EP0214064A1 - Method of controlling the movement of the impacting piston of a non-compressible fluid-actuated percussion device, and device therefor - Google Patents

Method of controlling the movement of the impacting piston of a non-compressible fluid-actuated percussion device, and device therefor Download PDF

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Publication number
EP0214064A1
EP0214064A1 EP86420181A EP86420181A EP0214064A1 EP 0214064 A1 EP0214064 A1 EP 0214064A1 EP 86420181 A EP86420181 A EP 86420181A EP 86420181 A EP86420181 A EP 86420181A EP 0214064 A1 EP0214064 A1 EP 0214064A1
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EP
European Patent Office
Prior art keywords
piston
channel
pressure
drawer
fluid
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86420181A
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German (de)
French (fr)
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EP0214064B1 (en
Inventor
Aimé Vénot
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Montabert SAS
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Montabert SAS
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Priority claimed from FR8511346A external-priority patent/FR2584968B1/en
Application filed by Montabert SAS filed Critical Montabert SAS
Priority to AT86420181T priority Critical patent/ATE55080T1/en
Publication of EP0214064A1 publication Critical patent/EP0214064A1/en
Application granted granted Critical
Publication of EP0214064B1 publication Critical patent/EP0214064B1/en
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    • 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
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • the subject of the present invention is a method for controlling the movement of the striking piston of a percussion device driven by an incompressible fluid under pressure, and an apparatus for implementing this method.
  • Percussion instruments driven by an incompressible fluid under pressure are supplied in such a way that the result of the hydraulic forces applied successively on the striking piston alternately displaces the latter in one direction then in the other.
  • this initial compression wave arrives in a soft ground, it will on the contrary be strongly absorbed by this one.
  • the piston will be assigned an initial speed in the same direction as the tool and the value of which depends on the same parameters as above.
  • Some devices are equipped with a regulator allowing the supply pressure and consequently the impact speed of the piston to be adjusted according to the hardness of the ground and the nature of the work to be carried out.
  • Other devices are equipped with a distributor actuated hydraulically in both directions and ensuring the alternation of the hydraulic forces applied to the piston.
  • these control devices are definitively adjusted according to the type of work envisaged for the device, without it being possible to obtain an automatic adjustment according to the working conditions.
  • French patent 2,375,008 relates to a device for adjusting the striking frequency by pneumatic or electro-hydraulic remote control.
  • This remote control acts on a drawer selecting a channel from a series of channels opening into a series of annular grooves formed in the working cylinder, the selected channel being able to be connected to the fluid supply network.
  • This device requiring manual intervention to adjust the striking frequency, cannot, in any case, react and adapt automatically to the hardness of the ground.
  • the control method which it relates to intended for a percussion device driven by an incompressible fluid under pressure, supplied in such a way that the result of the hydraulic forces is applied successively in one direction and in the other, and equipped with hydraulically controllable regulation devices capable of varying percussion parameters, such as the impact speed and / or the impact frequency of the piston, is characterized in that it consists in measuring, during each impact of the piston on the tool, the residence time of the piston near its theoretical striking position, then to act as a function of this time on the devices for regulating the impact parameters.
  • An apparatus for implementing this method comprises a channel opening into the interior of the cylinder containing the striking piston and communicating with a primary circuit connected to the devices for controlling the percussion parameters, while a groove formed in the piston allows, at each impact and during the residence time of the piston near its theoretical striking position, to establish a momentary circulation of fluid between the primary circuit and a secondary circuit.
  • the hydraulic information provided to the regulation devices allows them to adapt the operating parameters to the nature of the soil encountered by the tool.
  • the device represented in FIG. 1 relates to a percussion device of the type described in French patent 81 14043 in the name of the Applicant, and comprising a piston (1) sliding in a body (2) comprising a cavity in the form of cylinder, in which a distributor (3) is concentrically mounted.
  • This device is equipped in a known manner with a regulator making it possible to adjust the supply pressure and consequently the impact speed of the piston as a function of the hardness of the ground and the nature of the work to be performed.
  • This regulator comprises a drawer (4) in balance under the force of a spring (5) and under the pressure of the supply fluid supplied by a channel (6) and a nozzle (7), and acting on the surface (8 ) at the end of the drawer.
  • a chamber (11) generally connected to the low pressure return circuit (50) of the device is located on the same side of the drawer as the surface (8).
  • the drawer (4) defines with the walls of the cavity in which it is mounted, a throttled passage forming a nozzle (9) ensuring the passage of the fluid discharged through the channel (10) by the piston, during the return stroke thereof.
  • the nozzle (9) creates a back pressure in the channel (10), during the return stroke, such that the supply pressure acting on the section (8) rises to a value sufficient to compensate the action of the spring (5).
  • the supply pressure is adjusted by adjusting the setting of the spring (5).
  • a channel (12) is formed in the body (2) which is equipped with a nozzle (14), and which opens into the bearing surface (13) of the cylinder used for moving the piston.
  • This channel (12) is placed in communication with the fluid at its supply pressure, by means of a groove (15) which comprises the piston (1).
  • Figure 2 corresponds to a variant of the device of Figure 1 in which the nozzle (14) mounted on the channel (12) is replaced by a nozzle (14 ') disposed on a channel (56) for supplying the fluid under pressure.
  • the primary circuit to which the channel (12) is connected comprises a slide (17) slidably mounted inside a bore (20) delimiting on one side a chamber (51), hereinafter called the buffer chamber, communicating with the channel (12) and a chamber (52), containing a spring (18), connected to the low pressure return circuit (50) by a channel (21).
  • the channel (12) and the buffer chamber (51) are in communication with the control chamber (11) of the pressurized fluid supply regulator.
  • the pressure inside the pilot chamber (11) being itself low, the slide (4) tends to close the nozzle (9) which increases the back pressure in the channel (10) and consequently increases the supply pressure and the impact speed of the piston. If the ground encountered by the tool becomes softer, the quantity of fluid injected per cycle in the channel (12) increases, which causes an increase. pressure on the one hand in the buffer chamber (51) and on the other hand in the pilot chamber (11). This increase in pressure modifies the balance of the slide (4) in a direction of opening of the nozzle (9) which has the effect of reducing the existing back pressure in the channel (10) and therefore of reducing the pressure of fluid supply to the device and the impact speed of the piston.
  • the large dimension of the drawer (17) allows it to play the role of accumulator and to obtain a stabilized pressure in the buffer chamber (51), and therefore in the pilot chamber (11).
  • the drawer (17) will be in equilibrium for a pressure in the chamber (51), such that the continuous flow that this pressure allows to pass through the chamber (52) by a nozzle (19) is equal to the pulsed flow injected by the nozzle (14) in the channel (12).
  • FIG. 3 represents an apparatus in which the same members are designated by the same references as above.
  • This device operates according to a known principle, where a distributor (30) actuated hydraulically in both directions ensures the alternation of the hydraulic forces applied to the striking piston.
  • the distributor (30) is controlled by an annular control section (33) which, when under pressure, displaces the distributor by putting the channel (31) opening out at communication. above the piston head with the high pressure fluid supply circuit.
  • This chamber (33) is supplied by a channel (34) opening into an annular groove (40) of a drawer (35) mounted in a bore (20).
  • This groove (40) can be placed in communication, depending on the position of the drawer (35) with one or more of a series of channels (36 - 39) opening into the cylinder in which the piston is slidably mounted.
  • the function of the drawer (35) is to select the active control channel (36 - 39) which, supplied from the annular chamber (32) delimited by a groove (55) of the piston, will put under pressure the piloting section (33) and will trigger the start of the piston stroke.
  • the supply of pressurized fluid to the upper chamber of the piston will intervene more or less early, making it possible to vary the stroke of the piston and consequently the frequency of hit.
  • the control of the position of the drawer (35) is obtained as in the previous embodiments via the channel (12) which supplies pressurized fluid to the buffer chamber (51).
  • Figure 4 shows a variant of this device, in which it is equipped with both a regulator and a distributor.
  • the pressure created in the chamber (51) is used on the one hand to move the drawer (35) to select the strike stroke and to control the drawer (4) of the supply pressure regulator, which modifies the back pressure of return of the device, and consequently the supply pressure itself and the typing speed.
  • FIG. 5 represents an alternative embodiment of an apparatus equipped with a regulator, in which the channel (12) equipped with a nozzle (14) is capable of being placed in communication with the low pressure network (50) by through a channel (61) connected to this network and a groove (63) formed in the piston, when the groove (63) simultaneously discovers the orifice (80) of the channel (12) and the orifice (81) of the channel (61), when the piston is in its theoretical striking position.
  • the channel (12) communicates as before with the buffer chamber (51) which, in this case, contains the spring (18) acting on the slide (17) while the rear chamber (52) located on the other side of this drawer is continuously supplied with pressurized fluid by a pressure regulator or nozzle (71) itself in relation to the high pressure network of the device by a channel (58) or (59).
  • a nozzle (19) connects the chambers (51) and (52), and the chamber (51) is in relation to the control chamber of the slide valve (65) of the regulator via a channel (76).
  • the pressurized fluid from the chamber (52) passes through the nozzle (19) into the chamber (51) and must be evacuated through the channel. (12) and the groove (63) to the low pressure channel (61) and the low pressure network (50) via the nozzle (14) mounted on the channel (12) or a nozzle (14 ') mounted on the channel (61).
  • the slide (17) will be in equilibrium for a pressure in the chamber (51), such that the pulsed flow that this pressure allows to pass during each cycle in the nozzle (14) or (14 ') is equal to the flow supplied by the nozzle (71).
  • the slide valve (65) of the regulator delimits with its bore a chamber (8) connected to the supply pressure, a chamber (11) connected to the return circuit by the channel (64) and a pilot chamber (60 ) antagonist, connected to the buffer chamber (51) by the channel (76).
  • a pilot chamber (60 ) antagonist connected to the buffer chamber (51) by the channel (76).
  • This closure increases the back pressure in the channel (10) and consequently increases the supply pressure and the impact speed of the piston.
  • FIG. 6 represents an alternative embodiment of the apparatus of FIG. 5 in which the channel (12) and the buffer chamber (51) are constantly supplied with pressurized fluid by a nozzle itself supplied with fluid by a channel ( 58) or (59).
  • the chamber (52) delimited in part by the slide (66) is connected to the return circuit of the device by a channel (21) while a channel (22) also connected to the low pressure network opens into the bore in which is mounted the drawer (66), and is capable of putting the buffer chamber (51) in relation to the low pressure network when the pressure in this chamber exceeds a predetermined value.
  • the pressure which builds up in the chamber (51) is such that the quantity of fluid per cycle discharged by the nozzle (14) towards the low pressure network by the groove (63) of the piston is equal to the quantity of fluid per cycle entering the chamber (51) through the flow regulator or nozzle (78).
  • the quantity of fluid discharged by the nozzle (14) tends to increase, taking into account the longer residence time of the piston in the impact zone.
  • the pressure prevailing in the chamber (51) tends to decrease, as well as that prevailing in the chamber (60) which modifies the equilibrium position of the drawer (65) in a direction of opening of the nozzle ( 9).
  • This opening of the nozzle (9) causes a decrease in the back pressure and consequently a decrease in the supply pressure of the device and the impact speed of the piston.
  • FIG. 7 represents an alternative embodiment of the apparatus of FIG. 6, in which the buffer chamber (51) is momentarily supplied by a nozzle (78) itself supplied at the supply pressure by a channel ( 58) or (59).
  • the nozzle (78) is mounted on a channel (79) opening into the cylinder in which the piston (1) moves on the side opposite the channel (61) relative to the channel (12).
  • the height of the groove (63) is greater than the distance between the channel (12) and the channel (79) on the one hand, and the channel (12) and the channel (61) on the other part, but less than the distance between the channel (79) and the channel (61).
  • the piston In practice when the piston is in the position shown in FIG. 7, it places the channels (79) and (12) in communication and supplies the chamber (51) with pressurized fluid. When the movement of the piston continues, this communication is cut off and the groove (63) puts in communication, when the piston arrives at its theoretical striking position, the channel (12) with the low pressure network, via the channel (61).
  • the pressure in the chamber (51) is such that it establishes the equality of the quantity of fluid entering this chamber when the groove (63) puts the channel (12) and the channel (79) into communication with the quantity of fluid leaving this chamber when the groove (63) connects the channel (12) and the channel (61). As a result, the pressure of the chamber (51) depends on the hardness of the ground.
  • the primary circuit to which the channel (12) is connected comprises a buffer chamber or pilot chamber (51), formed in a bore (82) extended by a bore (20) of smaller cross section.
  • a drawer (87) Inside the bores (82) and (20) is slidably mounted a drawer (87), comprising two parts of different sections, which partly delimits the chamber (51), the end of the cavity opposite the chamber ( 51) being constituted by a chamber (52) connected to the low pressure return circuit of the device.
  • a peripheral groove (40) capable of being placed in communication with one or more of a series of channels (36-39) opening into the cylinder in which the piston (13) is slidably mounted, and an annular chamber (84) supplied by a channel (83) with pressurized fluid.
  • the annular chamber (84) being formed in the bore (82) of large section, the force exerted by the fluid under pressure on the drawer (87) tends to move the latter in a direction of reduction of the volume of the chamber ( 51).
  • the chamber (51) also communicates via a channel (86) with the low pressure return circuit, with mounting on the channel (86) of a member (85) allowing the regulated flow of the liquid from the chamber (51) to the low pressure circuit (50).
  • This regulating member (85) is constituted by a positive displacement pump actuated in synchronism with the striking piston (1).
  • the peripheral groove (40), formed in the drawer (87), also communicates, as indicated in the main patent, via a channel (34) with a pilot chamber (33) of the control distributor (30) of the device.
  • the drawer (87) has a stable position when the quantity of fluid extracted, per cycle, from the chamber (51) by the member (85), is equal to the quantity of fluid injected, per cycle, into the chamber (51 ).
  • the time of stay of the piston in contact with the tool increases, as does the time of supply of pressurized fluid to the chamber (51) through the channel (12).
  • the quantity of fluid supplying the chamber (51) being greater than that evacuated by the member (85), the drawer (87) moves in a direction of increase in the volume of the chamber (51), the displacement of this drawer resulting in an action on the distributor (30) which will reduce the striking stroke of the piston to find a new equilibrium position of the drawer (87), such that the impact speed is appropriate to the hardness of the ground.
  • the balance of the drawer is obtained without spring under the action, on the one hand, of the fluid pressure inside the buffer chamber (51) and, on the other hand, of the pressure supply inside the annular chamber (84).
  • the use of a positive displacement pump as a member (85) is advantageous in that it makes it possible to extract, per cycle, always the same quantity of fluid, and this regardless of the striking frequency of the 'apparatus.
  • FIG. 9 represents a variant of the apparatus of FIG. 8 in which the same references designate the same members as above.
  • the secondary circuit (61) in communication with the low pressure return circuit (50) of the device, is momentarily connected to the primary circuit comprising the chamber (51), via of the groove (63) of the piston (1), when the latter is in contact with the tool.
  • the buffer chamber (51) is supplied with fluid via the channel (86a) on which is mounted a flow control member (85a) consisting of a positive displacement pump actuated in synchronism with the impact piston.
  • the drawer (87) occupies a stable position when the quantity of fluid extracted per cycle from the chamber (51) through the channel (12), the nozzle (14), the chamber (63) and the channel (61 ), is equal to the quantity of fluid injected into the chamber (51) through the channel (86a) and the member (85a).
  • the quantity of fluid extracted from the chamber (51) becomes, taking into account the increase in the residence time of the piston (1) in the lower position, greater than the quantity of fluid injected by the organ (85a). This results in a displacement of the drawer (87) in a direction of reduction of the volume of the chamber (51) under the action of the supply pressure in the chamber (84), which results in an action on the dispenser. device control which decreases the stroke of the piston.
  • the invention brings a great improvement to the existing technique by providing a method and an apparatus making it possible to adapt, automatically and instantaneously, certain percussion parameters such as impact speed and frequency of the piston to the hardness of the ground in which the device works.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Ce procédé est destiné à la commande du mouvement du piston de frappe d'un appareil à percussions mû par un fluide incompressible sous pression et équipé de dispositifs de régulation pilotables hydrauliquement susceptibles de faire varier des paramètres de percussion, tels que vitesse d'impact et/ou fréquence de frappe du piston. Ce procédé consiste à mesurer, lors de chaque impact du piston (1) sur l'outil à l'aide d'un dispositif (15, 80), le temps de séjour du piston à proximité de sa position théorique de frappe, puis à agir en fonction de ce temps sur le dispositif de régulation (4) d'un paramètre de percussion.This method is intended for controlling the movement of the impact piston of a percussion device driven by an incompressible fluid under pressure and equipped with hydraulically controllable regulation devices capable of varying percussion parameters, such as impact speed and / or piston strike frequency. This method consists in measuring, at each impact of the piston (1) on the tool using a device (15, 80), the residence time of the piston near its theoretical striking position, then at act as a function of this time on the regulation device (4) of a percussion parameter.

Description

La présente invention a pour objet un procédé de commande du mouvement du piston de frappe d'un appareil à percussions mû par un fluide incompressible sous pression, et un appareil pour la mise en oeuvre de ce procédé.The subject of the present invention is a method for controlling the movement of the striking piston of a percussion device driven by an incompressible fluid under pressure, and an apparatus for implementing this method.

Les appareils à percussions mûs par un fluide incompressible sous pression sont alimentés de telle façon que la résultante des forces hydrauliques s'appliquant successivement sur le piston de frappe déplace alternativement celui-ci dans un sens puis dans l'autre.Percussion instruments driven by an incompressible fluid under pressure are supplied in such a way that the result of the hydraulic forces applied successively on the striking piston alternately displaces the latter in one direction then in the other.

La mise en service de tels appareils nécessite un réglage soit de la vitesse d'impact du piston sur l'outil, soit de la fréquence de frappe soit encore des deux paramètres simultanément. Pour une puissance de frappe donnée, il est préférable de privilégier l'énergie par coup par rapport à la fréquence, lorsque l'outil rencontre un terrain dur, tandis qu'il est préférable de privilégier la fréquence de frappe par rapport à l'énergie par coup, dans un terrain tendre.The commissioning of such devices requires adjustment either of the impact speed of the piston on the tool, or of the striking frequency or even of the two parameters simultaneously. For a given impact power, it is preferable to favor energy per stroke over frequency, when the tool encounters hard ground, while it is preferable to favor impact frequency over energy suddenly, in soft ground.

Le choix de ces deux paramètres est particulièrement important pour l'obtention d'une pénétration optimale de l'outil et pour la bonne tenue à l'usure et à la fatigue de celui-ci. Il faut en effet considérer que dans un appareil à percussions, l'énergie cinétique du piston se transforme en une onde de compression se propageant dans l'outil. Si cette onde de compression initiale arrive sur un terrain particulièrement dur elle va se réfléchir en grande partie sous forme d'une onde de compression, qui va remonter en direction du piston de frappe.The choice of these two parameters is particularly important for obtaining optimal penetration of the tool and for good resistance to wear and fatigue thereof. It must indeed be considered that in a percussion device, the kinetic energy of the piston is transformed into a compression wave propagating in the tool. If this initial compression wave arrives on particularly hard ground it will be reflected largely in the form of a compression wave, which will go up in the direction of the striking piston.

Dans la mesure où les sections du piston et de l'outil sont approximativement identiques, afin d'assurer l'absence du rebond immédiat du piston sur l'outil, et dans la mesure où, dans le temps nécessaire à un aller-retour de l'onde de choc dans l'outil, aucune force hydraulique n'a pu décoller le piston de celui-ci, le piston de frappe, emmagasinant une grande partie de l'once de choc réfléchie, sera affecté d'une vitesse initiale dans la direction opposée à l'outil et dont la valeur dépend de plusieurs paramètres tels que vitesse d'impact, longueurs et sections respectives du piston et de l'outil, qualités des faces de contact.Insofar as the sections of the piston and of the tool are approximately identical, in order to ensure the absence of the immediate rebound of the piston on the tool, and insofar as, in the time necessary for a round trip of the shock wave in the tool, no hydraulic force could take off the piston from it, the striking piston, storing a large part of the ounce of reflected shock, will be affected by an initial speed in the direction opposite to the tool and whose value depends on several parameters such as impact speed, lengths and respective sections of the piston and the tool, qualities of the contact faces.

Si cette onde de compression initiale arrive dans un terrain tendre, elle sera au contraire fortement absorbée par celui-ci. Dans les mêmes conditions que précédemment, le piston sera affecté d'une vitesse initiale dans la même direction que l'outil et dont la valeur dépend des mêmes paramètres que précédemment.If this initial compression wave arrives in a soft ground, it will on the contrary be strongly absorbed by this one. In the same conditions as above, the piston will be assigned an initial speed in the same direction as the tool and the value of which depends on the same parameters as above.

Certains appareils sont équipés d'un régulateur permettant d'ajuster la pression d'alimentation et par conséquent la vitesse d'impact du piston en fonction de la dureté du terrain et de la nature du travail à effectuer. D'autres appareils sont équipés d'un distributeur actionné hydrauliquement dans les deux sens et assurant l'alternance des forces hydrauliques appliquées au piston. Généralement, ces dispositifs de commande sont réglés de façon définitive en fonction du type de travail envisagé pour l'appareil, sans qu'il soit possible d'obtenir un réglage automatique en fonction des conditions de travail.Some devices are equipped with a regulator allowing the supply pressure and consequently the impact speed of the piston to be adjusted according to the hardness of the ground and the nature of the work to be carried out. Other devices are equipped with a distributor actuated hydraulically in both directions and ensuring the alternation of the hydraulic forces applied to the piston. Generally, these control devices are definitively adjusted according to the type of work envisaged for the device, without it being possible to obtain an automatic adjustment according to the working conditions.

Le brevet français 2 375 008 concerne un dispositif de réglage de la fréquence de frappe par télécommande pneumatique ou électro- hydraulique. Cette télécommande agit sur un tiroir sélectionnant un canal parmi une série de canaux débouchant dans une série de rainures annulaires ménagées dans le cylindre de travail, le canal sélectionné pouvant être relié au réseau d'alimentation en fluide. Ce dispositif nécessitant une intervention manuelle pour le réglage de la fréquence de frappe, ne peut, en aucun cas, réagir et s'adapter automatiquement à la dureté du terrain.French patent 2,375,008 relates to a device for adjusting the striking frequency by pneumatic or electro-hydraulic remote control. This remote control acts on a drawer selecting a channel from a series of channels opening into a series of annular grooves formed in the working cylinder, the selected channel being able to be connected to the fluid supply network. This device, requiring manual intervention to adjust the striking frequency, cannot, in any case, react and adapt automatically to the hardness of the ground.

La présente invention vise à remédier à ces inconvénients. A cet effet, le procédé de commande qu'elle concerne, destiné à un appareil à percussions mû par un fluide incompressible sous pression, alimenté de façon telle que la résultante des forces hydrauliques s'applique successivement dans un sens et dans l'autre, et équipé de dispositifs de régulation pilotables hydrauliquement, susceptibles de faire varier des paramètres de percussion, tels que la vitesse d'impact et/ou la fréquence d'impact du piston est caractérisé en ce qu'il consiste à mesurer, lors de chaque impact du piston sur l'outil, le temps de séjour du piston à proximité de sa position théorique de frappe, puis à agir en fonction de ce temps sur les dispositifs de régulation des paramètres de percussion.The present invention aims to remedy these drawbacks. To this end, the control method which it relates to, intended for a percussion device driven by an incompressible fluid under pressure, supplied in such a way that the result of the hydraulic forces is applied successively in one direction and in the other, and equipped with hydraulically controllable regulation devices capable of varying percussion parameters, such as the impact speed and / or the impact frequency of the piston, is characterized in that it consists in measuring, during each impact of the piston on the tool, the residence time of the piston near its theoretical striking position, then to act as a function of this time on the devices for regulating the impact parameters.

Un appareil pour la mise en oeuvre de ce procédé comporte un canal débouchant à l'intérieur du cylindre contenant le piston de frappe et communiquant avec un circuit primaire relié aux dispositifs de commande des paramètres de percussion, tandis qu'une gorge ménagée dans le piston permet, à chaque impact et pendant le temps de séjour du piston à proximité de sa position théorique de frappe, d'établir une circulation momentanée de fluide entre le circuit primaire et un circuit secondaire. L'information hydraulique fournie aux dispositifs de régulation permet à ceux-ci d'adapter les paramètres de fonctionnement à la nature du sol rencontré par l'outil.An apparatus for implementing this method comprises a channel opening into the interior of the cylinder containing the striking piston and communicating with a primary circuit connected to the devices for controlling the percussion parameters, while a groove formed in the piston allows, at each impact and during the residence time of the piston near its theoretical striking position, to establish a momentary circulation of fluid between the primary circuit and a secondary circuit. The hydraulic information provided to the regulation devices allows them to adapt the operating parameters to the nature of the soil encountered by the tool.

De toute façon, l'invention sera bien comprise à l'aide de la description qui suit en référence au dessin schématique annexé, représentant à titres d'exemples non limitatifs, plusieurs formes d'exécution de cet appareil :

  • Figure 1 est une vue en coupe longitudinale d'un premier appareil équipé d'un régulateur de pression ;
  • Figure 2 est une vue en coupe longitudinale d'une variante de l'appareil de figure 1 ;
  • Figure 3 est une vue en coupe longitudinale d'un appareil équipé d'un distributeur hydraulique d'admission du fluide ;
  • Figure 4 est une vue en coupe longitudinale d'un appareil équipé à la fois d'un régulateur et d'un distributeur ;
  • Figures 5 à 7 correspondent à trois variantes d'exécution d'un appareil, vues en coupe longitudinale, comportant un régulateur d'admission du fluide de commande ;
  • Figures 8 et 9 représentent deux autres formes d'exécution d'un appareil équipé d'un distributeur hydraulique d'admission du fluide.
In any case, the invention will be clearly understood with the aid of the description which follows with reference to the appended schematic drawing, representing by way of nonlimiting examples, several embodiments of this device:
  • Figure 1 is a longitudinal sectional view of a first device equipped with a pressure regulator;
  • Figure 2 is a longitudinal sectional view of a variant of the apparatus of Figure 1;
  • Figure 3 is a longitudinal sectional view of an apparatus equipped with a hydraulic fluid intake distributor;
  • Figure 4 is a longitudinal sectional view of an apparatus equipped with both a regulator and a distributor;
  • Figures 5 to 7 correspond to three alternative embodiments of an apparatus, seen in longitudinal section, comprising an inlet regulator for the control fluid;
  • Figures 8 and 9 show two other embodiments of an apparatus equipped with a hydraulic fluid intake distributor.

L'appareil représenté à la figure 1 concerne un appareil à percussions du type de celui décrit dans le brevet français 81 14043 au nom de la Demanderesse, et comprenant un piston (1) coulissant dans un corps (2) comportant une cavité en forme de cylindre, dans laquelle est monté concentriquement un distributeur (3). Cet appareil est équipé de façon connue d'un régulateur permettant d'ajuster la pression d'alimentation et par suite la vitesse d'impact du piston en fonction de la dureté du terrain et de la nature du travail à exécuter. Ce régulateur comporte un tiroir (4) en équilibre sous la force d'un ressort (5) et sous la pression du fluide d'alimentation amené par un canal (6) et un gicleur (7), et agissant sur la surface (8) d'extrémité du tiroir. Une chambre (11) généralement reliée au circuit de retour basse pression (50) de l'appareil est située du même côté du tiroir que la surface (8). Le tiroir (4) délimite avec les parois de la cavité dans laquelle il est monté, un passage étranglé formant un gicleur (9) assurant le passage du fluide refoulé à travers le canal (10) par le piston, lors de la course de retour de celui-ci. En position d'équilibre le gicleur (9) crée une contre-pression dans le canal (10), lors de la course de retour, telle que la pression d'alimentation agissant sur la section (8) monte à une valeur suffisante pour compenser l'action du ressort (5). Généralement le réglage de la pression d'alimentation se fait en jouant sur le tarage du ressort (5).The device represented in FIG. 1 relates to a percussion device of the type described in French patent 81 14043 in the name of the Applicant, and comprising a piston (1) sliding in a body (2) comprising a cavity in the form of cylinder, in which a distributor (3) is concentrically mounted. This device is equipped in a known manner with a regulator making it possible to adjust the supply pressure and consequently the impact speed of the piston as a function of the hardness of the ground and the nature of the work to be performed. This regulator comprises a drawer (4) in balance under the force of a spring (5) and under the pressure of the supply fluid supplied by a channel (6) and a nozzle (7), and acting on the surface (8 ) at the end of the drawer. A chamber (11) generally connected to the low pressure return circuit (50) of the device is located on the same side of the drawer as the surface (8). The drawer (4) defines with the walls of the cavity in which it is mounted, a throttled passage forming a nozzle (9) ensuring the passage of the fluid discharged through the channel (10) by the piston, during the return stroke thereof. In the equilibrium position the nozzle (9) creates a back pressure in the channel (10), during the return stroke, such that the supply pressure acting on the section (8) rises to a value sufficient to compensate the action of the spring (5). Generally, the supply pressure is adjusted by adjusting the setting of the spring (5).

Conformément à l'invention un canal (12) est ménagé dans le corps (2) qui est équipé d'un gicleur (14), et qui débouche dans la portée (13) du cylindre servant au déplacement du piston. Ce canal (12) est mis en communication avec le fluide à sa pression d'alimentation, par l'intermédiaire d'une gorge (15) que comporte le piston (1). L'arêteAccording to the invention a channel (12) is formed in the body (2) which is equipped with a nozzle (14), and which opens into the bearing surface (13) of the cylinder used for moving the piston. This channel (12) is placed in communication with the fluid at its supply pressure, by means of a groove (15) which comprises the piston (1). The ridge

(16) délimitant une extrémité de la gorge (15) est positionnée de telle sorte que, lorsque le piston (1) se trouve à sa position théorique de frappe, l'orifice (80) au niveau duquel débouche le canal (12) soit entièrement dégagé et assure la mise en communication de ce canal avec la source d'alimentation en fluide sous pression.(16) delimiting one end of the groove (15) is positioned so that, when the piston (1) is in its theoretical striking position, the orifice (80) at which the channel (12) opens fully cleared and ensures the communication of this channel with the pressurized fluid supply source.

La figure 2 correspond à une variante de l'appareil de figure 1 dans laquelle le gicleur (14) monté sur le canal (12) est remplacé par un gicleur (14') disposé sur un canal (56) d'amenée du fluide sous pression.Figure 2 corresponds to a variant of the device of Figure 1 in which the nozzle (14) mounted on the channel (12) is replaced by a nozzle (14 ') disposed on a channel (56) for supplying the fluid under pressure.

Le circuit primaire auquel est relié le canal (12) comporte un tiroir (17) monté coulissant à l'intérieur d'un alésage (20) délimitant d'un côté une chambre (51), appelée ci-après chambre-tampon, communiquant avec le canal (12) et une chambre (52), contenant un ressort (18), reliée au circuit (50) de retour basse pression par un canal (21). Le canal (12) et la chambre tampon (51) sont en communication avec la chambre de pilotage (11) du régulateur d'alimentation en fluide sous pression.The primary circuit to which the channel (12) is connected comprises a slide (17) slidably mounted inside a bore (20) delimiting on one side a chamber (51), hereinafter called the buffer chamber, communicating with the channel (12) and a chamber (52), containing a spring (18), connected to the low pressure return circuit (50) by a channel (21). The channel (12) and the buffer chamber (51) are in communication with the control chamber (11) of the pressurized fluid supply regulator.

Lorsque l'appareil travaille dans un terrain dur la vitesse initiale de rebond du piston. (1) est importante et l'orifice (80) du canal (12) n'est en communication avec la gorge (15) que pendant un temps très bref. La quantité de fluide injectée à chaque cycle dans la chambre tampon (51) par le canal (12) est donc faible.When the device works in hard ground the initial speed of rebound of the piston. (1) is large and the orifice (80) of the channel (12) is in communication with the groove (15) only for a very short time. The amount of fluid injected at each cycle into the buffer chamber (51) through the channel (12) is therefore low.

La pression à l'irtérieur de la chambre de pilotage (11) étant elle-même faible, le tiroir (4) a tendance à fermer le gicleur (9) ce qui augmente la contre-pression dans le canal (10) et par suite augmente la pression d'alimentation et la vitesse d'impact du piston. Si le terrain rencontré par l'outil devient plus tendre la quantité de fluide injectée par cycle dans le canal (12) augmente, ce qui provoque une augmentation de pression d'une part dans la chambre tampon (51) et d'autre part dans la chambre de pilotage (11). Cette augmentation de pression modifie l'équilibre du tiroir (4) dans un sens d'ouverture du gicleur (9) ce qui a pour effet de diminuer la contre-pression existante dans le canal (10) et donc de diminuer la pression d'alimentation en fluide de l'appareil et la vitesse d'impact du piston. Le large dimensionnement du tiroir (17) permet à celui-ci de jouer le rôle d'accumulateur et d'obtenir une pression stabilisée dans la chambre tampon (51), et donc dans la chambre de pilotage (11).The pressure inside the pilot chamber (11) being itself low, the slide (4) tends to close the nozzle (9) which increases the back pressure in the channel (10) and consequently increases the supply pressure and the impact speed of the piston. If the ground encountered by the tool becomes softer, the quantity of fluid injected per cycle in the channel (12) increases, which causes an increase. pressure on the one hand in the buffer chamber (51) and on the other hand in the pilot chamber (11). This increase in pressure modifies the balance of the slide (4) in a direction of opening of the nozzle (9) which has the effect of reducing the existing back pressure in the channel (10) and therefore of reducing the pressure of fluid supply to the device and the impact speed of the piston. The large dimension of the drawer (17) allows it to play the role of accumulator and to obtain a stabilized pressure in the buffer chamber (51), and therefore in the pilot chamber (11).

Le tiroir (17) sera en équilibre pour une pression dans la chambre (51), telle que le débit continu que cette pression permet de faire passer dans la chambre (52) par un gicleur (19) soit égal au débit pulsé injecté par le gicleur (14) dans le canal (12).The drawer (17) will be in equilibrium for a pressure in the chamber (51), such that the continuous flow that this pressure allows to pass through the chamber (52) by a nozzle (19) is equal to the pulsed flow injected by the nozzle (14) in the channel (12).

Il est à noter que dans la forme d'exécution représentée aux figures 1 et 2, il est possible de limiter la pression maximale de la chambre (51) par l'intermédiaire d'un canal (22) débouchant dans l'alésage (20) et en communication avec le réseau basse pression, susceptible d'être mis en communication avec la chambre (51) lorsque la valeur de la pression dans celle-ci dépasse un seuil prédéterminé.It should be noted that in the embodiment shown in Figures 1 and 2, it is possible to limit the maximum pressure of the chamber (51) via a channel (22) opening into the bore (20 ) and in communication with the low pressure network, capable of being placed in communication with the chamber (51) when the value of the pressure in the latter exceeds a predetermined threshold.

La figure 3 représente un appareil dans lequel les mêmes organes sont désignés par les mêmes références que précédemment. Cet appareil fonctionne selon un principe connu, où un distributeur (30) actionné hydrauliquement dans les deux sens assure l'alternance des forces hydrauliques appliquées au piston de frappe. Dans la forme d'exécution représentée à la figure 3 le distributeur (30) est piloté par une section annulaire de commande (33) qui, lorsqu'elle est sous pression, déplace le distributeur en mettant en communication le canal (31) débouchant au-dessus de la tête du piston avec le circuit d'alimentation en fluide sous haute pression.FIG. 3 represents an apparatus in which the same members are designated by the same references as above. This device operates according to a known principle, where a distributor (30) actuated hydraulically in both directions ensures the alternation of the hydraulic forces applied to the striking piston. In the embodiment shown in FIG. 3, the distributor (30) is controlled by an annular control section (33) which, when under pressure, displaces the distributor by putting the channel (31) opening out at communication. above the piston head with the high pressure fluid supply circuit.

Cette chambre (33) est alimentée par un canal (34) débouchant dans une gorge annulaire (40) d'un tiroir (35) monté dans un alésage (20). Cette gorge (40) est susceptible d'être mise en communication, en fonction de la position du tiroir (35) avec un ou plusieurs d'une série de canaux (36 - 39) débouchant dans le cylindre dans lequel est monté coulissant le piston (1). La fonction du tiroir (35) est de sélectionner le canal de commande actif (36 - 39) qui, alimenté à partir de la chambre annulaire (32) délimitée par une gorge (55) du piston, mettra sous pression la section de pilotage (33) et déclenchera le début de course de frappe du piston. En fonction du canal mettant en communication la chambre (33) avec le réseau haute pression, l'alimentation en fluide sous pression de la chambre haute du piston interviendra plus ou moins tôt permettant de faire varier la course du piston et par suite la fréquence de frappe.This chamber (33) is supplied by a channel (34) opening into an annular groove (40) of a drawer (35) mounted in a bore (20). This groove (40) can be placed in communication, depending on the position of the drawer (35) with one or more of a series of channels (36 - 39) opening into the cylinder in which the piston is slidably mounted. (1). The function of the drawer (35) is to select the active control channel (36 - 39) which, supplied from the annular chamber (32) delimited by a groove (55) of the piston, will put under pressure the piloting section (33) and will trigger the start of the piston stroke. Depending on the channel bringing the chamber (33) into communication with the high pressure network, the supply of pressurized fluid to the upper chamber of the piston will intervene more or less early, making it possible to vary the stroke of the piston and consequently the frequency of hit.

La commande de la position du tiroir (35) est obtenue comme dans les formes d'exécution précédentes par l'intermédiaire du canal (12) qui alimente en fluide sous pression la chambre tampon (51). Plus la pression dans la chambre tampon (51) sera importante, plus le tiroir (35) aura tendance à se déplacer à l'encontre de l'action du ressort (18), et plus tôt la cavité de pilotage (33) sera alimentée en fluide sous pression.The control of the position of the drawer (35) is obtained as in the previous embodiments via the channel (12) which supplies pressurized fluid to the buffer chamber (51). The higher the pressure in the buffer chamber (51), the more the drawer (35) will tend to move against the action of the spring (18), and the sooner the pilot cavity (33) will be supplied in pressurized fluid.

La figure 4 représente une variante de cet appareil, dans laquelle celui-ci est équipé à la fois d'un régulateur et d'un distributeur. La pression créée dans la chambre (51) sert d'une part à déplacer le tiroir (35) pour sélectionner la course de frappe et à piloter le tiroir (4) du régulateur de pression d'alimentation, qui modifie la contre-pression de retour de l'appareil, et par suite la pression d'alimentation elle-même et la vitesse de frappe.Figure 4 shows a variant of this device, in which it is equipped with both a regulator and a distributor. The pressure created in the chamber (51) is used on the one hand to move the drawer (35) to select the strike stroke and to control the drawer (4) of the supply pressure regulator, which modifies the back pressure of return of the device, and consequently the supply pressure itself and the typing speed.

La figure 5 représente une variante de réalisation d'un appareil équipé d'un régulateur, dans lequel le canal (12) équipé d'un gicleur (14) est susceptible d'être mis en communication avec le réseau basse pression (50) par l'intermédiaire d'un canal (61) relié à ce réseau et d'une gorge (63) ménagée dans le piston, lorsque la gorge (63) découvre simultanément l'orifice (80) du canal (12) et l'orifice (81) du canal (61), lorsque le piston est à sa position théorique de frappe.FIG. 5 represents an alternative embodiment of an apparatus equipped with a regulator, in which the channel (12) equipped with a nozzle (14) is capable of being placed in communication with the low pressure network (50) by through a channel (61) connected to this network and a groove (63) formed in the piston, when the groove (63) simultaneously discovers the orifice (80) of the channel (12) and the orifice (81) of the channel (61), when the piston is in its theoretical striking position.

Le canal (12) communique comme précédemment avec la chambre tampon (51) qui, dans ce cas, contient le ressort (18) agissant sur le tiroir (17) alors que la chambre arrière (52) située de l'autre côté de ce tiroir est alimentée de façon continue en fluide sous pression par un régulateur de pression ou gicleur (71) lui-même en relation avec le réseau haute pression de l'appareil par un canal (58) ou (59). Un gicleur (19) relie les chambres (51) et (52), et la chambre (51) est en relation avec la chambre de pilotage du tiroir (65) du régulateur par l'intermédiaire d'un canal (76).The channel (12) communicates as before with the buffer chamber (51) which, in this case, contains the spring (18) acting on the slide (17) while the rear chamber (52) located on the other side of this drawer is continuously supplied with pressurized fluid by a pressure regulator or nozzle (71) itself in relation to the high pressure network of the device by a channel (58) or (59). A nozzle (19) connects the chambers (51) and (52), and the chamber (51) is in relation to the control chamber of the slide valve (65) of the regulator via a channel (76).

En pratique le fluide sous pression de la chambre (52) passe par le gicleur (19) dans la chambre (51) et doit s'évacuer par le canal (12) et la gorge (63) vers le canal basse pression (61) et le réseau basse pression (50) en passant par le gicleur (14) monté sur le canal (12) ou un gicleur (14') monté sur le canal (61).In practice, the pressurized fluid from the chamber (52) passes through the nozzle (19) into the chamber (51) and must be evacuated through the channel. (12) and the groove (63) to the low pressure channel (61) and the low pressure network (50) via the nozzle (14) mounted on the channel (12) or a nozzle (14 ') mounted on the channel (61).

Le tiroir (17) sera en équilibre pour une pression dans la chambre (51), telle que le débit pulsé que cette pression permet de faire passer au cours de chaque cycle dans le gicleur (14) ou (14') soit égal au débit fourni par le gicleur (71).The slide (17) will be in equilibrium for a pressure in the chamber (51), such that the pulsed flow that this pressure allows to pass during each cycle in the nozzle (14) or (14 ') is equal to the flow supplied by the nozzle (71).

Dans cette disposition le tiroir (65) du régulateur délimite avec son alésage une chambre (8) reliée à la pression d'alimentation, une chambre (11) reliée au circuit de retour par le canal (64) et une chambre de pilotage (60) antagoniste, reliée à la chambre tampon (51) par le canal (76). Si le terrain rencontré par l'outil devient plus tendre le temps de séjour du piston au contact de l'outil augmente et la quantité de fluide évacué par cycle par le gicleur (14) ou (14') vers le réseau basse pression augmente. Ceci provoque une diminution de pression dans la chambre (51) et par suite dans la chambre (60), ce qui se traduit par un déplacement du tiroir (65) dans un sens d'ouverture du gicleur (9). Cette ouverture diminue la contre-pression dans le canal (10) et par suite la pression d'alimentation de l'appareil et la vitesse d'impact du piston.In this arrangement the slide valve (65) of the regulator delimits with its bore a chamber (8) connected to the supply pressure, a chamber (11) connected to the return circuit by the channel (64) and a pilot chamber (60 ) antagonist, connected to the buffer chamber (51) by the channel (76). If the ground encountered by the tool becomes softer, the residence time of the piston in contact with the tool increases and the quantity of fluid discharged per cycle by the nozzle (14) or (14 ') towards the low pressure network increases. This causes a decrease in pressure in the chamber (51) and consequently in the chamber (60), which results in a displacement of the drawer (65) in a direction of opening of the nozzle (9). This opening reduces the back pressure in the channel (10) and consequently the supply pressure of the device and the impact speed of the piston.

Au contraire, si le terrain rencontré par l'outil devient plus dur la quantité de fluide évacué par cycle par le gicleur (14) ou (14') diminue, ce qui se traduit par une augmentation de pression dans la chambre (51) et par suite dans la chambre de pilotage (60), provoquant un déplacement du tiroir (65) dans un sens de fermeture du gicleur.On the contrary, if the ground encountered by the tool becomes harder the quantity of fluid evacuated by cycle by the nozzle (14) or (14 ') decreases, which results in an increase in pressure in the chamber (51) and consequently in the piloting chamber (60), causing a displacement of the slide (65) in a direction of closing of the nozzle.

Cette fermeture augmente la contre-pression dans le canal (10) et par suite augmente la pression d'alimentation et la vitesse d'impact du piston.This closure increases the back pressure in the channel (10) and consequently increases the supply pressure and the impact speed of the piston.

La figure 6 représente une variante d'exécution de l'appareil de figure 5 dans laquelle le canal (12) et la chambre tampon (51) sont constamment alimentés en fluide sous pression par un gicleur lui-même alimenté en fluide par un canal (58) ou (59). La chambre (52) délimitée pour partie par le tiroir (66) est reliée au circuit de retour de l'appareil par un canal (21) tandis qu'un canal (22) également relié au réseau basse pression débouche dans l'alésage dans lequel est monté le tiroir (66), et est susceptible de mettre la chambre tampon (51) en relation avec le réseau basse pression lorsque la pression dans cette chambre dépasse une valeur prédéterminée.FIG. 6 represents an alternative embodiment of the apparatus of FIG. 5 in which the channel (12) and the buffer chamber (51) are constantly supplied with pressurized fluid by a nozzle itself supplied with fluid by a channel ( 58) or (59). The chamber (52) delimited in part by the slide (66) is connected to the return circuit of the device by a channel (21) while a channel (22) also connected to the low pressure network opens into the bore in which is mounted the drawer (66), and is capable of putting the buffer chamber (51) in relation to the low pressure network when the pressure in this chamber exceeds a predetermined value.

En pratique la pression qui s'établit dans la chambre (51) est telle que la quantité de fluide par cycle s'évacuant par le gicleur (14) vers le réseau basse pression par la gorge (63) du piston est égale à la quantité de fluide par cycle entrant dans la chambre (51) par le régulateur de débit ou gicleur (78).In practice, the pressure which builds up in the chamber (51) is such that the quantity of fluid per cycle discharged by the nozzle (14) towards the low pressure network by the groove (63) of the piston is equal to the quantity of fluid per cycle entering the chamber (51) through the flow regulator or nozzle (78).

Si le terrain rencontré par l'outil devient plus tendre, la quantité de fluide s'évacuant par le gicleur (14) a tendance à augmenter, compte tenu du temps de séjour plus important du piston dans la zone d'impact. Dans ces conditions la pression régnant dans la chambre (51) a tendance à diminuer, de même que celle régnant dans la chambre (60) ce qui modifie la position d'équilibre du tiroir (65) dans un sens d'ouverture du gicleur (9). Cette ouverture du gicleur (9) provoque une diminution de la contre-pression et par suite une diminution de la pression d'alimentation de l'appareil et de la vitesse d'impact du piston.If the ground encountered by the tool becomes softer, the quantity of fluid discharged by the nozzle (14) tends to increase, taking into account the longer residence time of the piston in the impact zone. Under these conditions the pressure prevailing in the chamber (51) tends to decrease, as well as that prevailing in the chamber (60) which modifies the equilibrium position of the drawer (65) in a direction of opening of the nozzle ( 9). This opening of the nozzle (9) causes a decrease in the back pressure and consequently a decrease in the supply pressure of the device and the impact speed of the piston.

Si, au contraire, le terrain rencontré par l'outil devient plus dur, la pression dans la chambre tampon (51) augmente, de même que celle dans la chambre de pilotage (60), ce qui se traduit par un déplacement du tiroir (65) dans un sens de fermeture du gicleur. Cette fermeture augmente la contre-pression dans le canal (10), et par suite augmente la pression d'alimentation de l'appareil et la vitesse d'impact du piston.If, on the contrary, the ground encountered by the tool becomes harder, the pressure in the buffer chamber (51) increases, as does that in the pilot chamber (60), which results in a displacement of the slide ( 65) in a direction of closing of the nozzle. This closure increases the back pressure in the channel (10), and consequently increases the supply pressure of the device and the impact speed of the piston.

La figure 7 représente une variante d'exécution de l'appareil de figure 6, dans laquelle la chambre tampon (51) est alimentée de façon momentanée par un gicleur (78) lui-même alimenté à la pression d'alimentation par un canal (58) ou (59). Le gicleur (78) est monté sur un canal (79) débouchant dans le cylindre dans lequel se déplace le piston (1) du côté opposé au canal (61) par rapport au canal (12). Il est à noter que la hauteur de la gorge (63) est supérieure à la distance entre le canal (12) et le canal (79) d'une part, et le canal (12) et le canal (61) d'autre part, mais inférieure à la distance entre le canal (79) et le canal (61).FIG. 7 represents an alternative embodiment of the apparatus of FIG. 6, in which the buffer chamber (51) is momentarily supplied by a nozzle (78) itself supplied at the supply pressure by a channel ( 58) or (59). The nozzle (78) is mounted on a channel (79) opening into the cylinder in which the piston (1) moves on the side opposite the channel (61) relative to the channel (12). It should be noted that the height of the groove (63) is greater than the distance between the channel (12) and the channel (79) on the one hand, and the channel (12) and the channel (61) on the other part, but less than the distance between the channel (79) and the channel (61).

En pratique lorsque le piston est dans la position représentée à la figure 7, il met en communication les canaux (79) et (12) et assure l'alimentation de la chambre (51) en fluide sous pression. Lorsque le mouvement du piston se poursuit, cette communication est coupée et la gorge (63) met en communication, lorsque le piston arrive à sa position théorique de frappe, le canal (12) avec le réseau basse pression, par l'intermédiaire du canal (61). La pression régnant dans la chambre (51) est telle qu'elle établit l'égalité de la quantité de fluide entrant dans cette chambre lorsque la gorge (63) met en communication le canal (12) et le canal (79) et de la quantité de fluide sortant de cette chambre lorsque la gorge (63) met en communication le canal (12) et le canal (61). Il en résulte que la pression de la chambre (51) dépend de la dureté du terrain.In practice when the piston is in the position shown in FIG. 7, it places the channels (79) and (12) in communication and supplies the chamber (51) with pressurized fluid. When the movement of the piston continues, this communication is cut off and the groove (63) puts in communication, when the piston arrives at its theoretical striking position, the channel (12) with the low pressure network, via the channel (61). The pressure in the chamber (51) is such that it establishes the equality of the quantity of fluid entering this chamber when the groove (63) puts the channel (12) and the channel (79) into communication with the quantity of fluid leaving this chamber when the groove (63) connects the channel (12) and the channel (61). As a result, the pressure of the chamber (51) depends on the hardness of the ground.

Dans l'appareil représenté à la figure 8, les mêmes éléments sont désignés par les mêmes références qu'aux figures 3 et 4.In the apparatus represented in FIG. 8, the same elements are designated by the same references as in FIGS. 3 and 4.

Le circuit primaire auquel est relié le canal (12) comporte une chambre tampon ou chambre de pilotage (51), ménagée dans un alésage (82) prolongé par un alésage (20) de plus faible section. A l'intérieur des alésages (82) et (20) est monté coulissant un tiroir (87), comportant deux parties de sections différentes, qui délimite pour partie la chambre (51), l'extrémité de la cavité opposée à la chambre (51) étant constituée par une chambre (52) reliée au circuit de retour basse pression de l'appareil. A l'intérieur du tiroir (87) est ménagée, d'une part, une gorge périphérique (40), susceptible d'être mise en communication avec un ou plusieurs d'une série de canaux (36-39) débouchant dans le cylindre dans lequel est monté coulissant le piston (13), et une chambre annulaire (84) alimentée par un canal (83) en fluide sous pression. La chambre annulaire (84) étant ménagée dans l'alésage (82) de grande section, la force exercée par le fluide sous pression sur le tiroir (87) tend à déplacer celui-ci dans un sens de diminution du volume de la chambre (51).The primary circuit to which the channel (12) is connected comprises a buffer chamber or pilot chamber (51), formed in a bore (82) extended by a bore (20) of smaller cross section. Inside the bores (82) and (20) is slidably mounted a drawer (87), comprising two parts of different sections, which partly delimits the chamber (51), the end of the cavity opposite the chamber ( 51) being constituted by a chamber (52) connected to the low pressure return circuit of the device. Inside the drawer (87) is provided, on the one hand, a peripheral groove (40), capable of being placed in communication with one or more of a series of channels (36-39) opening into the cylinder in which the piston (13) is slidably mounted, and an annular chamber (84) supplied by a channel (83) with pressurized fluid. The annular chamber (84) being formed in the bore (82) of large section, the force exerted by the fluid under pressure on the drawer (87) tends to move the latter in a direction of reduction of the volume of the chamber ( 51).

La chambre (51) communique également par l'intermédiaire d'un canal (86) avec le circuit de retour basse pression, avec montage sur le canal (86) d'un organe (85) permettant l'écoulement régulé du liquide depuis la chambre (51) vers le circuit basse pression (50).The chamber (51) also communicates via a channel (86) with the low pressure return circuit, with mounting on the channel (86) of a member (85) allowing the regulated flow of the liquid from the chamber (51) to the low pressure circuit (50).

Cet organe de régulation (85) est constitué par une pompe volumétrique actionnée en synchronisme avec le piston de frappe (1). La gorge périphérique (40), ménagée dans le tiroir (87), communique également, comme indiqué au brevet principal, par l'intermédiaire d'un canal (34) avec une chambre de pilotage (33) du distributeur de commande (30) de l'appareil.This regulating member (85) is constituted by a positive displacement pump actuated in synchronism with the striking piston (1). The peripheral groove (40), formed in the drawer (87), also communicates, as indicated in the main patent, via a channel (34) with a pilot chamber (33) of the control distributor (30) of the device.

Le tiroir (87) possède une position stable lorsque la quantité de fluide extraite, par cycle, de la chambre (51) par l'organe (85), est égale à la quantité de fluide injectée, par cycle, dans la chambre (51).The drawer (87) has a stable position when the quantity of fluid extracted, per cycle, from the chamber (51) by the member (85), is equal to the quantity of fluid injected, per cycle, into the chamber (51 ).

Si le terrain rencontré par l'outil devient plus tendre, le temps de séjour du piston au contact de l'outil augmente, de même que le temps d'alimentation en fluide sous pression de la chambre (51) par le canal (12). La quantité de fluide alimentant la chambre (51) étant supérieure à celle évacuée par l'organe (85), le tiroir (87) se déplace dans un sens d'augmentation du volume de la chambre (51), le déplacement de ce tiroir se traduisant par une action sur le distributeur (30) qui va réduire la course de frappe du piston pour trouver une nouvelle position d'équilibre du tiroir (87), telle que la vitesse d'impact soit appropriée à la dureté du terrain.If the ground encountered by the tool becomes softer, the time of stay of the piston in contact with the tool increases, as does the time of supply of pressurized fluid to the chamber (51) through the channel (12). The quantity of fluid supplying the chamber (51) being greater than that evacuated by the member (85), the drawer (87) moves in a direction of increase in the volume of the chamber (51), the displacement of this drawer resulting in an action on the distributor (30) which will reduce the striking stroke of the piston to find a new equilibrium position of the drawer (87), such that the impact speed is appropriate to the hardness of the ground.

Au contraire, si le terrain devient plus dur, le temps de séjour du piston au contact de l'outil diminue, ce qui se traduit par une diminution du volume de fluide envoyé dans la chambre tampon (51), ce volume devenant alors inférieur au volume évacué par l'organe (85).On the contrary, if the ground becomes harder, the residence time of the piston in contact with the tool decreases, which results in a reduction in the volume of fluid sent to the buffer chamber (51), this volume then becoming less than volume evacuated by the organ (85).

Il en résulte un déplacement du tiroir (87) dans un sens de réduction du volume de la chambre (51) qui se traduit par une action sur le distributeur, de telle sorte que celui-ci augmente la course de frappe du piston pour trouver une nouvelle position d'équilibre du tiroir (87), telle que la nouvelle vitesse d'impact soit appropriée à la dureté du terrain.This results in a displacement of the drawer (87) in a direction of reduction of the volume of the chamber (51) which results in an action on the distributor, so that the latter increases the striking stroke of the piston to find a new balance position of the slide (87), such that the new impact speed is appropriate for the hardness of the ground.

Il est à noter que l'équilibre du tiroir est obtenu sans ressort sous l'action, d'une part, de la pression de fluide à l'intérieur de la chambre tampon (51) et, d'autre part, de la pression d'alimentation à l'intérieur de la chambre annulaire (84). En outre, l'utilisation d'une pompe volumétrique comme organe (85) est avantageuse en ce sens qu'elle permet d'extraire, par cycle, toujours la même quantité de fluide, et ceci quelle que soit la fréquence de frappe de l'appareil.It should be noted that the balance of the drawer is obtained without spring under the action, on the one hand, of the fluid pressure inside the buffer chamber (51) and, on the other hand, of the pressure supply inside the annular chamber (84). In addition, the use of a positive displacement pump as a member (85) is advantageous in that it makes it possible to extract, per cycle, always the same quantity of fluid, and this regardless of the striking frequency of the 'apparatus.

La figure 9 représente une variante de l'appareil de figure 8 dans laquelle les mêmes références désignent les mêmes organes que précédemment.FIG. 9 represents a variant of the apparatus of FIG. 8 in which the same references designate the same members as above.

Dans cette seconde forme d'exécution, le circuit secondaire (61), en communication avec le circuit de retour basse' pression (50) de l'appareil, est momentanément relié au circuit primaire comprenant la chambre (51), par l'intermédiaire de la gorge (63) du piston (1), lorsque ce dernier est en contact avec l'outil. Pour sa part, la chambre tampon (51) est alimentée en fluide par l'intermédiaire du canal (86a) sur lequel est monté un organe de régulation de débit (85a) constitué par une pompe volumétrique actionnée en synchronisme avec le piston de frappe.In this second embodiment, the secondary circuit (61), in communication with the low pressure return circuit (50) of the device, is momentarily connected to the primary circuit comprising the chamber (51), via of the groove (63) of the piston (1), when the latter is in contact with the tool. For its part, the buffer chamber (51) is supplied with fluid via the channel (86a) on which is mounted a flow control member (85a) consisting of a positive displacement pump actuated in synchronism with the impact piston.

En pratique, le tiroir (87) occupe une position stable lorsque la quantité de fluide extraite par cycle de la chambre (51) à travers le canal (12), le gicleur (14), la chambre (63) et le canal (61), est égale à la quantité de fluide injectée dans la chambre (51) par le canal (86a) et l'organe (85a).In practice, the drawer (87) occupies a stable position when the quantity of fluid extracted per cycle from the chamber (51) through the channel (12), the nozzle (14), the chamber (63) and the channel (61 ), is equal to the quantity of fluid injected into the chamber (51) through the channel (86a) and the member (85a).

Si le terrain devient plus tendre, la quantité de fluide extraite de la chambre (51) devient, compte tenu de l'augmentation du temps de séjour du piston (1) en position basse, plus importante que la quantité de fluide injectée par l'organe (85a). Il en résulte un déplacement du tiroir (87) dans un sens de réduction du volume de la chambre (51) sous l'action de la pression d'alimentation dans la chambre (84), qui se traduit par une action sur le distributeur de commande de l'appareil qui diminue la course de frappe du piston.If the ground becomes softer, the quantity of fluid extracted from the chamber (51) becomes, taking into account the increase in the residence time of the piston (1) in the lower position, greater than the quantity of fluid injected by the organ (85a). This results in a displacement of the drawer (87) in a direction of reduction of the volume of the chamber (51) under the action of the supply pressure in the chamber (84), which results in an action on the dispenser. device control which decreases the stroke of the piston.

Au contraire, si le terrain devient plus dur, la quantité de fluide extraite de la chambre (51), compte tenu du faible temps de séjour du piston au contact de l'outil, devient inférieure à la quantité de fluide admise par l'organe (85a). Le tiroir (87) se déplace alors dans un sens d'augmentation du volume de la chambre (51), agissant sur le distributeur (30) pour que celui-ci augmente la course de frappe du piston.On the contrary, if the ground becomes harder, the quantity of fluid extracted from the chamber (51), taking into account the short residence time of the piston in contact with the tool, becomes less than the quantity of fluid admitted by the member. (85a). The slide (87) then moves in a direction of increase in the volume of the chamber (51), acting on the distributor (30) so that the latter increases the striking stroke of the piston.

Comme il ressort de ce qui précède, l'invention apporte une grande amélioration à la technique existante en fournissant un procédé et un appareil permettant d'adapter, automatiquement et instantanément, certains paramètres de percussion tels que vitesse d'impact et fréquence du piston à la dureté du terrain dans lequel travaille l'appareil.As is apparent from the above, the invention brings a great improvement to the existing technique by providing a method and an apparatus making it possible to adapt, automatically and instantaneously, certain percussion parameters such as impact speed and frequency of the piston to the hardness of the ground in which the device works.

Claims (16)

1- Procédé de commande du mouvement du piston de frappe d'un appareil à percussions mû par un fluide incompressible sous pression, alimenté de façon telle que la résultante des forces hydrauliques s'applique successivement dans un sens puis dans l'autre, cet appareil étant équipé de dispositifs de régulation pilotables hydrauliquement susceptibles de faire varier des paramètres de percussion tels que la vitesse d'impact et/ou la fréquence de frappe du piston, caractérisé en ce qu'il consiste à mesurer, lors de chaque impact du piston (1) sur l'outil, le temps de séjour du piston à proximité de sa position théorique de frappe, puis à agir en fonction de ce temps sur les dispositifs (4, 30, 65) de régulation des paramètres de percussion.1- Method for controlling the movement of the striking piston of a percussion device driven by an incompressible fluid under pressure, supplied in such a way that the result of the hydraulic forces is applied successively in one direction then in the other, this device being equipped with hydraulically controllable regulating devices capable of varying percussion parameters such as the impact speed and / or the striking frequency of the piston, characterized in that it consists in measuring, at each impact of the piston ( 1) on the tool, the residence time of the piston near its theoretical striking position, then to act as a function of this time on the devices (4, 30, 65) for regulating the impact parameters. 2- Appareil à percussions pour la mise en oeuvre du procédé selon la revendication 1, du type comprenant un piston (1) déplaçable alternativement à l'intérieur d'un cylindre, sous l'action de la résultante des forces hydrauliques, et équipé de dispositifs de régulation (4, 30, 65) pilotables hydrauliquement, susceptibles de faire varier des paramètres de percussion tels que la vitesse d'impact et/ou la fréquence de frappe du piston, caractérisé en ce qu'il comporte un canal (12) débouchant à l'intérieur du cylindre contenant le piston de frappe (1) et communiquant avec un circuit primaire relié aux dispositifs de commande des paramètres de percussion, tandis qu'une gorge (15, 55, 63) ménagée dans le piston permet, à chaque impact et pendant le temps de séjour du piston à proximité de sa position théorique de frappe, d'établir une circulation momentanée de fluide entre le circuit primaire et un circuit secondaire.2- percussion device for implementing the method according to claim 1, of the type comprising a piston (1) which can be moved alternately inside a cylinder, under the action of the resultant of hydraulic forces, and equipped with regulation devices (4, 30, 65) hydraulically controllable, capable of varying percussion parameters such as the impact speed and / or the striking frequency of the piston, characterized in that it comprises a channel (12) opening into the cylinder containing the striking piston (1) and communicating with a primary circuit connected to the devices for controlling the percussion parameters, while a groove (15, 55, 63) formed in the piston allows, each impact and during the residence time of the piston near its theoretical striking position, to establish a momentary circulation of fluid between the primary circuit and a secondary circuit. 3- Appareil à percussions selon la revendication 2, caractérisé en ce que le circuit primaire comporte une chambre tampon (51) dont l'une des parois est délimitée par un tiroir coulissant (17, 35, 66) permettant de créer, à partir du fluide injecté dans le canal (12) une pression stabilisée dont la valeur dépend de la résistance à la pénétration de l'outil dans le terrain, et qui est utilisée pour piloter les dispositifs de régulation des paramètres de percussion.3- percussion device according to claim 2, characterized in that the primary circuit comprises a buffer chamber (51) one of the walls of which is delimited by a sliding drawer (17, 35, 66) making it possible to create, from the fluid injected into the channel (12) a stabilized pressure whose value depends on the resistance to penetration of the tool into the ground, and which is used to control the devices for regulating the percussion parameters. 4- Appareil à percussions selon la revendication 3, caractérisé en ce que le circuit secondaire est en communication avec le circuit d'alimentation en fluide sous haute pression et est momentanément relié au circuit primaire, lorsque la gorge (15, 55) ménagée dans le piston (1) se trouve en regard de l'orifice (80) du canal (12) débouchant dans le cylindre, et en ce que la chambre tampon (51) alimentée par ledit canal (12), est mise en communication avec une chambre (52) située de l'autre côté du tiroir annexe, par l'intermédiaire d'un orifice (19) formant gicleur, cette seconde chambre ou chambre arrière du tiroir étant reliée au circuit de retour basse pression (50).4- percussion device according to claim 3, characterized in that the secondary circuit is in communication with the fluid supply circuit under high pressure and is momentarily connected to the primary circuit, when the groove (15, 55) formed in the piston (1) is located opposite the orifice (80) of the channel (12) opening into the cylinder, and in that the buffer chamber (51) supplied by said channel (12), is placed in communication with a chamber ( 52) located on the other side of the auxiliary drawer, via an orifice (19) forming a nozzle, this second chamber or rear chamber of the drawer being connected to the low pressure return circuit (50). 5- Appareil à percusions selon la revendication 3, caractérisé en ce que le circuit secondaire (61) est en communication avec le circuit de retour (50) de l'appareil et est momentanément relié au circuit primaire, par l'intermédiaire de la gorge (63) du piston (1) lorsque ce dernier est en contact avec l'outil, tandis que la chambre tampon (51), reliée au canal précité, est en communication par l'intermédiaire d'un orifice (19) formant gicleur avec la chambre arrière (52) du tiroir (17) qui est elle-même alimentée par l'intermédiaire d'un régulateur de pression ou gicleur (71) par le fluide d'alimentation haute pression de l'appareil.5- percussion device according to claim 3, characterized in that the secondary circuit (61) is in communication with the return circuit (50) of the device and is momentarily connected to the primary circuit, via the groove (63) of the piston (1) when the latter is in contact with the tool, while the buffer chamber (51), connected to the aforementioned channel, is in communication via an orifice (19) forming a nozzle with the rear chamber (52) of the drawer (17) which is itself supplied by means of a pressure regulator or nozzle (71) by the high pressure supply fluid of the device. 6- Appareil à percussions selon la revendication 3, caractérisé en ce que le circuit secondaire (61) est en communication, avec le circuit de retour (50) de l'appareil, et est momentanément relié au circuit primaire par l'intermédiaire de la gorge (63) du piston lorsque ce dernier est en position théorique de frappe, tandis que le canal (12) débouchant dans la chambre tampon (51) comporte un gicleur (14) et est alimenté par un régulateur de débit ou un gicleur (78) en fluide à la pression d'alimentation de l'appareil, alors que la chambre arrière (52), située du côté du tiroir (66) opposé à la chambre tampon, est relié au circuit de retour basse pression (50).6- percussion device according to claim 3, characterized in that the secondary circuit (61) is in communication with the return circuit (50) of the device, and is momentarily connected to the primary circuit via the groove (63) of the piston when the latter is in theoretical striking position, while the channel (12) opening into the buffer chamber (51) comprises a nozzle (14) and is supplied by a flow regulator or a nozzle (78 ) in fluid at the supply pressure of the device, while the rear chamber (52), located on the side of the slide (66) opposite the buffer chamber, is connected to the low pressure return circuit (50). 7- Appareil à percussions selon la revendication 3, caractérisé en ce que débouchent, dans le cylindre où se déplace le piston (1), outre le canal (12) en relation avec le circuit primaire, d'une part, un canal (79) comportant un gicleur (78) et relié en permanence au circuit d'alimentation haute pression de l'appareil et, d'autre part, un canal (61) en communication avec le circuit basse pression (50) de l'appareil, ces deux derniers canaux (79, 61) étant situés de part et d'autre du premier canal cité (12), et disposés chacun à une distance de ce dernier inférieure à la hauteur de la gorge (63) ménagée dans le piston (1), la chambre tampon (51) étant en communication avec le canal (12), et la chambre arrière (52) située du côté opposé du tiroir étant pour sa part reliée au circuit de retour basse pression (50) de l'appareil, les différents canaux (79, 12, 61) étant disposés de telle sorte que, pendant le cycle de fonctionnement, la gorge (63) du piston mette le canal (12) en communication de façon momentanée et alternative, d'une part, avec le circuit d'alimentation de l'appareil et, d'autre part, avec le circuit de retour de celui-ci lorsque le piston arrive à sa position théorique de frappe.7- percussion device according to claim 3, characterized in that open into the cylinder where the piston (1) moves, in addition to the channel (12) in relation to the primary circuit, on the one hand, a channel (79 ) comprising a nozzle (78) and permanently connected to the high pressure supply circuit of the device and, on the other hand, a channel (61) in communication with the low pressure circuit (50) of the device, these two last channels (79, 61) being located on either side of the first cited channel (12), and each arranged at a distance from the latter less than the height of the groove (63) formed in the piston (1) , the buffer chamber (51) being in communication with the channel (12), and the rear chamber (52) located on the opposite side of the slide being for its part connected to the low pressure return circuit (50) of the device, the various channels (79, 12, 61) being arranged so that, during the operating cycle, the groove (63) of the piston places the channel (12) in temporary and alternative communication, on the one hand, with the power supply circuit of the device and, on the other hand, with the return circuit thereof when the piston arrives at its theoretical striking position. 8- Appareil à percussions selon l'une quelconque des revendications 2 à 7, caractérisé en ce que la pression de fluide est utilisée pour piloter un régulateur de pression servant à ajuster la pression d'alimentation de l'appareil, de telle sorte que, lorsque la pression dans la chambre tampon (51) et sur le tiroir (4, 65) du régulateur varie, le régulateur commande une variation de la pression d'alimentation et, par suite, une variation de la vitesse d'impact du piston.8- percussion device according to any one of claims 2 to 7, characterized in that the fluid pressure is used to control a pressure regulator serving to adjust the supply pressure of the device, so that, when the pressure in the buffer chamber (51) and on the regulator slide (4, 65) varies, the regulator controls a variation of the supply pressure and, consequently, a variation of the impact speed of the piston. 9- Appareil à percussions selon l'une quelconque des revendications 3 à 7, caractérisé en ce que le tiroir (35) délimitant, pour partie, la chambre tampon (51), est monté coulissant dans un cylindre dans lequel débouchent plusieurs canaux (36-39) décalés axialement, qui débouchent également dans le cylindre de guidage du piston (1), le tiroir comportant une gorge périphérique (40) susceptible, en fonction de la position du tiroir, d'être mise en communication avec l'un ou l'autre des canaux précités, eux-mêmes en communication par l'intermédiaire de la gorge du piston avec le réseau d'alimentation haute-pression, un autre canal débouchant dans le cylindre en regard du volume annulaire ménagé par la gorge du tiroir, qui demeure en permanence en communication avec ce volume, et qui est relié à un distributeur de régulation de la fréquence de frappe, de façon telle que plus le temps de séjour du piston au point d'impact est court, plus la fréquence de frappe sera importante.9- Percussion device according to any one of claims 3 to 7, characterized in that the drawer (35) delimiting, in part, the buffer chamber (51), is slidably mounted in a cylinder into which open several channels (36 -39) axially offset, which also open into the piston guide cylinder (1), the drawer having a peripheral groove (40) capable, depending on the position of the drawer, of being placed in communication with one or the other of the above-mentioned channels, themselves in communication via the groove of the piston with the high-pressure supply network, another channel opening into the cylinder opposite the annular volume formed by the groove of the drawer, which remains permanently in communication with this volume, and which is connected to a distributor for regulating the striking frequency, so that the shorter the residence time of the piston at the point of impact, the more the striking frequency will be important. 10- Appareil à percussions selon l'ensemble des revendications 8 et 9, caractérisé en ce que la pression régnant dans le circuit primaire sert, simultanément, à piloter un régulateur de pression servant à ajuster la pression d'alimentation de l'appareil et à déplacer le tiroir limitant pour partie la chambre tampon pour ajuster la course du piston et par suite la fréquence de frappe.10- Percussion device according to all of claims 8 and 9, characterized in that the pressure prevailing in the primary circuit serves simultaneously to control a pressure regulator used to adjust the supply pressure of the device and to move the drawer partially limiting the buffer chamber to adjust the stroke of the piston and consequently the striking frequency. 11- Appareil à percussions selon l'une quelconque des revendications 2 à 10, caractérisé en ce qu'à l'intérieur du cylindre contenant le tiroir (17, 35, 66) délimitant pour partie la chambre tampon (51), débouche un canal (22) relié au circuit de retour basse pression (50) de l'appareil, ce canal étant normalement obturé par le tiroir, et susceptible d'être mis en communication avec la chambre tampon (51) lorsque la pression à l'intérieur de celle-ci dépasse une valeur prédéterminée.11- Percussion device according to any one of claims 2 to 10, characterized in that inside the cylinder containing the drawer (17, 35, 66) partially defining the buffer chamber (51), opens a channel (22) connected to the low pressure return circuit (50) of the device, this channel being normally closed by the drawer, and capable of being placed in communication with the buffer chamber (51) when the pressure inside the latter exceeds a predetermined value. 12- Appareil à percussions selon la revendication 2, caractérisé en ce qu'il comprend une chambre tampon (51) qui, délimitée par un tiroir coulissant permettant de créer une pression constante et communiquant avec un canal (12) débouchant à l'intérieur du cylindre contenant le piston de frappe, communique, en outre, avec un canal sur lequel est disposé un organe (85) de régulation du débit de fluide, constitué par une pompe volumétrique.12- Percussion device according to claim 2, characterized in that it comprises a buffer chamber (51) which, delimited by a sliding drawer making it possible to create a constant pressure and communicating with a channel (12) opening inside the cylinder containing the impact piston, communicates, in addition, with a channel on which is disposed a member (85) for regulating the flow of fluid, consisting of a positive displacement pump. 13- Appareil à percussions selon la revendication 12, caractérisé en ce que l'organe de régulation du débit de fluide est constitué par une pompe volumétrique actionnée en synchronisme avec le piston de frappe.13- Percussion device according to claim 12, characterized in that the fluid flow regulation member is constituted by a positive displacement pump actuated in synchronism with the striking piston. 14- Appareil à percussions selon l'une quelconque des revendications 12 et 13, caractérisé en ce que le circuit secondaire, en communication avec le circuit d'alimentation en fluide sous haute pression, est momentanément relié au circuit primaire, lorsque la gorge (55), ménagée dans le piston (1), se trouve en regard de l'orifice (80) du canal (12) débouchant dans le cylindre, et en ce que la chambre tampon (51), alimentée par ledit canal (12), est en communication avec le circuit de basse pression (50) par l'intermédiaire d'un canal d'évacuation de fluide (86) sur lequel est monté l'organe (85) de régulation du débit de fluide.14- Percussion device according to any one of claims 12 and 13, characterized in that the secondary circuit, in communication with the fluid supply circuit under high pressure, is momentarily connected to the primary circuit, when the groove (55 ), formed in the piston (1), is located opposite the orifice (80) of the channel (12) opening into the cylinder, and in that the buffer chamber (51), supplied by said channel (12), is in communication with the low pressure circuit (50) via a fluid discharge channel (86) on which is mounted the member (85) for regulating the flow of fluid. 15- Appareil à percussions selon l'une quelconque des revendications 12 et 13, caractérisé en ce que le circuit secondaire, en communication avec le circuit de retour basse pression (50) de l'appareil, est momentanément relié au circuit primaire, par l'intermédiaire de la gorge (63) du piston (1) lorsque ce dernier est en contact avec l'outil, et en ce que la chambre tampon (51), reliée au canal (12), est alimentée en fluide à partir du circuit basse pression par l'intermédiaire de l'organe (85a) de régulation du débit de fluide.15- Percussion device according to any one of claims 12 and 13, characterized in that the secondary circuit, in communication with the low pressure return circuit (50) of the device, is momentarily connected to the primary circuit, by l intermediate of the groove (63) of the piston (1) when the latter is in contact with the tool, and in that the buffer chamber (51), connected to the channel (12), is supplied with fluid from the circuit low pressure by means of the member (85a) for regulating the flow of fluid. 16- Appareil à percussions selon l'une quelconque des revendications 12 à 15, caractérisé en ce que le tiroir coulissant (87) délimitant pour partie la chambre tampon (51) comporte deux parties coaxiales, dont celle située du côté de la chambre tampon est de section supérieure à celle de l'autre partie, ce tiroir étant monté coulissant dans deux alésages coaxiaux (82, 20) de sections correspondant à celles des deux parties du tiroir, avec ménagement d'une chambre annulaire (84) entre le tiroir et l'alésage de grande section, en communication avec la source d'alimentation en fluide sous pression de l'appareil.16- percussion device according to any one of claims 12 to 15, characterized in that the sliding drawer (87) partly defining the buffer chamber (51) has two coaxial parts, including that located on the side of the buffer chamber is of section larger than that of the other part, this drawer being slidably mounted in two coaxial bores (82, 20) of sections corresponding to those of the two parts of the drawer, with an annular chamber (84) between the drawer and the bore of large section, in communication with the source of fluid supply under device pressure.
EP86420181A 1985-07-16 1986-07-07 Method of controlling the movement of the impacting piston of a non-compressible fluid-actuated percussion device, and device therefor Expired - Lifetime EP0214064B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86420181T ATE55080T1 (en) 1985-07-16 1986-07-07 METHOD AND APPARATUS FOR CONTROLLING THE MOVEMENT OF THE IMPACT PISTON OF AN INCOMPRESSible FLUID-DRIVEN IMPACT DEVICE.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8511346A FR2584968B1 (en) 1985-07-16 1985-07-16 METHOD FOR CONTROLLING THE MOVEMENT OF THE IMPACT PISTON OF A PERCUSSION APPARATUS MOUSED BY AN INCOMPRESSIBLE PRESSURE FLUID, AND APPARATUS FOR IMPLEMENTING THE METHOD
FR8604302 1986-03-18
FR868604302A FR2595972B2 (en) 1985-07-16 1986-03-18 PERCUSSION APPARATUS
FR8511346 1986-03-18

Publications (2)

Publication Number Publication Date
EP0214064A1 true EP0214064A1 (en) 1987-03-11
EP0214064B1 EP0214064B1 (en) 1990-08-01

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Application Number Title Priority Date Filing Date
EP86420181A Expired - Lifetime EP0214064B1 (en) 1985-07-16 1986-07-07 Method of controlling the movement of the impacting piston of a non-compressible fluid-actuated percussion device, and device therefor

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Country Link
US (1) US4899836A (en)
EP (1) EP0214064B1 (en)
JP (1) JPH0698578B2 (en)
AU (1) AU592357B2 (en)
CA (1) CA1288317C (en)
DE (2) DE214064T1 (en)
ES (1) ES8706506A1 (en)
FI (1) FI86762C (en)
FR (1) FR2595972B2 (en)
NO (1) NO167266C (en)

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EP0256955B1 (en) * 1986-08-07 1990-11-07 Etablissements Montabert Method and apparatus for adjusting the percussion parameters of the impacting piston of a non compressible fluid-actuated device
EP0461565A1 (en) * 1990-06-14 1991-12-18 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Method and device for the determination of characteristic features of an impact motor
EP0486898A1 (en) * 1990-11-20 1992-05-27 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Method and device for adjustment of working caracteristics of an impact mechanism to the hardness of the material to be destroyed
EP0688636A1 (en) * 1994-06-23 1995-12-27 Bretec Oy Hydraulic percussion hammer
EP0715932A1 (en) 1994-12-08 1996-06-12 Etablissements Montabert Method and apparatus for adjusting the stroke of a non-compressible fluid-actuated percussion device
EP0752297A2 (en) * 1995-07-06 1997-01-08 Bretec Oy Hydraulic percussion hammer
FR2902684A1 (en) * 2006-06-27 2007-12-28 Montabert Soc Par Actions Simp METHOD FOR SWITCHING THE STROKE STROKE OF A MU-PERCUSSION APPARATUS BY AN INCOMPRESSIBLE FLUID UNDER PRESSURE, AND APPARATUS FOR CARRYING OUT SAID METHOD
CN100522501C (en) * 2004-10-20 2009-08-05 阿特拉斯科普科凿岩机股份公司 Percussion device
WO2013083903A1 (en) 2011-12-09 2013-06-13 Montabert Method for switching between striking stroke lengths of a percussive tool striking piston
EP1963052A4 (en) * 2005-12-22 2016-07-27 Atlas Copco Rock Drills Ab Pulse generator and impulse machine for a cutting tool
WO2019158849A1 (en) 2018-02-14 2019-08-22 Montabert Method for adjusting the striking stroke of a striking piston of a percussion apparatus, and a percussion apparatus for implementing said method

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JP2669761B2 (en) * 1993-02-15 1997-10-29 電気化学工業株式会社 Powdery cement dispersant and method for producing the same
FI941689A (en) * 1994-04-13 1995-10-14 Doofor Oy A method and drill for adjusting the shape of an impact pulse transmitted to a drill bit
CN2215384Y (en) * 1994-12-30 1995-12-20 陈利钧 Energy-storage impact controller
FI104961B (en) * 1996-07-19 2000-05-15 Sandvik Tamrock Oy Hydraulic impact hammer
FI107891B (en) * 1998-03-30 2001-10-31 Sandvik Tamrock Oy Impact fluid driven impactor
US6035634A (en) 1999-02-09 2000-03-14 Latch-Tool Development Co. Llc Compact, resistance regulated, multiple output hydraulic tool and seal valve arrangement
US6491114B1 (en) 2000-10-03 2002-12-10 Npk Construction Equipment, Inc. Slow start control for a hydraulic hammer
DE102004035306A1 (en) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Pressure medium operated impact device, in particular hydraulic hammer
SE528081C2 (en) * 2004-08-25 2006-08-29 Atlas Copco Constr Tools Ab Hydraulic impact mechanism
SE527762C2 (en) * 2004-10-14 2006-05-30 Atlas Copco Rock Drills Ab percussion
SE528745C2 (en) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Valve device for percussion and percussion for rock drill
SE530885C2 (en) * 2007-02-23 2008-10-07 Atlas Copco Rock Drills Ab Procedure for percussion, percussion and rock drilling
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
FI123634B (en) * 2007-10-05 2013-08-30 Sandvik Mining & Constr Oy Mining equipment, protective valve and method for using mining equipment
CN101927479B (en) * 2009-06-23 2014-10-22 蒙塔博特公司 Hydraulic impact equipment
AU2011301130A1 (en) * 2010-09-10 2013-03-07 Rockdrill Services Australia Pty Ltd Improved rock drill
US9701003B2 (en) * 2014-05-23 2017-07-11 Caterpillar Inc. Hydraulic hammer having delayed automatic shutoff
FR3027543B1 (en) 2014-10-28 2016-12-23 Montabert Roger PERCUSSION APPARATUS
US9840000B2 (en) * 2014-12-17 2017-12-12 Caterpillar Inc. Hydraulic hammer having variable stroke control
US20160199969A1 (en) * 2015-01-12 2016-07-14 Caterpillar Inc. Hydraulic hammer having variable stroke control
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
US10377028B2 (en) * 2016-03-14 2019-08-13 Caterpillar Inc. Hammer protection system and method
ES2945157T3 (en) 2017-07-24 2023-06-28 Furukawa Rock Drill Co Ltd hydraulic percussion device
FR3134738A1 (en) * 2022-04-20 2023-10-27 Montabert Percussion device equipped with a pressure regulating device

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EP0070246A1 (en) * 1981-07-10 1983-01-19 Etablissements Montabert Hydraulic percussion device
EP0080446A2 (en) * 1981-11-20 1983-06-01 Atlas Copco Aktiebolag Method of controlling an impact motor and an impact motor

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FR2375008A1 (en) * 1976-12-23 1978-07-21 Krupp Gmbh HYDRAULIC OR PNEUMATIC SHEEP WITH REMOTE CONTROLLED STRIKE FREQUENCY
EP0070246A1 (en) * 1981-07-10 1983-01-19 Etablissements Montabert Hydraulic percussion device
EP0080446A2 (en) * 1981-11-20 1983-06-01 Atlas Copco Aktiebolag Method of controlling an impact motor and an impact motor

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0256955B1 (en) * 1986-08-07 1990-11-07 Etablissements Montabert Method and apparatus for adjusting the percussion parameters of the impacting piston of a non compressible fluid-actuated device
EP0461565A1 (en) * 1990-06-14 1991-12-18 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Method and device for the determination of characteristic features of an impact motor
DE4019019A1 (en) * 1990-06-14 1991-12-19 Krupp Maschinentechnik METHOD FOR DETERMINING CHARACTERISTIC CHARACTERISTICS OF A STRIKE AND DEVICE FOR IMPLEMENTING THE METHOD
EP0486898A1 (en) * 1990-11-20 1992-05-27 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Method and device for adjustment of working caracteristics of an impact mechanism to the hardness of the material to be destroyed
EP0688636A1 (en) * 1994-06-23 1995-12-27 Bretec Oy Hydraulic percussion hammer
US5653295A (en) * 1994-06-23 1997-08-05 Bretec Oy Hydraulic precussion hammer
US5669281A (en) * 1994-12-08 1997-09-23 Etablissements Montabert Method and machine for altering the striking stroke of a percussive machine moved by a pressurized incompressible fluid
EP0715932A1 (en) 1994-12-08 1996-06-12 Etablissements Montabert Method and apparatus for adjusting the stroke of a non-compressible fluid-actuated percussion device
US5890548A (en) * 1995-07-06 1999-04-06 Bretec Oy Hydraulic percussion hammer
EP0752297A3 (en) * 1995-07-06 1998-01-14 Bretec Oy Hydraulic percussion hammer
EP0752297A2 (en) * 1995-07-06 1997-01-08 Bretec Oy Hydraulic percussion hammer
CN100522501C (en) * 2004-10-20 2009-08-05 阿特拉斯科普科凿岩机股份公司 Percussion device
EP1963052A4 (en) * 2005-12-22 2016-07-27 Atlas Copco Rock Drills Ab Pulse generator and impulse machine for a cutting tool
FR2902684A1 (en) * 2006-06-27 2007-12-28 Montabert Soc Par Actions Simp METHOD FOR SWITCHING THE STROKE STROKE OF A MU-PERCUSSION APPARATUS BY AN INCOMPRESSIBLE FLUID UNDER PRESSURE, AND APPARATUS FOR CARRYING OUT SAID METHOD
WO2008000958A2 (en) * 2006-06-27 2008-01-03 Montabert Percussion equipment driven by a pressurized incompressible fluid
WO2008000958A3 (en) * 2006-06-27 2008-02-21 Montabert Roger Percussion equipment driven by a pressurized incompressible fluid
CN101500761B (en) * 2006-06-27 2012-01-25 蒙塔贝特公司 Percussion equipment driven by a pressurized incompressible fluid
US8151900B2 (en) 2006-06-27 2012-04-10 Montabert Percussion equipment driven by a pressurized incompressible fluid
WO2013083903A1 (en) 2011-12-09 2013-06-13 Montabert Method for switching between striking stroke lengths of a percussive tool striking piston
US9981371B2 (en) 2011-12-09 2018-05-29 Montabert Method for switching the striking stroke of a striking piston of a percussion device
WO2019158849A1 (en) 2018-02-14 2019-08-22 Montabert Method for adjusting the striking stroke of a striking piston of a percussion apparatus, and a percussion apparatus for implementing said method

Also Published As

Publication number Publication date
AU592357B2 (en) 1990-01-11
NO862855L (en) 1987-01-19
FI86762B (en) 1992-06-30
DE3673100D1 (en) 1990-09-06
CA1288317C (en) 1991-09-03
EP0214064B1 (en) 1990-08-01
FI86762C (en) 1992-10-12
NO167266C (en) 1991-10-23
NO862855D0 (en) 1986-07-15
FR2595972A2 (en) 1987-09-25
JPS6219386A (en) 1987-01-28
US4899836A (en) 1990-02-13
FI862952A (en) 1987-01-17
AU6018286A (en) 1987-01-22
FR2595972B2 (en) 1989-10-20
ES556161A0 (en) 1987-07-01
JPH0698578B2 (en) 1994-12-07
DE214064T1 (en) 1987-07-02
ES8706506A1 (en) 1987-07-01
NO167266B (en) 1991-07-15
FI862952A0 (en) 1986-07-15

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