic perforator 2, and this without addition of external fluid at the level of the thrust piston 13) .

Comme il va de soi, l'invention ne se limite pas aux seules formes d'exécution de ce perforateur hydraulique, décrites ci-dessus à titre d'exemples, elle en embrasse au contraire toutes les variantes de réalisation.It goes without saying that the invention is not limited solely to the embodiments of this hydraulic perforator, described above by way of examples, on the contrary it embraces all variant embodiments.

Claims (15)

  1. A rotary percussive hydraulic perforator (2) comprising:
    - a body (3),
    - a fitting (15) intended to be coupled to at least one drilling bar equipped with a tool,
    - a striking piston (5) slidably mounted inside the body (3) along a striking axis (A) and configured to strike the fitting (15),
    - a stop piston (13) which is slidably mounted in a cavity (14) of the body (3) along an axis of displacement substantially parallel to the striking axis (A), the stop piston (13) including a front face (18) facing the fitting (15) and intended to position the fitting (15) in a predetermined equilibrium position with respect to the striking piston (5), and a rear face (19) opposite to the face front (18) and situated opposite to a rear wall (21) of the cavity (14), and
    - a main hydraulic supply circuit configured to control an alternating sliding of the striking piston (5) along the striking axis (A) and to control a sliding of the stop piston (13) along the displacement axis, the main hydraulic supply circuit including a high pressure fluid supply conduit (9) and a low pressure fluid return conduit (11),
    the body (3) and the stop piston (13) delimiting at least partially a first control chamber (22) permanently connected to the high pressure fluid supply conduit (9) and configured to bias the stop piston (13) forwards, the rotary percussive hydraulic perforator (2) further comprising a connecting channel (33) configured to fluidly connect the first control chamber (22) to the low pressure fluid return conduit (11) when the rear face (19) of the stop piston (13) is located at a distance from the rear wall (21) of the cavity (14) which is greater than a predetermined value,
    characterized in that the main hydraulic supply circuit further includes a low pressure accumulator (26) connected to the low pressure fluid return conduit (11), and in that the body (3) and the stop piston (13) further delimit at least partially a second control chamber (25) permanently connected to the low pressure accumulator (26) and configured to bias the stop piston (13) forwards.
  2. The rotary percussive hydraulic perforator (2) according to claim 1, wherein the stop piston (13) includes a first annular control surface (28) extending transversely to the axis of displacement and delimiting at least partially the first control chamber (22) and a second annular control surface (29) extending transversely to the axis of displacement and at least partially delimiting the second control chamber (25), the second annular control surface (29) having a surface area greater than the surface area of the first annular control surface (28).
  3. The rotary percussive hydraulic perforator (2) according to claim 1 or 2, wherein the body (3) and the stop piston (13) at least partially further delimit a third control chamber (31) connected permanently to the low pressure fluid return conduit (11), the third control chamber (31) being antagonistic to the first and second control chambers (22, 25).
  4. The rotary percussive hydraulic perforator (2) according to claim 3, wherein the third control chamber (31) is connected to the low pressure fluid return conduit (11) by a fluid communication channel (32) provided with a calibrated orifice (42).
  5. The rotary percussive hydraulic perforator (2) according to claim 3 or 4, wherein the stop piston (13) includes the connecting channel (33), and the connecting channel (33) includes a first end portion (33.1) opening into the third control chamber (31) and a second end portion (33.2) opposite to the first end portion (33.1) and opening into an external surface of the stop piston (13), the second end portion (33.2) of the connecting channel (33) being able to be fluidly connected to the first control chamber (22) when the rear face (19) of the stop piston (13) is located at a distance from the rear wall (21) of the cavity (14) which is greater than the predetermined value.
  6. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 4, wherein the stop piston (13) includes the connecting channel (33).
  7. The rotary percussive hydraulic perforator (2) according to claim 6, wherein the connecting channel (33) includes a first end portion (33.1) opening into the first control chamber (22) and a second end portion (33.2) opposite to the first end portion (33.2) and opening into an external surface of the stop piston (13), the second end portion (33.2) of the connecting channel (33) being able to be fluidly connected to the low pressure fluid return conduit (11) when the rear face (19) of the stop piston (13) is located at a distance from the rear wall (21) of the cavity (14) which is greater than the predetermined value.
  8. The rotary percussive hydraulic perforator (2) according to claim 7, wherein the body (3) has an annular groove (34) opening into the cavity (14) and permanently connected to the low pressure fluid return conduit (11), the second end portion (33.2) of the connecting channel (33) being able to be fluidly connected to the annular groove (34) when the rear face (19) of the stop piston (13) is located at a distance from the rear wall (21) of the cavity (14) which is greater than the predetermined value.
  9. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 8, which includes a supply channel (23) connecting the first control chamber (22) to the high pressure fluid supply conduit. (9).
  10. The rotary percussive hydraulic perforator (2) according to claim 9, wherein the supply channel (23) is provided with a calibrated orifice (24).
  11. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 10, wherein the stop piston (13) is slidably mounted around the striking piston (5).
  12. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 11, wherein the main hydraulic supply circuit includes a high pressure accumulator (12) connected to the high pressure fluid supply conduit (9).
  13. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 12, which further includes an annular stop member (38) disposed between the fitting (15) and the front face (18) of the stop piston (13).
  14. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 13, which includes a thrust bearing (44) disposed between the rear face (19) of the stop piston (13) and the rear wall (21) of the cavity (14).
  15. The rotary percussive hydraulic perforator (2) according to any one of claims 1 to 14, wherein the stop piston (13) includes an annular bearing surface (39) configured to abut against an annular stop surface (41) of the body (3).
EP19705982.7A 2018-02-14 2019-01-16 Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator Active EP3752325B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1851249A FR3077752B1 (en) 2018-02-14 2018-02-14 ROTO-PERCUTANT HYDRAULIC PERFORATOR PROVIDED WITH A CONTROL CHAMBER PERMANENTLY CONNECTED TO A LOW PRESSURE ACCUMULATOR
PCT/FR2019/050089 WO2019158834A1 (en) 2018-02-14 2019-01-16 Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator

Publications (2)

Publication Number Publication Date
EP3752325A1 EP3752325A1 (en) 2020-12-23
EP3752325B1 true EP3752325B1 (en) 2022-03-09

Family

ID=61913427

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19705982.7A Active EP3752325B1 (en) 2018-02-14 2019-01-16 Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator

Country Status (10)

Country Link
US (1) US11724379B2 (en)
EP (1) EP3752325B1 (en)
JP (1) JP2021513464A (en)
KR (1) KR20200120671A (en)
CN (1) CN111712353B (en)
AU (1) AU2019221107B2 (en)
CA (1) CA3088119C (en)
FR (1) FR3077752B1 (en)
WO (1) WO2019158834A1 (en)
ZA (1) ZA202005522B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3077753B1 (en) * 2018-02-14 2020-01-31 Montabert METHOD FOR ADJUSTING THE STRIKING STROKE OF A STRIKING PISTON OF A PERCUSSION APPARATUS, AND A PERCUSSION APPARATUS FOR CARRYING OUT SAID METHOD
FR3108931B1 (en) 2020-04-02 2022-04-08 Montabert Roger Hydraulic roto-percussive drill fitted with a fitting fitted with coupling splines
FR3120247B1 (en) 2021-03-01 2023-09-29 Montabert Roger Hydraulic rotary hammer drill equipped with a stop piston

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE8106907L (en) * 1981-11-20 1983-05-21 Atlas Copco Ab WAY TO CONTROL A PERFORMANCE AND PERFORMANCE
SE508064C2 (en) * 1993-10-15 1998-08-17 Atlas Copco Rock Drills Ab Rock drilling device with reflex damper
FR2837523B1 (en) * 2002-03-19 2004-05-14 Montabert Sa ROTO-PERCUTANT HYDRAULIC PERFORATOR HAMMER
SE533344C2 (en) * 2009-01-16 2010-08-31 Atlas Copco Rock Drills Ab Attenuation device for percussion, percussion and drilling machine
CN101927478B (en) * 2009-06-23 2015-03-04 蒙塔博特公司 Hydraulic impact equipment
FR3027543B1 (en) * 2014-10-28 2016-12-23 Montabert Roger PERCUSSION APPARATUS

Also Published As

Publication number Publication date
CN111712353B (en) 2023-03-21
CA3088119A1 (en) 2019-08-22
ZA202005522B (en) 2021-08-25
CA3088119C (en) 2024-04-23
JP2021513464A (en) 2021-05-27
EP3752325A1 (en) 2020-12-23
FR3077752B1 (en) 2020-01-31
US11724379B2 (en) 2023-08-15
AU2019221107B2 (en) 2024-04-04
FR3077752A1 (en) 2019-08-16
US20210001462A1 (en) 2021-01-07
AU2019221107A1 (en) 2020-07-30
KR20200120671A (en) 2020-10-21
WO2019158834A1 (en) 2019-08-22
CN111712353A (en) 2020-09-25

Similar Documents

Publication Publication Date Title
EP3752325B1 (en) Rotary-percussive hydraulic drill provided with a control chamber which is permanently connected to a low-pressure accumulator
FR2647870A1 (en) HYDRAULIC PERCUSSION APPARATUS WITH RETURNING SHOCK WAVE DAMPING DEVICE
EP1492648B2 (en) Hydraulic rotary-percussive hammer drill
FR2639279A1 (en) HYDRAULIC PERCUSSION APPARATUS WITH EXTRACTED RETRACT HITTING DEVICE
EP4053374B1 (en) Rotary percussion hydraulic perforator provided with a piston stop and a braking chamber
EP4052854A1 (en) Rotary percussion hydraulic perforator provided with a piston stop
EP3212362B1 (en) Percussion apparatus
EP4080011A1 (en) Rotary percussion hydraulic perforator
FR2596681A1 (en) Hydraulic percussion apparatus with a device for damping out the return shock waves
EP2616623B1 (en) Hydraulic rotary percussion apparatus for boring mine holes
WO2018091791A1 (en) Percussion apparatus
FR3108931A1 (en) Roto-percussion hydraulic perforator fitted with a shank fitted with coupling splines
FR3026041A1 (en) HYDRAULIC PERFORATION APPARATUS FOR PERFORATING MINE HOLES
WO2020201288A1 (en) Percussion apparatus with automatic regulation of the percussion-apparatus supply pressure
BE833220A (en) HYDRAULIC PERCUSSION MACHINE

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20200828

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602019012370

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: B25D0017060000

Ipc: B25D0017240000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: E21B 6/04 20060101ALI20210929BHEP

Ipc: B25D 9/14 20060101ALI20210929BHEP

Ipc: B25D 17/06 20060101ALI20210929BHEP

Ipc: B25D 17/24 20060101AFI20210929BHEP

INTG Intention to grant announced

Effective date: 20211013

INTG Intention to grant announced

Effective date: 20211104

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1473721

Country of ref document: AT

Kind code of ref document: T

Effective date: 20220315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602019012370

Country of ref document: DE

REG Reference to a national code

Ref country code: FI

Ref legal event code: FGE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20220309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220609

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220609

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220610

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220711

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220709

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602019012370

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

26N No opposition filed

Effective date: 20221212

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

REG Reference to a national code

Ref country code: AT

Ref legal event code: UEP

Ref document number: 1473721

Country of ref document: AT

Kind code of ref document: T

Effective date: 20220309

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602019012370

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20230116

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230116

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20230131

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: 20230131

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230116

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230801

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230116

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20231229

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FI

Payment date: 20240124

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20240108

Year of fee payment: 6

Ref country code: SE

Payment date: 20240119

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220309