EP1492648B2 - Hydraulic rotary-percussive hammer drill - Google Patents

Hydraulic rotary-percussive hammer drill Download PDF

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Publication number
EP1492648B2
EP1492648B2 EP03725300A EP03725300A EP1492648B2 EP 1492648 B2 EP1492648 B2 EP 1492648B2 EP 03725300 A EP03725300 A EP 03725300A EP 03725300 A EP03725300 A EP 03725300A EP 1492648 B2 EP1492648 B2 EP 1492648B2
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EP
European Patent Office
Prior art keywords
hammer drill
piston
chamber
circuit
stop piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03725300A
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German (de)
French (fr)
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EP1492648B1 (en
EP1492648A1 (en
Inventor
Jean-Sylvain Comarmond
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Montabert SAS
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Montabert SAS
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • 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
    • B25D9/06—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

Definitions

  • the present invention relates to a roto-percussion hydraulic rotary hammer according to the preamble of claim 1.
  • a hammer perforator is known from the document WO 02/01 041 and is especially used on a drilling rig.
  • a drilling rig includes a roto-percussion hydraulic rotary hammer sliding on a slide and driving one or more drill bars, the last of these bars carrying a tool called cutting which is rock contact.
  • a hammer perforator generally aims to drill more or less deep holes in order to place explosive charges.
  • the hammer drill is thus the main element which, on the one hand, confers on the cutter the rotation and the percussion by means of the drill bars so as to penetrate the rock, and on the other hand, provides an injection fluid so as to extract debris from the drilled hole.
  • a hammer drill comprises a mechanism, driven by one or more hydraulic fluid flows from a main power supply circuit of the striking mechanism, acting on the drill bars through a fitting which is adapted to retransmit, on the one hand, the successive shocks caused by a striking piston, and on the other hand, the rotation due to a hydraulic rotary motor.
  • the support force of the hammer drill on the drill bars, and thus by transmission of the cutter on the rock, is obtained using the hydraulic motor of the slide. More specifically, the bearing force is transmitted from the body of the hammer drill to the fitting via a stop element incorporated in the hammer drill.
  • This abutment element may consist of a fixed piece of rotary friction, but more generally, for powerful hammer drills, a stop piston whose surface is hydraulically supplied so as to ensure a transmission of the force of support by means of a fluid.
  • the hammer drill according to the present invention aims to solve the problem mentioned above and for this comprises a body enclosing a reciprocating plunger piston sliding under the effect of a main hydraulic supply circuit, this main circuit being also intended to cause the sliding of a substantially annular abutment piston housed in a cavity of the body and having, on the one hand, a front face for positioning a fitting at a predetermined distance from the striking piston, and secondly, a rear face located opposite a rear wall of the cavity, an external hydraulic supply circuit being adapted, when stopping the main supply circuit, to introduce a fluid under pressure between the rear face of the piston of the abutment and the rear wall of the cavity so as to maintain a space therebetween, and is characterized in that the abutment piston has a front part, an ep a central portion and a rear portion, said central shoulder being flanked by an annular front chamber and an annular rear chamber, and the main supply circuit is for delivering a fluid directly into the rear chamber and a connecting channel is for
  • the external supply circuit opens into the rear wall of the cavity and a sliding annular liner is placed around the rear portion of the stop piston and is able, on the one hand, to prevent the introduction of the fluid delivered by the external supply circuit when the pressure in the annular rear chamber is greater than or equal to a determined value (P), and secondly, allow the introduction of this fluid when the pressure in the annular rear chamber is less than the determined value (P).
  • the rear face of the stop piston is put under the pressure of a drain by means of a first channel.
  • the front chamber is also placed in communication with the drain by means of a second channel when the fitting is at a distance from the striking piston less than the predetermined distance.
  • the stop piston is intended to slide inside a guide integral with the body.
  • the liner has a rear portion having, on the one hand, an outer shoulder having a first rear surface intended to cooperate with the external supply circuit, and on the other hand, an internal recess having a second rear surface offset.
  • a substantially annular chamber connected to the main circuit is provided between the outer shoulder of the liner and a rear end of the guide.
  • the front face of the stop piston advantageously has a diameter substantially greater than that of the rear face.
  • a hammer drill 1 has a body 2 comprising a cavity 3 which extends rearwardly in a bore 31 containing a striking piston 4. More specifically, the cavity 3 encloses a substantially annular abutment piston 5 which is slidable around the striking piston 4, an annular sleeve 6, a fitting 7 and a rotary motor 8. The fitting 7 is connected to drill bars 9 which act on a cutting edge 10 in contact with the rock 11.
  • the stop piston 5 has a front portion, a central shoulder 12 and a rear portion, the central shoulder having a front annular surface 25 and a rear annular surface 26.
  • the piston abutment is provided respectively with a front face 13 and a rear face 14. More particularly, the front face 13 is in contact with the fitting 7 and the rear face 14 is opposite a rear wall 15 of the cavity 3.
  • the liner 6 is placed around the rear portion of the stop piston 5 and is slidably sealable therealong.
  • the front portion of the stop piston 5, the front surface 25 of the central shoulder 12 and the body 2 define a front chamber 16 annular.
  • the rear portion of the stop piston 5, the rear surface 26 of the central shoulder 12, the body 2 and the liner 6 define an annular rear chamber 17.
  • a connecting channel 18 is provided so that, in operation, put the front chamber 16 and the rear chamber 17 at the same pressure.
  • a first channel 30 longitudinally traversing the stop piston 5 over its entire rear portion makes it possible to put the rear face 14 of the stop piston 5 at the pressure of a drain 19 via a groove 20.
  • a second channel 21 formed in the front portion of the stop piston allows the communication of the front chamber 16 with the groove 20 and the drain 19.
  • a main hydraulic supply circuit 22 for the hammer drill 1 is connected to the bore 31 containing the striking piston 4, but also to the rear chamber 17.
  • an external hydraulic supply circuit 23 independent of the main circuit 22 has an end opening into the rear end 15 of the cavity 3 at the level of the jacket 6.
  • the hydraulic motor of the slide (not shown) containing the hammer drill 1 applies a bearing force on the body 2, as illustrated by the arrow 24.
  • This bearing force is transmitted to the stop piston 5 by means of of the main circuit 22, which generates a fluid underpressure in the rear chamber 17 so as to exert stresses on the rear surface 26 of the shoulder 12 and on the liner 6.
  • the stop piston 5 is then caused to slide towards the front and transmits the support force by its front face 13 to the fitting 7, and thus to the drill bars 9 and the cutter 10.
  • the sleeve 6 is pushed back and closes the circuit external 15.
  • the stop piston 5 stops its stroke because a pressure balance is established between the front chamber 16 and the rear chamber 17 so that the fitting 7 is then placed at a predetermined adequate distance of the striking piston 4. It should be noted that the fitting 7 is held in this position because, if it tended to retreat, the second channel 21 would be able to put the chamber before 16 in communication with the drain 19, which would have the effect of displacing the thrust piston 5 forward. Finally, the striking piston 4 can strike the fitting 7 by sliding in its housing 31 under the effect of the pressure of the fluid of the main circuit 22. Similarly, the rotary motor can be actuated and act on the fitting 7 .
  • This hammer drill 101 has a body 102 and differs mainly from that shown in FIGS. Figures 1 to 3 in that, on the one hand, the stop piston 5 is now slid inside a guide 103 integral with the body 102, and on the other hand, the sleeve 6 is replaced by a jacket 106 provided with an outer shoulder 107 and an internal recess.
  • the outer shoulder 107 has a first rear surface 108 intended to cooperate with the external circuit 23 and the inner recess has a second rear surface 109 offset from the first rear surface 108. In operation, this second rear surface 109 is then put under the pressure of the drain 19.
  • a substantially annular chamber 110 is provided between the outer shoulder 107 and a rear end 111 of the guide 103, and this annular chamber 110 is connected to the main hydraulic supply circuit 22 .
  • the operation of the hammer drill 101 is similar to that described above for the hammer drill 1. It should be noted only that when the hammer drill 101 is fed by the main circuit 22, the underpressure fluid is delivered in the rear chamber 17 but also in the chamber 110.
  • the advantage of this particular embodiment of the invention lies in the fact that the front surface 25 and the rear surface 26 of the shoulder 12 of the stop piston 5, as well as the first and second surfaces
  • the backs 107, 108 of the liner 106 can be easily selected so that the minimum pressure generated by the external circuit 23 necessary for the displacement of the liner 106 is much greater than the pressure generated by the main circuit 22 in the rear chamber 17. and the room 110.
  • the figure 6 describes a hammer drill 201 which differs from the hammer drill 101 shown in FIGS. Figures 4 and 5 only by the fact that the front face 13 of the stop piston 5 has a diameter substantially greater than that of the rear face 14. In operation, this has the effect of pushing the piston forward, even beyond its position equilibrium, because when the front chamber 16 and the rear chamber 17 are at an identical pressure, the difference in diameter between the front face 13 and the rear face 14 induces the creation of an additional annular section thrust forward . This then has the advantage of allowing the front face 13 of the stop piston 5 to remain longer in contact with the fitting 7 despite the important vibratory movements related to the percussion of the striking piston 4 on the fitting 7.

Abstract

The hammer drill (1) comprises a body (2) containing an alternating impact piston (4) which slides under the effect of a main hydraulic supply circuit (22). The circuit also causes an annular stop piston (5) to slide in a body cavity (3). The stop piston comprises a front face, in contact with an insert (7), which positions the insert at a pre-determined distance from the impact piston. When the main circuit is stopped, an external hydraulic supply circuit (23) can introduce pressurized fluid between the stop piston rear face and the cavity rear wall so as to maintain a space between them.

Description

La présente invention se rapporte à un marteau perforateur hydraulique roto-percutant selon le préambule de la revendication 1. Un tel marteau perforateur est connu du document WO 02/01 041 et est plus spécialement utilisé sur une installation de forage.The present invention relates to a roto-percussion hydraulic rotary hammer according to the preamble of claim 1. Such a hammer perforator is known from the document WO 02/01 041 and is especially used on a drilling rig.

Une installation de forage comprend un marteau perforateur hydraulique roto-percutant coulissant sur une glissière et entraînant une ou plusieurs barres de forage, la dernière de ces barres portant un outil appelé taillant qui est contact de la roche. Un tel marteau perforateur a généralement pour objectif de forer des trous plus ou moins profonds afin de pouvoir y placer des charges explosives. Le marteau perforateur est donc l'élément principal 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 includes a roto-percussion hydraulic rotary hammer sliding on a slide and driving one or more drill bars, the last of these bars carrying a tool called cutting which is rock contact. Such a hammer perforator generally aims to drill more or less deep holes in order to place explosive charges. The hammer drill is thus the main element which, on the one hand, confers on the cutter the rotation and the percussion by means of the drill bars so as to penetrate the rock, and on the other hand, provides an injection fluid so as to extract debris from the drilled hole.

Un marteau perforateur comprend un mécanisme, animé par un ou plusieurs débits de fluide hydraulique provenant d'un circuit principal d'alimentation du mécanisme de frappe, agissant sur les barres de forage par l'intermédiaire d'un emmanchement qui est apte à retransmettre, d'une part, les chocs successifs provoqués par un piston de frappe, et d'autre part, la mise en rotation due à un moteur rotatif hydraulique.A hammer drill comprises a mechanism, driven by one or more hydraulic fluid flows from a main power supply circuit of the striking mechanism, acting on the drill bars through a fitting which is adapted to retransmit, on the one hand, the successive shocks caused by a striking piston, and on the other hand, the rotation due to a hydraulic rotary motor.

L'effort d'appui du marteau perforateur sur les barres de forage, et donc par transmission du taillant sur la roche, est obtenu à l'aide du moteur hydraulique de la glissière. Plus précisément, l'effort d'appui est transmis du corps du marteau perforateur à l'emmanchement par l'intermédiaire d'un élément de butée incorporé dans le marteau perforateur. Cet élément de butée peut être constitué d'une pièce fixe de frottement rotatif, mais plus généralement, pour des marteaux perforateurs puissants, d'un piston de butée dont une surface est alimentée hydrauliquement de façon à assurer une transmission de l'effort d'appui au moyen d'un fluide.The support force of the hammer drill on the drill bars, and thus by transmission of the cutter on the rock, is obtained using the hydraulic motor of the slide. More specifically, the bearing force is transmitted from the body of the hammer drill to the fitting via a stop element incorporated in the hammer drill. This abutment element may consist of a fixed piece of rotary friction, but more generally, for powerful hammer drills, a stop piston whose surface is hydraulically supplied so as to ensure a transmission of the force of support by means of a fluid.

Les demandes de brevet européen EP 0 058 650 et EP 0 856 637 divulguent des dispositions de piston de butée pour lesquelles l'alimentation hydraulique provient du circuit principal d'alimentation du mécanisme de frappe. Mais, lorsque l'opérateur ferme ce circuit principal d'alimentation et n'active par exemple que le moteur rotatif, la surface du piston de butée n'est plus alimentée hydrauliquement et le piston peut donc entrer en contact direct avec le corps du marteau perforateur, ce qui peut entraîner des dégâts considérables.Requests for European patent EP 0 058 650 and EP 0 856 637 disclose thrust piston arrangements for which the hydraulic supply is from the main feed circuit of the striking mechanism. But when the operator closes this main supply circuit and activates for example only the rotary motor, the surface of the stop piston is no longer fed hydraulically and the piston can therefore come into direct contact with the body of the hammer. perforator, which can lead to considerable damage.

Le marteau perforateur selon la présente invention a pour but de résoudre le problème évoqué ci-dessus et pour cela comprend un corps renfermant un piston de frappe alternatif coulissant sous l'effet d'un circuit principal d'alimentation hydraulique, ce circuit principal étant également destiné à provoquer le coulissement d'un piston de butée sensiblement annulaire logé dans une cavité du corps et possédant, d'une part, une face avant destinée à positionner un emmanchement à une distance prédéterminée du piston de frappe, et d'autre part, une face arrière située en regard d'une paroi arrière de la cavité, un circuit externe d'alimentation hydraulique étant apte, lors de l'arrêt du circuit principal d'alimentation, à introduire un fluide sous-pression entre la face arrière du piston de butée et la paroi arrière de la cavité de façon à maintenir un espace entre celles-ci, et est caractérisé en ce que le piston de butée présente une partie avant, un épaulement central et une partie arrière, ledit épaulement central étant encadré par une chambre avant annulaire et par une chambre arrière annulaire, et le circuit principal d'alimentation est destiné à délivrer un fluide directement dans la chambre arrière et un canal de liaison est destiné à mettre la chambre arrière en libre communication avec la chambre avant.The hammer drill according to the present invention aims to solve the problem mentioned above and for this comprises a body enclosing a reciprocating plunger piston sliding under the effect of a main hydraulic supply circuit, this main circuit being also intended to cause the sliding of a substantially annular abutment piston housed in a cavity of the body and having, on the one hand, a front face for positioning a fitting at a predetermined distance from the striking piston, and secondly, a rear face located opposite a rear wall of the cavity, an external hydraulic supply circuit being adapted, when stopping the main supply circuit, to introduce a fluid under pressure between the rear face of the piston of the abutment and the rear wall of the cavity so as to maintain a space therebetween, and is characterized in that the abutment piston has a front part, an ep a central portion and a rear portion, said central shoulder being flanked by an annular front chamber and an annular rear chamber, and the main supply circuit is for delivering a fluid directly into the rear chamber and a connecting channel is for put the back room in free communication with the front room.

Ainsi, le fait d'associer un circuit externe d'alimentation indépendant, capable de délivrer un fluide entre la face arrière du piston de butée et la paroi arrière de la cavité, offre la possibilité à l'opérateur de fermer en toute sécurité le circuit principal car ce fluide permet de constituer un coussin hydraulique qui empêche le frottement du piston de butée sur le corps du marteau perforateur.Thus, the fact of associating an independent external supply circuit, capable of delivering a fluid between the rear face of the stop piston and the rear wall of the cavity, offers the possibility to the operator to safely close the circuit. principal because this fluid makes it possible to constitute a hydraulic cushion which prevents the friction of the stop piston on the body of the hammer perforator.

Avantageusement, le circuit externe d'alimentation débouche dans la paroi arrière de la cavité et une chemise annulaire coulissante est placée autour de la partie arrière du piston de butée et est apte à, d'une part, empêcher l'introduction du fluide délivré par le circuit externe d'alimentation lorsque la pression régnant dans la chambre arrière annulaire est supérieure ou égale à une valeur déterminée (P), et d'autre part, autoriser l'introduction de ce fluide lorsque la pression régnant dans la chambre arrière annulaire est inférieure à la valeur déterminée (P).Advantageously, the external supply circuit opens into the rear wall of the cavity and a sliding annular liner is placed around the rear portion of the stop piston and is able, on the one hand, to prevent the introduction of the fluid delivered by the external supply circuit when the pressure in the annular rear chamber is greater than or equal to a determined value (P), and secondly, allow the introduction of this fluid when the pressure in the annular rear chamber is less than the determined value (P).

De plus, lorsque le circuit principal d'alimentation est activé, la face arrière du piston de butée est mise à la pression d'un drain au moyen d'un premier canal. Avantageusement, la chambre avant est également mise en communication avec le drain au moyen d'un second canal dès lors que l'emmanchement est à une distance du piston de frappe inférieure à la distance prédéterminée.In addition, when the main supply circuit is activated, the rear face of the stop piston is put under the pressure of a drain by means of a first channel. Advantageously, the front chamber is also placed in communication with the drain by means of a second channel when the fitting is at a distance from the striking piston less than the predetermined distance.

Selon un mode réalisation particulier de l'invention, le piston de butée est destiné à coulisser à l'intérieur d'un guide solidaire du corps. Préférentiellement, la chemise possède une partie arrière présentant, d'une part, un épaulement externe présentant une première surface arrière destinée à coopérer avec le circuit externe d'alimentation, et d'autre part, un renfoncement interne présentant une seconde surface arrière décalée. Préférentiellement encore, une chambre sensiblement annulaire reliée au circuit principal est prévue entre l'épaulement externe de la chemise et une extrémité arrière du guide. Enfin, la face avant du piston de butée possède avantageusement un diamètre sensiblement supérieur à celui de la face arrière.According to a particular embodiment of the invention, the stop piston is intended to slide inside a guide integral with the body. Preferably, the liner has a rear portion having, on the one hand, an outer shoulder having a first rear surface intended to cooperate with the external supply circuit, and on the other hand, an internal recess having a second rear surface offset. Preferably, a substantially annular chamber connected to the main circuit is provided between the outer shoulder of the liner and a rear end of the guide. Finally, the front face of the stop piston advantageously has a diameter substantially greater than that of the rear face.

L'invention sera mieux comprise à l'aide de la description détaillée qui est exposée ci-dessous en regard des dessins annexés dans lesquels :

  • La figure 1 est une vue en coupe longitudinale du marteau perforateur selon l'invention muni de barres de forage au contact de la roche.
  • La figure 2 est une vue en coupe longitudinale et à échelle agrandie du marteau perforateur représenté à la figure 1 lorsque le circuit principal d'alimentation hydraulique est activé et que l'emmanchement est à la distance prédéterminée du piston de frappe.
  • La figure 3 est une vue en coupe similaire à la figure 2 lorsque le circuit principal d'alimentation hydraulique est fermé.
  • La figure 4 est une vue en coupe longitudinale d'un marteau perforateur selon un autre mode de réalisation de l'invention lorsque le circuit principal d'alimentation hydraulique est activé et que l'emmanchement est à la distance prédéterminée du piston de frappe.
  • La figure 5 est une vue en coupe longitudinale du marteau perforateur de la figure 4 lorsque le circuit principal d'alimentation hydraulique est fermé.
  • La figure 6 est une vue en coupe longitudinale d'un marteau perforateur similaire à celui représenté à la figure 4, à la seule différence que la face avant du piston de butée possède un diamètre sensiblement supérieur à celui de la face arrière.
The invention will be better understood with the aid of the detailed description which is set out below with reference to the appended drawings in which:
  • The figure 1 is a longitudinal sectional view of the hammer drill according to the invention provided with drill bars in contact with the rock.
  • The figure 2 is a longitudinal sectional view on an enlarged scale of the hammer drill shown in FIG. figure 1 when the main hydraulic supply circuit is activated and the fitting is at the predetermined distance from the striking piston.
  • The figure 3 is a sectional view similar to the figure 2 when the main hydraulic supply circuit is closed.
  • The figure 4 is a longitudinal sectional view of a hammer drill according to another embodiment of the invention when the main hydraulic supply circuit is activated and the fitting is at the predetermined distance from the striking piston.
  • The figure 5 is a longitudinal sectional view of the hammer drill of the figure 4 when the main hydraulic supply circuit is closed.
  • The figure 6 is a longitudinal sectional view of a hammer drill similar to that shown in FIG. figure 4 , with the only difference that the front face of the stop piston has a diameter substantially greater than that of the rear face.

En se référant aux figures 1 à 3, un marteau perforateur 1 selon l'invention présente un corps 2 comprenant une cavité 3 qui se prolonge vers l'arrière en un alésage 31 contenant un piston de frappe 4. Plus précisément, la cavité 3 renferme un piston de butée 5 sensiblement annulaire qui peut coulisser autour du piston de frappe 4, une chemise 6 annulaire, un emmanchement 7 et un moteur rotatif 8. L'emmanchement 7 est relié à des barres de forage 9 qui agissent sur un taillant 10 au contact de la roche 11.Referring to Figures 1 to 3 a hammer drill 1 according to the invention has a body 2 comprising a cavity 3 which extends rearwardly in a bore 31 containing a striking piston 4. More specifically, the cavity 3 encloses a substantially annular abutment piston 5 which is slidable around the striking piston 4, an annular sleeve 6, a fitting 7 and a rotary motor 8. The fitting 7 is connected to drill bars 9 which act on a cutting edge 10 in contact with the rock 11.

Le piston de butée 5 présente une partie avant, un épaulement central 12 et une partie arrière, l'épaulement central comportant une surface annulaire avant 25 et une surface annulaire arrière 26. Au niveau de sa partie avant et de sa partie arrière, le piston de butée est muni respectivement d'une face avant 13 et d'une face arrière 14. Plus particulièrement, la face avant 13 est au contact de l'emmanchement 7 et la face arrière 14 est en regard d'une paroi arrière 15 de la cavité 3. La chemise 6 est placée autour de la partie arrière du piston de butée 5 et peut coulisser avec étanchéité le long de celle-ci. Par ailleurs, la partie avant du piston de butée 5, la surface avant 25 de l'épaulement central 12 et le corps 2 définissent une chambre avant 16 annulaire. De même, la partie arrière du piston de butée 5, la surface arrière 26 de l'épaulement central 12, le corps 2 et la chemise 6 définissent une chambre arrière 17 annulaire.The stop piston 5 has a front portion, a central shoulder 12 and a rear portion, the central shoulder having a front annular surface 25 and a rear annular surface 26. At its front portion and rear portion, the piston abutment is provided respectively with a front face 13 and a rear face 14. More particularly, the front face 13 is in contact with the fitting 7 and the rear face 14 is opposite a rear wall 15 of the cavity 3. The liner 6 is placed around the rear portion of the stop piston 5 and is slidably sealable therealong. Furthermore, the front portion of the stop piston 5, the front surface 25 of the central shoulder 12 and the body 2 define a front chamber 16 annular. Similarly, the rear portion of the stop piston 5, the rear surface 26 of the central shoulder 12, the body 2 and the liner 6 define an annular rear chamber 17.

Un canal de liaison 18 est prévu de façon à pouvoir, en fonctionnement, mettre la chambre avant 16 et la chambre arrière 17 à la même pression. Un premier canal 30 traversant longitudinalement le piston de butée 5 sur toute sa partie arrière permet de mettre la face arrière 14 du piston de butée 5 à la pression d'un drain 19 par l'intermédiaire d'une gorge 20. Enfin, un second canal 21 ménagé dans la partie avant du piston de butée permet la mise en communication de la chambre avant 16 avec la gorge 20 et le drain 19.A connecting channel 18 is provided so that, in operation, put the front chamber 16 and the rear chamber 17 at the same pressure. A first channel 30 longitudinally traversing the stop piston 5 over its entire rear portion makes it possible to put the rear face 14 of the stop piston 5 at the pressure of a drain 19 via a groove 20. Finally, a second channel 21 formed in the front portion of the stop piston allows the communication of the front chamber 16 with the groove 20 and the drain 19.

Un circuit principal22 d'alimentation hydraulique du marteau perforateur 1 est relié à l'alésage 31 contenant le piston de frappe 4, mais également à la chambre arrière 17. De plus, un circuit externe 23 d'alimentation hydraulique indépendant du circuit principal 22 présente une extrémité débouchant dans l'extrémité arrière 15 de la cavité 3 au niveau de la chemise 6.A main hydraulic supply circuit 22 for the hammer drill 1 is connected to the bore 31 containing the striking piston 4, but also to the rear chamber 17. In addition, an external hydraulic supply circuit 23 independent of the main circuit 22 has an end opening into the rear end 15 of the cavity 3 at the level of the jacket 6.

En fonctionnement, le moteur hydraulique de la glissière (non représenté) contenant le marteau perforateur 1 applique un effort d'appui sur le corps 2, comme illustré par la flèche 24. Cet effort d'appui est transmis au piston de butée 5 au moyen du circuit principal 22, qui génère un fluide sous-pression dans la chambre arrière 17 de façon à exercer des contraintes sur la surface arrière 26 de l'épaulement 12 et sur la chemise 6. Le piston de butée 5 est alors amené à coulisser vers l'avant et transmet l'effort d'appui par sa face avant 13 à l'emmanchement 7, et donc aux barres de forage 9 et au taillant 10. En revanche, la chemise 6 est poussée vers l'arrière et obture le circuit externe 15. Grâce au canal de liaison 18, le piston de butée 5 stoppe sa course car un équilibre des pressions est établi entre la chambre avant 16 et la chambre arrière 17 de sorte que l'emmanchement 7 est alors placé à une distance adéquate prédéterminée du piston de frappe 4. II est à noter que l'emmanchement 7 est maintenu dans cette position car, s'il tendait à reculer, le second canal 21 serait apte à mettre la chambre avant 16 en communication avec le drain 19, ce qui aurait pour conséquence de déplacer le piston de butée 5 vers l'avant. Enfin, le piston de frappe 4 peut venir percuter l'emmanchement 7 en coulissant dans son logement 31 sous l'effet de la pression du fluide du circuit principal 22. De même, le moteur rotatif peut être actionné et agir sur l'emmanchement 7.In operation, the hydraulic motor of the slide (not shown) containing the hammer drill 1 applies a bearing force on the body 2, as illustrated by the arrow 24. This bearing force is transmitted to the stop piston 5 by means of of the main circuit 22, which generates a fluid underpressure in the rear chamber 17 so as to exert stresses on the rear surface 26 of the shoulder 12 and on the liner 6. The stop piston 5 is then caused to slide towards the front and transmits the support force by its front face 13 to the fitting 7, and thus to the drill bars 9 and the cutter 10. On the other hand, the sleeve 6 is pushed back and closes the circuit external 15. Through the connecting channel 18, the stop piston 5 stops its stroke because a pressure balance is established between the front chamber 16 and the rear chamber 17 so that the fitting 7 is then placed at a predetermined adequate distance of the striking piston 4. It should be noted that the fitting 7 is held in this position because, if it tended to retreat, the second channel 21 would be able to put the chamber before 16 in communication with the drain 19, which would have the effect of displacing the thrust piston 5 forward. Finally, the striking piston 4 can strike the fitting 7 by sliding in its housing 31 under the effect of the pressure of the fluid of the main circuit 22. Similarly, the rotary motor can be actuated and act on the fitting 7 .

En revanche, lorsque le marteau perforateur 1 n'est plus alimenté par le circuit principal 22, la pression régnant dans la chambre arrière 17 chute, ce qui a pour effet de provoquer le recul du piston de butée 5 vers l'extrémité arrière 15 de la cavité 3 du corps 2. La face arrière 14 du piston de butée n'est alors rapidement plus mise à la pression du drain 19 car le canal de liaison 30 est progressivement obturé. Lorsque la pression dans la chambre arrière 17 devient inférieure à une valeur P déterminée, le fluide sous-pression délivré par le circuit externe 23 exerce alors des contraintes suffisantes sur la chemise 6 pour obliger celui-ci à coulisser vers l'avant. Par conséquent, le fluide s'intercale entre la face arrière 14 du piston de butée 5 et la paroi arrière 15 de la cavité 3 de façon à empêcher tout contact entre elles. Il est à noter que le moteur rotatif 8 peut continuer à fonctionner même lorsque le circuit principal 22 est fermé.On the other hand, when the hammer drill 1 is no longer fed by the main circuit 22, the pressure in the rear chamber 17 drops, which has the effect of causing the abutment piston 5 to fall back towards the rear end 15. the cavity 3 of the body 2. The rear face 14 of the stop piston is then no longer put under the pressure of the drain 19 because the connecting channel 30 is gradually closed. When the pressure in the rear chamber 17 becomes lower than a determined value P, the underpressure fluid delivered by the external circuit 23 then exerts sufficient stresses on the liner 6 to force it to slide forward. Consequently, the fluid is inserted between the rear face 14 of the stop piston 5 and the rear wall 15 of the cavity 3 so as to prevent any contact between them. He is at note that the rotary motor 8 can continue to operate even when the main circuit 22 is closed.

Aux figures 4 et 5 est décrit marteau perforateur 101 selon le mode particulier de l'invention. Nous ne décrirons ci-après que les différences existant entre ce marteau perforateur 101 et celui représenté aux figures 1 à 3. Ce marteau perforateur 101 présente un corps 102 et diffère principalement de celui représenté aux figures 1 à 3 par le fait que, d'une part, le piston de butée 5 est désormais amené à coulisser à l'intérieur d'un guide 103 solidaire du corps 102, et d'autre part, la chemise 6 est remplacée par une chemise 106 dotée d'un épaulement externe 107 et d'un renfoncement interne. Plus précisément, l'épaulement externe 107 présente une première surface arrière 108 destinée à coopérer avec le circuit externe 23 et le renfoncement interne présente une seconde surface arrière 109 décalée par rapport à la première surface arrière 108. En fonctionnement, cette seconde surface arrière 109 est alors mise à la pression du drain 19. De plus, une chambre 110 sensiblement annulaire est prévue entre l'épaulement externe 107 et une extrémité arrière 111 du guide 103, et cette chambre annulaire 110 est reliée au circuit principal 22 d'alimentation hydraulique.To the Figures 4 and 5 is described hammer drill 101 according to the particular embodiment of the invention. We will only describe below the differences existing between this hammer drill 101 and that shown in FIGS. Figures 1 to 3 . This hammer drill 101 has a body 102 and differs mainly from that shown in FIGS. Figures 1 to 3 in that, on the one hand, the stop piston 5 is now slid inside a guide 103 integral with the body 102, and on the other hand, the sleeve 6 is replaced by a jacket 106 provided with an outer shoulder 107 and an internal recess. More specifically, the outer shoulder 107 has a first rear surface 108 intended to cooperate with the external circuit 23 and the inner recess has a second rear surface 109 offset from the first rear surface 108. In operation, this second rear surface 109 is then put under the pressure of the drain 19. In addition, a substantially annular chamber 110 is provided between the outer shoulder 107 and a rear end 111 of the guide 103, and this annular chamber 110 is connected to the main hydraulic supply circuit 22 .

Le fonctionnement du marteau perforateur 101 est similaire à celui décrit précédemment pour le marteau perforateur 1. Il faut seulement remarquer que lorsque le marteau perforateur 101 est alimenté par le circuit principal 22, le fluide sous-pression est délivré dans la chambre arrière 17 mais également dans la chambre 110. L'avantage de ce mode de réalisation particulier de l'invention réside dans le fait que la surface avant 25 et la surface arrière 26 de l'épaulement 12 du piston de butée 5, ainsi que les première et seconde surfaces arrières 107, 108 de la chemise 106 peuvent être facilement choisies de façon à ce que la pression minimum générée par le circuit externe 23 nécessaire au déplacement de la chemise 106 soit très supérieure à la pression générée par le circuit principal 22 dans la chambre arrière 17 et la chambre 110.The operation of the hammer drill 101 is similar to that described above for the hammer drill 1. It should be noted only that when the hammer drill 101 is fed by the main circuit 22, the underpressure fluid is delivered in the rear chamber 17 but also in the chamber 110. The advantage of this particular embodiment of the invention lies in the fact that the front surface 25 and the rear surface 26 of the shoulder 12 of the stop piston 5, as well as the first and second surfaces The backs 107, 108 of the liner 106 can be easily selected so that the minimum pressure generated by the external circuit 23 necessary for the displacement of the liner 106 is much greater than the pressure generated by the main circuit 22 in the rear chamber 17. and the room 110.

La figure 6 décrit un marteau perforateur 201 qui diffère du marteau perforateur 101 représenté aux figures 4 et 5 uniquement par le fait que la face avant 13 du piston de butée 5 possède un diamètre sensiblement supérieur à celui de la face arrière 14. En fonctionnement, ceci a pour conséquence de pousser le piston vers l'avant, même au-delà de sa position d'équilibre, car lorsque la chambre avant 16 et la chambre arrière 17 sont à une pression identique, la différence de diamètre entre la face avant 13 et la face arrière 14 induit la création d'une section annulaire supplémentaire de poussée vers l'avant. Ceci a alors pour avantage de permettre à la face avant 13 du piston de butée 5 de rester plus longtemps en contact avec l'emmanchement 7 malgré les mouvements vibratoires importants liés à la percussion du piston de frappe 4 sur l'emmanchement 7.The figure 6 describes a hammer drill 201 which differs from the hammer drill 101 shown in FIGS. Figures 4 and 5 only by the fact that the front face 13 of the stop piston 5 has a diameter substantially greater than that of the rear face 14. In operation, this has the effect of pushing the piston forward, even beyond its position equilibrium, because when the front chamber 16 and the rear chamber 17 are at an identical pressure, the difference in diameter between the front face 13 and the rear face 14 induces the creation of an additional annular section thrust forward . This then has the advantage of allowing the front face 13 of the stop piston 5 to remain longer in contact with the fitting 7 despite the important vibratory movements related to the percussion of the striking piston 4 on the fitting 7.

Bien que l'invention ait été décrite en liaison avec des exemples particuliers de réalisation, il est bien évident qu'elle n'y est nullement limitée et qu'elle comprend tous les équivalents techniques des moyens décrits ainsi que leurs combinaisons si celles-ci entrent dans le cadre de l'invention, défini par les revendications.Although the invention has been described in connection with particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention, defined by the claims.

Claims (8)

  1. Rotary percussive hydraulic hammer drill (1, 101, 201) comprising a body (2, 102) enclosing an alternative striking piston (4) sliding under the effect of a main hydraulic supply circuit (22), this main circuit being also intended to bring about the sliding of a substantially annular stop piston (5) housed in a cavity (3) in the body and possessing, on the one hand, a front face (13) intended to position a sleeve-joint (7) at a predetermined distance from the striking piston and, on the other hand, a rear face (14) opposite a rear wall (15) of said cavity, an external hydraulic supply circuit (23) being capable, when the main supply circuit is stopped, of introducing an uplift fluid between the rear face of the stop piston and the rear wall of the cavity so as to maintain a space between them, characterised in that the stop piston (5) has a front part, a central shoulder (12) and a rear part, the said central shoulder being surrounded by an annular front chamber (16) and by an annular rear chamber (17), and in that the main circuit (22) is intended to deliver a fluid directly into the rear chamber (17), and in that a linking conduit (18) is intended to bring the rear chamber into free communication with the front chamber (16).
  2. Hammer drill (1, 101, 201) according to Claim 1, characterised in that the external circuit (23) opens into the rear end (15) of the cavity (3), and in that a sliding annular liner (6, 106) is located around the rear part of the stop piston (5) and is capable of, on the one hand, preventing the introduction of the fluid delivered by the external circuit when the pressure prevailing in the rear chamber (17) is greater than, or equal to, a given value (P) and, on the other hand, allowing the introduction of this fluid when the pressure prevailing in the rear chamber is lower than said given value (P).
  3. Hammer drill (1, 101, 201) according to one of Claims 1 and 2, characterised in that, when the main circuit (22) is activated, the rear face (14) of the stop piston (5) is brought to the pressure of a drain (19) by means of a first conduit (30).
  4. Hammer drill (1, 101, 201) according to Claim 3, characterised in that the front chamber (16) is brought into communication with the drain (19) by means of a second conduit (21) as soon as the sleeve-joint (7) is at a distance from the striking piston (4) which is less than the predetermined distance.
  5. Hammer drill (101, 201) according to any of Claims 2 to 4, characterised in that the stop piston (5) is intended to slide inside a guide (103) which is integral with the body (102).
  6. Hammer drill (101, 201) according to Claim 5, characterised in that the liner (106) possesses a rear part having, on the one hand, an external shoulder (107) having a first rear surface (108) intended to cooperate with the external circuit (23) and, on the other hand, an internal recess having a second, offset rear surface (109).
  7. Hammer drill (101, 201) according to Claim 6 characterised in that a substantially annular chamber (110) connected to the main circuit (22) is provided between the external shoulder (107) of the liner (106) and a rear end (111) of the guide (103).
  8. Hammer drill (201) according to any of Claims 5 to 7, characterised in that the front face (13) of the stop piston (5) possesses a diameter which is substantially greater than that of the rear face (14).
EP03725300A 2002-03-19 2003-03-18 Hydraulic rotary-percussive hammer drill Expired - Lifetime EP1492648B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0203402 2002-03-19
FR0203402A FR2837523B1 (en) 2002-03-19 2002-03-19 ROTO-PERCUTANT HYDRAULIC PERFORATOR HAMMER
PCT/FR2003/000859 WO2003078107A1 (en) 2002-03-19 2003-03-18 Hydraulic rotary-percussive hammer drill

Publications (3)

Publication Number Publication Date
EP1492648A1 EP1492648A1 (en) 2005-01-05
EP1492648B1 EP1492648B1 (en) 2006-10-25
EP1492648B2 true EP1492648B2 (en) 2009-10-21

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EP03725300A Expired - Lifetime EP1492648B2 (en) 2002-03-19 2003-03-18 Hydraulic rotary-percussive hammer drill

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US (1) US7234548B2 (en)
EP (1) EP1492648B2 (en)
JP (1) JP2005527388A (en)
KR (1) KR20040091661A (en)
CN (1) CN100333879C (en)
AT (1) ATE343458T1 (en)
AU (1) AU2003227845B2 (en)
BR (1) BR0308436A (en)
CA (1) CA2479055C (en)
DE (1) DE60309303T2 (en)
DK (1) DK1492648T3 (en)
ES (1) ES2274231T3 (en)
FR (1) FR2837523B1 (en)
IL (2) IL163897A0 (en)
NO (1) NO20044415L (en)
PT (1) PT1492648E (en)
WO (1) WO2003078107A1 (en)
ZA (1) ZA200406502B (en)

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FI121004B (en) * 2003-01-03 2010-06-15 Sandvik Mining & Constr Oy Rock drill and axial bearing for a striking rock drill
FR2916377B1 (en) * 2007-05-25 2009-07-24 Montabert Soc Par Actions Simp METHOD OF PROTECTING AGAINST FLOW SUPPLY OF A DEVICE WITH MUTE PERCUSSIONS BY AN INCOMPRESSIBLE FLUID UNDER PRESSURE AND APPARATUS FOR CARRYING OUT SAID METHOD
FR2929322B1 (en) * 2008-03-25 2010-03-12 Montabert Roger ROTO-PERCUTANT HYDRAULIC PUNCH HAMMER
US8353369B2 (en) * 2008-08-06 2013-01-15 Atlas Copco Secoroc, LLC Percussion assisted rotary earth bit and method of operating the same
FI121221B (en) 2008-11-20 2010-08-31 Sandvik Mining & Constr Oy Rock drill and axial bearing module
FI121220B (en) * 2008-11-20 2010-08-31 Sandvik Mining & Constr Oy Rock drill and axial bearing module
FI124781B (en) * 2009-03-26 2015-01-30 Sandvik Mining & Constr Oy Type of device
SE534815C2 (en) 2010-05-03 2012-01-10 Atlas Copco Rock Drills Ab Rock drill with damper piston
FR2964691B1 (en) * 2010-09-13 2012-09-28 Montabert Roger HYDRAULIC ROTOPERCUTANT APPARATUS FOR PERFORATING MINE HOLES
KR101504402B1 (en) * 2012-12-10 2015-03-24 주식회사 에버다임 Hydraulic rotary percussive drilling tool
KR101410134B1 (en) * 2012-12-26 2014-06-25 주식회사 에버다임 Damping device of hydraulic rotary percussive drilling tool
KR101565140B1 (en) 2013-06-24 2015-11-02 주식회사 에버다임 Hydraulic rotary percussive drilling tool
WO2014208922A1 (en) * 2013-06-24 2014-12-31 주식회사 에버다임 Hydraulic rotating striking device
KR102026543B1 (en) * 2014-08-19 2019-09-27 비쉐이-실리코닉스 Electronic circuit
FR3077752B1 (en) * 2018-02-14 2020-01-31 Montabert ROTO-PERCUTANT HYDRAULIC PERFORATOR PROVIDED WITH A CONTROL CHAMBER PERMANENTLY CONNECTED TO A LOW PRESSURE ACCUMULATOR

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CN100333879C (en) 2007-08-29
ZA200406502B (en) 2006-06-28
AU2003227845A1 (en) 2003-09-29
WO2003078107A1 (en) 2003-09-25
NO20044415L (en) 2004-10-18
EP1492648B1 (en) 2006-10-25
EP1492648A1 (en) 2005-01-05
DE60309303T2 (en) 2007-02-01
AU2003227845B2 (en) 2008-04-03
ES2274231T3 (en) 2007-05-16
PT1492648E (en) 2007-02-28
BR0308436A (en) 2005-01-18
CA2479055A1 (en) 2003-09-25
US7234548B2 (en) 2007-06-26
IL163897A0 (en) 2005-12-18
IL163897A (en) 2008-11-26
KR20040091661A (en) 2004-10-28
CA2479055C (en) 2011-05-10
JP2005527388A (en) 2005-09-15
DE60309303D1 (en) 2006-12-07
CN1638924A (en) 2005-07-13
ATE343458T1 (en) 2006-11-15
FR2837523B1 (en) 2004-05-14
DK1492648T3 (en) 2007-02-26
FR2837523A1 (en) 2003-09-26
US20050016774A1 (en) 2005-01-27

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