EP4052854B1 - Hydraulischer drehschlagbohrer mit einem anschlagkolben - Google Patents

Hydraulischer drehschlagbohrer mit einem anschlagkolben Download PDF

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Publication number
EP4052854B1
EP4052854B1 EP22158565.6A EP22158565A EP4052854B1 EP 4052854 B1 EP4052854 B1 EP 4052854B1 EP 22158565 A EP22158565 A EP 22158565A EP 4052854 B1 EP4052854 B1 EP 4052854B1
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EP
European Patent Office
Prior art keywords
control chamber
piston
stop piston
pressure fluid
hammer drill
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
EP22158565.6A
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English (en)
French (fr)
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EP4052854A1 (de
EP4052854C0 (de
Inventor
François-Xavier CHEYLUS
Michel ESCOLLE
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
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Publication date
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Publication of EP4052854A1 publication Critical patent/EP4052854A1/de
Application granted granted Critical
Publication of EP4052854C0 publication Critical patent/EP4052854C0/de
Publication of EP4052854B1 publication Critical patent/EP4052854B1/de
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Anticipated expiration legal-status Critical

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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
    • B25D17/02—Percussive tool bits
    • 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
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/04—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously of the hammer piston type, i.e. in which the tool bit or anvil is hit by an impulse member
    • 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
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • 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
    • 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
    • E21B1/00—Percussion drilling
    • E21B1/12—Percussion drilling with a reciprocating impulse member
    • E21B1/24—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure
    • E21B1/26—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure by liquid pressure
    • 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
    • E21B1/00—Percussion drilling
    • E21B1/38—Hammer piston type, i.e. in which the tool bit or anvil is hit by an impulse member
    • 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
    • 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
    • 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
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0034—Details of shank profiles

Definitions

  • the present invention relates to a rotary-percussive hydraulic drill more specifically used on a drilling installation.
  • a relevant example can be found in the document FR3077752 A1 .
  • a drilling installation comprises in a known manner a rotary-percussive hydraulic perforator mounted sliding on a slide and driving one or more drilling bars, the last of these drilling bars carrying a tool called a cutting edge which in contact with the rock.
  • a perforator generally aims to drill holes of varying depth 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 bit the rotation and percussion via the drilling bars so as to penetrate the rock, and On the other hand, it provides an injection fluid so as to extract debris from the drilled hole.
  • a rotary-percussive hydraulic drill more particularly comprises 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, at each operating cycle of the drill, a fitting coupled to the drilling bars, and on the other hand a rotation system provided with a hydraulic rotary motor and configured to rotate the fitting and the drilling bars.
  • a pushing force is generally applied by the slide on the rotary-percussive hydraulic drill.
  • the thrust force is generated by the slide mainly by a cable or a drive chain, driven mainly by a hydraulic cylinder or a hydraulic motor.
  • the aforementioned thrust force is transmitted from the rotary-percussive hydraulic drill to the cutting edge via the shank and the drilling bars. More precisely, the thrust force is transmitted from the body of the perforator to the shank via a stop element incorporated in the body of the perforator.
  • This stop element can consist, for powerful perforators, of a stop piston of which at least one surface is hydraulically powered so as to ensure transmission of the thrust force by means of a fluid.
  • the thrust force must also partly compensate for the recoil force of the perforator which is mainly generated by the striking pressure and the striking frequency of the piston of typing and which grows with these parameters.
  • the cutter is only pressed against the rock by approximately the difference between the pushing force and the recoil force, as well as by the force exerted by the thrust piston on the shank.
  • WO2010/082871 discloses a rotary-percussive hydraulic perforator in which, under operating conditions of the striking system, the stop piston is positioned in an equilibrium position, conforming to a desired striking stroke of the striking piston, by means of a hydraulic control chamber delimited by the strike piston and the body of the perforator and permanently connected to a high pressure fluid supply conduit, the hydraulic control chamber being configured on the one hand to bias the stop piston forward and on the other hand to be connected to a low pressure fluid return conduit when the rear face of the stop piston is located at a predetermined distance from the rear wall of the cavity receiving the stop piston.
  • the configuration of the thrust piston and the body described in the document WO2010/082871 makes it possible to ensure approximately stable positioning of the stop piston during operation of the striking system, around a predetermined optimum working position.
  • the present invention aims to remedy all or part of these drawbacks.
  • the technical problem underlying the invention therefore consists of providing a hydraulic perforator which is simple and economical in structure, while having improved performance.
  • the particular configuration of the first control chamber and 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 specific configuration of the second control chamber makes it possible, due to the permanent connection of the latter with a fluidic communication channel provided with a calibrated orifice, to limit in amplitude the recoil movement of the stop piston because the pressure in the second control chamber increases more quickly thanks to the calibrated orifice and thus limits the stroke recoil of the stop piston. Also, when the stop piston advances, the pressure in the second control chamber decreases, again thanks to the calibrated orifice, which limits the advance force applied to the stop piston, and therefore the forward movement of the stop piston.
  • the specific configuration of the second control chamber makes it possible to better recenter the stop piston around its equilibrium position, and thereby prevent the stop piston from advancing to a front mechanical stop provided on the body, or the stop piston does not move back too much and comes into contact with the rear wall of the cavity receiving the stop piston.
  • the rotary-percussive hydraulic drill according to the present invention ensures on the one hand better support, direct or indirect, of the stop piston on the fitting and therefore optimized maintenance of the cutter against the rock during the striking phases of the striking piston, which considerably limits the risks of empty striking of the fitting and consequently the risks of damage to the fitting, the drilling bars and of the cutting edge, and on the other hand an optimized positioning of the fitting relative to the striking piston, which gives the rotary-percussive hydraulic drill according to the present invention improved performance.
  • the rotary-percussive hydraulic perforator makes it possible on the one hand to avoid reducing the strike stroke of the strike piston (and consequently to avoid limit the energy per blow of the rotary-percussive hydraulic perforator), and therefore to further increase the performance of the rotary-percussive hydraulic perforator, and on the other hand to prevent the stop piston from moving back until it touches the rear wall of the cavity, which could damage the body and the thrust piston.
  • the hydraulic drill may also have one or more of the following characteristics, taken alone or in combination.
  • the second control chamber is configured to be supplied with high pressure fluid only by the fluidic communication channel.
  • the fluidic communication channel comprises a first end portion opening into the second control chamber and a second end portion opening into an internal chamber which is partially delimited by the body and which is configured to be permanently supplied with high pressure fluid.
  • the rotary-percussive hydraulic drill comprises a main hydraulic power circuit configured to control reciprocating sliding of the striking piston along the striking axis.
  • the main hydraulic supply circuit is further configured to control sliding of the stop piston along the axis of movement, the main hydraulic supply circuit comprising the supply conduit in high pressure fluid and the low pressure fluid return line.
  • the body and the striking piston delimit at least in part a primary control chamber permanently connected to the high pressure fluid supply conduit and a secondary control chamber which is antagonistic to the primary control chamber, the rotary-percussive hydraulic drill further comprising a control distributor configured to fluidly connect the secondary control chamber alternately to the high pressure fluid supply conduit and to the low pressure fluid return conduit so as to control the strike and return strokes of the strike piston.
  • the main hydraulic supply circuit comprises a main high pressure fluid supply conduit and a main low pressure fluid return conduit
  • the body and the striking piston delimit at least in part a primary control chamber permanently connected to the main high-pressure fluid supply conduit and a secondary control chamber which is antagonistic to the primary control chamber
  • the rotary-percussive hydraulic perforator further comprising a control valve configured to fluidly connect the secondary control chamber alternately to the main high pressure fluid supply conduit and to the main low pressure fluid return conduit so as to control strike and return strokes of the piston struck.
  • the rotary-percussive hydraulic drill comprises a secondary hydraulic power circuit configured to control sliding of the stop piston along the axis of movement, the secondary hydraulic power circuit comprising the conduit high pressure fluid supply line and the low pressure fluid return line.
  • the second control chamber is permanently connected to the primary control chamber via the fluidic communication channel.
  • the second control chamber is permanently connected to the first control chamber via the fluidic communication channel.
  • the stop piston comprises a first annular control surface extending transversely to the axis of movement 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 partly the second control chamber.
  • each of the first and second annular control surfaces is oriented opposite the fitting, that is to say towards the rear wall of the cavity receiving the stop piston.
  • the second annular control surface has a surface greater than the surface of the first annular control surface.
  • each of the first and second annular control surfaces extends substantially perpendicular to the axis of movement.
  • the first annular control surface is closer to the front face of the stop piston than the second annular control surface.
  • the first annular control surface is further from the front face of the stop piston than the second annular control surface.
  • the body and the stop piston further delimit at least in part 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 configured to urge the stop piston backwards, that is to say towards the rear wall of the cavity and therefore opposite to the 'fitting.
  • the third control chamber is connected to the low pressure fluid return conduit by a channel.
  • additional fluidic communication can for example be provided with an additional calibrated orifice.
  • 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 exterior surface of the stop piston, the second end portion of the connecting channel being able to be fluidly connected 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 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 fluidly 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 which is greater than the predetermined value.
  • the connecting channel comprises a first end portion opening into the third control chamber and a second end portion opposite the first end portion and opening into an exterior surface of the stop piston, the second end portion of the connecting channel being capable of being fluidly connected to the first control chamber when the rear face of the stop piston is located at a distance from the rear wall of the cavity which is greater than the predetermined value.
  • the rotary-percussive hydraulic drill comprises a supply channel connecting the first control chamber to the high-pressure fluid supply conduit, the supply channel being provided with an orifice calibrated power supply.
  • the supply channel comprises a nozzle comprising the calibrated supply orifice.
  • the calibrated orifice has a passage section smaller than that of the calibrated supply orifice.
  • the stop piston is slidably mounted around the strike piston.
  • the main hydraulic supply circuit comprises a high pressure accumulator connected to the high pressure fluid supply conduit.
  • the main hydraulic supply circuit further comprises a low pressure accumulator connected to the low pressure fluid return conduit.
  • the third control chamber is permanently connected to the low pressure accumulator.
  • the annular groove is connected to the low pressure accumulator.
  • the rotary-percussive hydraulic drill further comprises a stop ring disposed axially between the fitting and the front face of the stop piston.
  • the stop piston comprises an annular bearing surface configured to abut against an annular stop surface of the body.
  • the annular support surface is inclined relative to the axis of movement.
  • the stop piston comprises an annular flange comprising the annular bearing surface.
  • the annular collar delimits at least partly the third control chamber.
  • the annular flange comprises the first annular control surface.
  • the annular bearing surface is configured to abut against the annular abutment surface of the body when the rear face of the abutment piston is located at a predetermined distance from the rear wall of the cavity, the predetermined distance being greater than the predetermined value.
  • the fluidic communication channel and the calibrated orifice are formed by an axial groove or an axial flat which is provided on the stop piston or on the body, and which connects the first control chamber to the second control chamber.
  • the fluid communication channel comprises a nozzle comprising the calibrated orifice.
  • the nozzle is provided with two passage orifices, one of which forms the calibrated orifice.
  • the two passage orifices can be angularly offset from each other by approximately 90° relative to a central axis of the nozzle.
  • the first control chamber is entirely delimited by the body and the stop piston.
  • the first control chamber is delimited in part by the body and the stop piston.
  • the second control chamber is entirely delimited by the body and the stop piston.
  • the second control chamber is delimited in part by the body and the stop piston.
  • the body and the striking piston partially or entirely delimit the primary control chamber.
  • the body and the striking piston partially or entirely delimit the secondary control chamber.
  • FIG. 1 is a longitudinal sectional view of a rotary-percussive hydraulic drill according to a first embodiment of the invention.
  • figure 2 is a longitudinal sectional view, on an enlarged scale, of a detail of the figure 1 .
  • FIG. 3 is a longitudinal sectional view of a rotary-percussive hydraulic drill according to a second embodiment of the invention.
  • THE figures 1 And 2 represent a first embodiment of a rotary-percussive hydraulic perforator 2 which is intended for perforating blast holes, and which is provided in particular with a striking system.
  • the rotary-percussive hydraulic drill 2 more particularly comprises a body 3 comprising a piston cylinder 4.
  • the body 3 comprises a main body 3.1 partially 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 rotary-percussive hydraulic drill 2 also includes a striking system comprising a striking piston 5 mounted slidingly alternative in the piston cylinder 4 along a striking axis A. As shown more particularly on 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 rotary-percussive hydraulic drill 2 further comprises a control distributor 8 arranged to control a reciprocating 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, alternatively in relation with a high pressure fluid supply conduit 9, such as an incompressible fluid supply conduit (for example oil) to high pressure, during the striking stroke of the striking piston 5, and with a low pressure fluid return conduit 11, such as an incompressible fluid return conduit (for example oil) at low pressure, during the return stroke of the striking piston 5.
  • the high pressure fluid supply conduit 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 comprise a high pressure accumulator 12 connected to the high pressure fluid supply conduit 9, and a low pressure accumulator 10 connected to the low pressure fluid return conduit 11.
  • the control distributor 8 is more particularly mounted movably in a bore formed 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 9 and a second position in which the control distributor 8 is configured to place the control chamber secondary control 7 in relation to the low pressure fluid return conduit 11.
  • the primary control chamber 6 is advantageously permanently supplied with high pressure fluid by a supply channel connected to the high pressure fluid supply conduit 9, so that each position of the control distributor 8 causes the stroke impact of the impact piston 5, then the return stroke of the impact piston 5.
  • the striking system of the rotary-percussive hydraulic drill 2 also includes 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 substantially parallel to the striking axis A and preferably coincident with the striking axis A.
  • the stop piston 13 is slidably mounted around the strike piston 5, and the cavity 14 is formed in the body 3 coaxially with the piston cylinder 4.
  • the rotary-percussive hydraulic drill 2 further comprises a shank 15 intended to be coupled, in a known manner, to at least one drilling bar (not shown in the figures) equipped with a tool, also called a cutting edge.
  • the fitting 15 extends longitudinally along the striking axis A, and comprises a first end portion facing the striking piston 5 and provided with an end face 17 against which is intended to strike the piston of strikes 5 during each operating cycle of the rotary-percussive hydraulic perforator 2, and a second end portion (not shown in the figures), opposite the first end portion, intended to be coupled to the at least a drill bar.
  • the stop piston 13 comprising a front face 18 facing the fitting 15 and configured to position the fitting 15 in a predetermined equilibrium position relative to the striking piston 5, and a rear face 19 opposite the front face 18 and located opposite a rear wall 21 of the cavity 14.
  • the front face 18 of the stop piston 13 is configured to apply a thrust force directly on the fitting 15 or indirectly on the fitting 15 via a stop ring 20 interposed axially between the fitting 15 and the stop piston 13.
  • the body 3 and the stop piston 13 define, 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 'front, that is to say towards the fitting 15 and therefore opposite the rear wall 21 of the cavity 14.
  • the rotary-percussive hydraulic drill 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 supply 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 also define a second control chamber 25 which is, like the first control chamber 22, configured to urge the stop piston 13 forward.
  • the second control chamber 25 is connected to the first control chamber 22 via a fluid communication channel 26 provided with a calibrated orifice 27, which can for example be provided on a nozzle incorporated in the communication channel fluid 26.
  • the second control chamber 25 is configured to be supplied with high pressure fluid only by the fluid communication channel 26.
  • the stop piston 13 comprises a first annular control surface 28, also called first annular active surface, extending perpendicular to the axis of movement and partly delimiting the first control chamber 22, and a second annular control surface 29, also called second annular active surface, extending perpendicular to the axis of movement and partially 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 body 3 and the stop piston 13 also delimit a third control chamber 31 permanently connected to the low pressure fluid return conduit 11, via an additional fluid communication channel 32 opening into the third chamber control chamber 31.
  • 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 towards the rear.
  • the rotary-percussive hydraulic drill 2 further comprises 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 of the rear wall 21 of the cavity 14 which is greater than a predetermined value.
  • the stop piston 13 comprises the connecting channel 33
  • the connecting channel 33 comprises 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 exterior surface of the stop piston 13.
  • the second end portion 33.2 of the connecting channel 33 is capable of being fluidly 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 stop piston stop 13 which is subjected, by the rock, to a force reactive to the thrust force exerted by the rotary-percussive hydraulic perforator 2, stops advancing, and finds an equilibrium position on the edge of the outlet of the channel connection 33 in the annular groove 34.
  • 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.
  • the calibrated supply orifice 24 is advantageously small in relation to the connection channel 33 and the additional fluid communication channel 32 so that the pressure which is established in the first control chamber 22 drops very quickly when the connecting channel 33 opens in the annular groove 34.
  • the calibrated orifice 27, of smaller section than the calibrated supply orifice 24, will gradually fill the second control chamber 25 with high pressure fluid, the pressure had dropped due to the increase in the volume of the second control chamber 25 (resulting from the advance movement of the stop piston 13) and the presence of the calibrated orifice 27 which prevents rapid filling of the second chamber order 25.
  • the pressure in the first control chamber 22 will increase to a first pressure level greater than the supply pressure thanks to the presence of the calibrated supply orifice 24, and the pressure in the second control chamber 25 will increase to a pressure level much higher than that of the first control chamber 22 thanks to the presence of the calibrated orifice 27 whose section is lower to that of the calibrated supply orifice 24.
  • the second annular control surface 29 being larger than the first annular control surface 28, and the level of pressure exerted on the second annular control surface 29 being much greater than that of the calibrated supply orifice 24. exerted on the first annular control surface 28, itself greater than it would have been without the presence of the calibrated supply orifice 24, the advance force exerted on the stop piston 13 becomes very significant, such that the recoil distance of the stop piston 13 will be small.
  • the pressures in the first and second control chambers 22, 25 increase rapidly because their volume remains substantially constant and they are force-fed.
  • high pressure fluid through the calibrated supply orifice 24 specifically calibrated in order to optimize the effectiveness of this feeding, the hydraulic resistance in the face of a sudden recoil of the stop piston 13 and the modulation of the pressure in the first control chamber 22.
  • the striking frequency of a hydraulic perforator generally exceeding 50 Hz, the cycle times of the striking piston 5 are very short, which allows, with the aforementioned architecture of the power system of the stop piston 13, to be able to play with the compressibility of the hydraulic fluid much more than with the supply flow rates.
  • the oil contained in the first control chamber 22 will only leave very little in the low pressure fluid return conduit 11 via the opening of the connecting channel 33, because the stop piston 13 will not be pushed too far forward in relation to the hydraulic equilibrium position thanks to the mechanisms previously explained.
  • the rotary-percussive hydraulic drill 2 also comprises a rotation drive system which is configured to rotate the fitting 15 around an axis of rotation which is substantially coincident with the striking axis A.
  • the system rotational drive comprises a member coupling member 35, such as a coupling pinion, which is tubular and which is arranged around the fitting 15.
  • the coupling member 35 comprises male coupling splines and female coupling splines which are coupled in rotation respectively with female and male coupling splines provided on the fitting 15.
  • the coupling member 35 comprises external peripheral teeth coupled in rotation with an output shaft of a drive motor 36, such as a hydraulic motor supplied hydraulically by an external hydraulic supply circuit, belonging to the rotational drive system.
  • the rotational drive system can for example comprise an intermediate pinion 37 which is coupled on the one hand to the output shaft of the drive motor 36 and on the other hand to the external peripheral teeth of the gearing member. coupling 35.
  • the fitting 15 When the rotary-percussive hydraulic drill 2 is in operation, the fitting 15 is rotated thanks to the drive motor 36, and the fitting 15 receives on its end face 17 the cyclic shocks of the striking piston 5, ensured by the striking system powered by the main hydraulic power circuit.
  • the carrier on which the hydraulic roto-percussive drill 2 is mounted applies a thrust force on the drilling bar, via the body 3 and the shank 15. Inside the hydraulic roto-percussive drill impacting 2, between the body 3 and the fitting 15, this thrust force is transmitted via the stop piston 13 and the stop ring 20.
  • 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 abut against an annular stop surface 41 provided on the body 3, so as to limit the forward movement of the stop piston 13. , that is to say towards the fitting 15.
  • the annular bearing surface 39 is configured to abut 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 support surface 39 is inclined relative to the axis of movement, and partly delimits the third control chamber 31.
  • FIG. 3 represents a second embodiment of the rotary-percussive hydraulic drill 2 which differs from the first embodiment essentially in that the additional fluidic communication channel 32 is provided with an additional calibrated orifice 42, which can for example be provided on a nozzle incorporated in the additional fluidic communication channel 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 exterior surface of the stop piston 13, the second end portion 33.2 of the connecting channel 33 being capable of being 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.
  • the additional fluidic communication channel 32 is provided with an additional calibrated orifice 42, which can for example be provided on a nozzle incorporated in the additional fluidic communication channel 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 exterior
  • the first control chamber 22 When the rotary-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 oil under high pressure then flows into the third control chamber 31 which connects with the return channel 27 is throttled by the additional 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 piston of stop 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 connected to the first control chamber 22 via a fluid communication channel 26 provided with a calibrated orifice 27, performing the same function as in the first embodiment.
  • the fluid communication channel 26 is however provided on the body 3, and for example on the rear jacket 3.3.
  • 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 may be devoid of a calibrated orifice, or of any other specific throttling element.
  • the first control chamber 22 is delimited only by the body 3 and the stop piston 13 and the second control chamber 25 is delimited by the body 3, the stop piston 13 and the striking piston 5.
  • the fluidic communication channel 26 could be configured to connect the second control chamber 25 to the primary control chamber 6, still being provided with a calibrated orifice 27.
  • the fluidic communication channel 26 and the calibrated orifice 27 could be formed by a calibrated axial flat or a calibrated axial groove connecting either the first control chamber 22 to the second control chamber 25 or either the primary control chamber 6 to the second control chamber 25.
  • the calibrated axial flat or the calibrated axial groove can for example be provided on the body 3 or the stop piston 13.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (15)

  1. Hydraulischer Drehschlagbohrer (2), der Folgendes umfasst:
    - einen Körper (3),
    - einen Schaft (15), der dazu bestimmt ist, mit mindestens einer Bohrstange verbunden zu werden, die mit einem Werkzeug ausgestattet ist,
    - einen Schlagkolben (5), der im Inneren des Körpers (3) entlang einer Schlagachse (A) gleitend montiert und dazu konfiguriert ist, auf den Schaft (15) zu schlagen,
    - einen Anschlagkolben (13), der in einem Hohlraum (14) des Körpers (3) entlang einer Verschiebungsachse, die im Wesentlichen parallel zur Schlagachse (A) liegt, gleitend montiert ist, wobei der Anschlagkolben (13) eine Vorderseite (18), die dem Schaft (15) zugewandt und dazu konfiguriert ist, den Schaft (15) in einer in Bezug auf den Schlagkolben (5) vorbestimmten ausgeglichenen Position zu positionieren, und eine Rückseite (19) aufweist, die der Vorderseite (18) entgegengesetzt ist und sich gegenüber einer hinteren Wand (21) des Hohlraums (14) befindet, und
    - eine Hochdruck-Fluidversorgungsleitung (9) und eine Niederdruck-Fluidrücklaufleitung (11),
    wobei der Körper (3) und der Anschlagkolben (13) mindestens teilweise eine erste Steuerkammer (22) begrenzen, die permanent mit der Hochdruck-Fluidversorgungsleitung (9) verbunden und dazu konfiguriert ist, den Anschlagkolben (13) nach vorne zu drücken, wobei der Anschlagkolben (13) ferner einen Verbindungskanal (33) umfasst, der dazu konfiguriert ist, die erste Steuerkammer (22) mit der Niederdruck-Fluidrücklaufleitung (11) fluidisch zu verbinden, wenn sich die Rückseite (19) des Anschlagkolbens (13) in einem Abstand von der hinteren Wand (21) des Hohlraums (14) befindet, der größer als ein vorbestimmter Wert ist,
    wobei der Körper (3) und der Anschlagkolben (13) ferner mindestens teilweise eine zweite Steuerkammer (25) begrenzen, die dazu konfiguriert ist, den Anschlagkolben (13) nach vorne zu drücken,
    dadurch gekennzeichnet, dass der hydraulische Drehschlagbohrer (2) einen Fluidverbindungskanal (26) umfasst, der in die zweite Steuerkammer (25) mündet und der dazu konfiguriert ist, die zweite Steuerkammer (25) mit Hochdruckfluid zu versorgen, wobei der Fluidverbindungskanal (26) mit einer kalibrierten Öffnung (27) versehen ist.
  2. Hydraulischer Drehschlagbohrer (2) nach Anspruch 1, der einen hydraulischen Hauptversorgungskreis umfasst, der dazu konfiguriert ist, ein abwechselndes Gleiten des Schlagkolbens (5) entlang der Schlagachse (A) zu steuern.
  3. Hydraulischer Drehschlagbohrer (2) nach Anspruch 2, wobei der hydraulische Hauptversorgungskreis ferner dazu konfiguriert ist, ein Gleiten des Anschlagkolbens (13) entlang der Verschiebungsachse zu steuern, wobei der hydraulische Hauptversorgungskreis die Hochdruck-Fluidversorgungsleitung (9) und die Niederdruck-Fluidrücklaufleitung (11) enthält.
  4. Hydraulischer Drehschlagbohrer (2) nach Anspruch 3, wobei der Körper (3) und der Schlagkolben (5) mindestens teilweise eine primäre Steuerkammer (6), die permanent mit der Hochdruck-Fluidversorgungsleitung (9) verbunden ist, und eine sekundäre Steuerkammer (7) begrenzen, die antagonistisch zur primären Steuerkammer (6) ist, wobei der hydraulische Drehschlagbohrer (2) ferner einen Steuerverteiler (8) enthält, der dazu konfiguriert ist, die sekundäre Steuerkammer (7) abwechselnd mit der Hochdruck-Fluidversorgungsleitung (9) und der Niederdruck-Fluidrücklaufleitung (11) fluidisch zu verbinden, um die Schlag-und Rücklaufhübe des Schlagkolbens (5) zu steuern.
  5. Hydraulischer Drehschlagbohrer (2) nach Anspruch 4, wobei die zweite Steuerkammer (25) über den Fluidverbindungskanal (26) permanent mit der primären Steuerkammer (6) verbunden ist.
  6. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 4, wobei die zweite Steuerkammer (25) über den Fluidverbindungskanal (26) permanent mit der ersten Steuerkammer (22) verbunden ist.
  7. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 6, wobei der Anschlagkolben (13) eine erste ringförmige Steuerfläche (28), die sich quer zur Verschiebungsachse erstreckt und mindestens teilweise die erste Steuerkammer (22) begrenzt, und eine zweite ringförmige Steuerfläche (29) enthält, die sich quer zur Verschiebungsachse erstreckt und mindestens teilweise die zweite Steuerkammer (25) begrenzt.
  8. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 7, wobei der Körper (3) und der Anschlagkolben (13) ferner mindestens teilweise eine dritte Steuerkammer (31) begrenzen, die permanent mit der Niederdruck-Fluidrücklaufleitung (11) verbunden ist, wobei die dritte Steuerkammer (31) antagonistisch zu der ersten und der zweiten Steuerkammer (22, 25) ist.
  9. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 8, wobei der Verbindungskanal (33) einen ersten Endabschnitt (33.1), der in die erste Steuerkammer (22) mündet, und einen zweiten Endabschnitt (33.2) enthält, der dem ersten Endabschnitt (33.2) gegenüberliegt und in eine Außenfläche des Anschlagkolbens (13) mündet, wobei der zweite Endabschnitt (33.2) des Verbindungskanals (33) dazu ausgelegt ist, mit der Niederdruck-Fluidrücklaufleitung (11) fluidisch verbunden zu werden, wenn sich die Rückseite (19) des Anschlagkolbens (13) in einem Abstand von der Rückwand (21) des Hohlraums (14) befindet, der größer als der vorbestimmte Wert ist.
  10. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 8, wobei der Verbindungskanal (33) einen ersten Endabschnitt (33.1), der in die dritte Steuerkammer (31) mündet, und einen zweiten Endabschnitt (33.2) enthält, der dem ersten Endabschnitt (33.1) gegenüberliegt und in eine Außenfläche des Anschlagkolbens (13) mündet, wobei der zweite Endabschnitt (33.2) des Verbindungskanals (33) dazu ausgelegt ist, mit der ersten Steuerkammer (22) fluidisch verbunden zu werden, wenn sich die Rückseite (19) des Anschlagkolbens (13) in einem Abstand von der Rückwand (21) des Hohlraums (14) befindet, der größer als der vorbestimmte Wert ist.
  11. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 10, der einen Versorgungskanal (23) umfasst, der die erste Steuerkammer (22) mit der Hochdruck-Fluidversorgungsleitung (9) verbindet, wobei der Versorgungskanal (23) mit einer kalibrierten Versorgungsöffnung (24) versehen ist.
  12. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 11, wobei der Anschlagkolben (13) gleitend um den Schlagkolben (5) herum montiert ist.
  13. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 12, der ferner einen Anschlagring (20) enthält, der axial zwischen dem Schaft (15) und der Vorderseite (18) des Anschlagkolbens (13) angeordnet ist.
  14. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 13, wobei der Fluidverbindungskanal (26) und die kalibrierte Öffnung (27) durch eine axiale Nut oder eine axiale Abflachung gebildet werden, die am Anschlagkolben (13) oder am Körper (3) vorgesehen ist und die erste Steuerkammer (22) mit der zweiten Steuerkammer (25) verbindet.
  15. Hydraulischer Drehschlagbohrer (2) nach einem der Ansprüche 1 bis 13, wobei der Fluidverbindungskanal (26) eine Düse enthält, die die kalibrierte Öffnung (27) umfasst.
EP22158565.6A 2021-03-01 2022-02-24 Hydraulischer drehschlagbohrer mit einem anschlagkolben Active EP4052854B1 (de)

Applications Claiming Priority (1)

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FR2101949A FR3120247B1 (fr) 2021-03-01 2021-03-01 Perforateur hydraulique roto-percutant pourvu d’un piston de butée

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JP (1) JP7801911B2 (de)
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CN (1) CN115075723A (de)
AU (1) AU2022201351A1 (de)
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FR3108931B1 (fr) * 2020-04-02 2022-04-08 Montabert Roger Perforateur hydraulique roto-percutant pourvu d’un emmanchement équipé de cannelures d’accouplement

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FR2355617A1 (fr) * 1975-12-18 1978-01-20 Montabert Roger Machine de percussion
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KR20220123595A (ko) 2022-09-08
JP2022133250A (ja) 2022-09-13
CA3149887A1 (fr) 2022-09-01
EP4052854A1 (de) 2022-09-07
EP4052854C0 (de) 2024-07-17
US20220274240A1 (en) 2022-09-01
FR3120247A1 (fr) 2022-09-02
JP7801911B2 (ja) 2026-01-19
CN115075723A (zh) 2022-09-20
FR3120247B1 (fr) 2023-09-29
US11697197B2 (en) 2023-07-11
ZA202202360B (en) 2022-09-28
CA3149887C (fr) 2026-03-03
AU2022201351A1 (en) 2022-09-15

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