EP0214064B1 - 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
EP0214064B1
EP0214064B1 EP86420181A EP86420181A EP0214064B1 EP 0214064 B1 EP0214064 B1 EP 0214064B1 EP 86420181 A EP86420181 A EP 86420181A EP 86420181 A EP86420181 A EP 86420181A EP 0214064 B1 EP0214064 B1 EP 0214064B1
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EP
European Patent Office
Prior art keywords
piston
conduit
pressure
chamber
communication
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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.)
Expired - Lifetime
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EP86420181A
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German (de)
French (fr)
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EP0214064A1 (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
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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 Under 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.
  • 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.
  • Document US-A-3,908,767 relates to a percussion device comprising a distributor of simple structure and allowing a flow rate for the passage of hydraulic fluid.
  • This device has a movement control conduit comprising several orifices opening into the cylinder inside which the striking piston moves, the manual selection of these orifices making it possible to control the movement of the distributor.
  • this device does not allow movement control for automatic adaptation of the strike to the hardness of the ground.
  • the present invention aims to remedy these drawbacks.
  • 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 then in the other, this device being equipped with hydraulically controllable regulating devices capable of varying percussion parameters, the impact speed and the striking frequency of the piston, is characterized, according to the invention, in that it consists, during each impact of the piston on the tool, to be modified, relative to the duration of stay of the piston near its theoretical striking zone, the flow of fluid in a channel connected to the devices regulating the parameters of percussion.
  • 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 period of stay of the piston near its theoretical striking area, to establish a momentary circulation of fluid between the primary circuit and a secondary circuit.
  • the hydraulic information supplied to the regulation devices allows them to adapt the operating parameters to the nature of the soil encountered by the tool.
  • the device shown in Figure 1 relates to a percussion device of the type described in French patent 81 14043 (EP-A-0 070 246) in the name of the Applicant, and comprising a piston (1) sliding in a body (2) comprising a cylinder-shaped cavity, 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 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 edge (16) delimiting one end of the groove (15) is positioned so that, when the piston (1) is at its theoretical striking area, the orifice (80) at which the channel opens ( 12) is completely free and ensures the communication of this channel with the pressurized fluid supply source.
  • 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 initial rebound speed of the piston (1) is high 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.
  • 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 in pressure on the one hand in the buffer chamber (51) and on the other hand in the piloting 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 piloted by an annular control section (33) which, when under pressure, moves the distributor by putting in communication the channel (31) opening above the piston head with the fluid supply circuit under high pressure.
  • 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 slide valve (35) is to select the active control channel (36-39) which, fed from the annular chamber (32) delimited by a groove (55) of the piston, will pressurize 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) towards the low pressure channel (61). and the low pressure network (50) passing through 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).
  • 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 prevailing in the chamber (51) is such that it establishes the equality of the quantity of fluid entering this chamber when the groove (63) places the channel (12) and the channel (79) in communication with the quantity of fluid leaving this chamber when the groove (63) puts the channel (12) and the channel (61) in communication.
  • 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) consisting of 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 duration 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 feed 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 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 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.
  • 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)

Abstract

1. A method of controlling the movement of the impacting piston of a non-compressible pressure fluid-actuated percussion apparatus, supplied in a manner such that the resultant of the hydraulic force is applied successively in one direction and then in the other, the apparatus being equipped with hydraulically controlled regulating devices adapted to cause the percussion parameters, the speed of impact and the frequency of impact of the piston to vary, characterised in that it consists in modifying, at each impact of the piston (1) on the tool, the fluid flow in a conduit connected to the devices regulating the percussion parameters, relative to the time during which the piston remains close to its theoretical impact zone.

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'onde 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 reflected shock wave, 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. Under 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 électrohydrauli- que. 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.

Le document US-A-3 908 767 concerne un appareil à percussions comportant un distributeur de structure simple et permettant un débit de passage de fluide hydraulique. Cet appareil présente un conduit de commande du mouvement comportant plusieurs orifices débouchant dans le cylindre à l'intérieur duquel se déplace le piston de frappe, la sélection manuelle de ces orifices permettant de contrôler le déplacement du distributeur. Toutefois, ce dispositif ne permet pas un contrôle du mouvement en vue d'une adaptation automatique de la frappe à la dureté du terrain.Document US-A-3,908,767 relates to a percussion device comprising a distributor of simple structure and allowing a flow rate for the passage of hydraulic fluid. This device has a movement control conduit comprising several orifices opening into the cylinder inside which the striking piston moves, the manual selection of these orifices making it possible to control the movement of the distributor. However, this device does not allow movement control for automatic adaptation of the strike 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 puis dans l'autre, cet appareil étant équipé de dispositifs de régulation pilotables hydrauliquement susceptibles de faire varier des paramètres de percussion, la vitesse d'impact et la frequence de frappe du piston, est caractérisé, selon l'invention, en ce qu'il consiste, lors de chaque impact du piston sur l'outil, à modifier, relativement à la durée de séjour du piston à proximité de sa zone théorique de frappe, l'écoulement de fluide dans un canal relié aux dispositifs réglant les 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 then in the other, this device being equipped with hydraulically controllable regulating devices capable of varying percussion parameters, the impact speed and the striking frequency of the piston, is characterized, according to the invention, in that it consists, during each impact of the piston on the tool, to be modified, relative to the duration of stay of the piston near its theoretical striking zone, the flow of fluid in a channel connected to the devices regulating the parameters of percussion.

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 la durée de séjour du piston à proximité de sa zone 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 régùlation 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 period of stay of the piston near its theoretical striking area, to establish a momentary circulation of fluid between the primary circuit and a secondary circuit. The hydraulic information supplied to the regulation devices allows them to adapt the operating parameters to the nature of the soil encountered by the tool.

Des modes préférentiels de realisation de l'invention sont l'objet des revendications depen- dantes.Preferential embodiments of the invention are the subject of the dependent claims.

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 well understood with the aid of the description which follows with reference to the schematic appended 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 (EP-A-0 070 246) 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 shown in Figure 1 relates to a percussion device of the type described in French patent 81 14043 (EP-A-0 070 246) in the name of the Applicant, and comprising a piston (1) sliding in a body (2) comprising a cylinder-shaped cavity, 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 of it. In 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'arête (16) délimitant une extrémité de la gorge (15) est positionnée de telle sorte que, lorsque le piston (1) se trouve à sa zone 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.According 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 edge (16) delimiting one end of the groove (15) is positioned so that, when the piston (1) is at its theoretical striking area, the orifice (80) at which the channel opens ( 12) is completely free 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 rebound speed of the piston (1) is high 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'intérieur 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 in pressure on the one hand in the buffer chamber (51) and on the other hand in the piloting 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 Figure 3 the distributor (30) is piloted by an annular control section (33) which, when under pressure, moves the distributor by putting in communication the channel (31) opening above the piston head with the fluid supply circuit under high pressure.

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 slide valve (35) is to select the active control channel (36-39) which, fed from the annular chamber (32) delimited by a groove (55) of the piston, will pressurize 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) towards the low pressure channel (61). and the low pressure network (50) passing through 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. 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.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. 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 prevailing in the chamber (51) is such that it establishes the equality of the quantity of fluid entering this chamber when the groove (63) places the channel (12) and the channel (79) in communication with the quantity of fluid leaving this chamber when the groove (63) puts the channel (12) and the channel (61) in communication. 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 (51The 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) consisting of 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, la durée 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 duration 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 feed 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 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. A method of controlling the movement of the impacting piston of a non-compressible pressure fluid-actuated percussion apparatus, supplied in a manner such that the resultant of the hydraulic force is applied successively in one direction and then in the other, the apparatus being equipped with hydraulically controlled regulating devices adapted to cause the percussion parameters, the speed of impact and the frequency of impact of the piston to vary, characterised in that it consists in modifying, at each impact of the piston (1) on the tool, the fluid flow in a conduit connected to the devices regulating the percussion parameters, relative to the time during which the piston remains close to its theoretical impact zone.
2. A percussion apparatus for carrying out the method according to Claim 1, of the type including a piston (1) reciprocably movable within a cylinder under the action of the resultant of hydraulic forces and equipped with hydraulically controlled regulating devices (4, 30, 65), adapted to vary the percussion parameters, the speed of impact and the frequency of impact of the piston, characterised in that it has a conduit (12) opening into the interior of the cylinder containing the impacting piston (1), arranged to avoid any interference in the operation of the device ensuring the reciprocating movement of the piston, and communicating with a primary circuit connected to the devices controlling the percussion parameters, whilst a groove (15, 55, 63) formed in the piston enables, at each impact and throughout the time for which the piston remains close to its theoretical impact zone, a momentary fluid circulation to be established between the primary circuit and a secondary circuit, which is at a different pressure to that of the primary circuit.
3. A percussion apparatus according to Claim 2, characterised in that the primary circuit has a buffer chamber (51), one of the walls of which is delimited by a slide valve (17,35,66), the primary circuit being in communication with a volume located to one side of this slide valve, the valve supplying, from fluid injected into the conduit (12), a stable pressure, of which the value depends on the resistance to the penetration of the tool into the ground, and which is used to control the devices regulating the percussion parameters.
4. A percussion apparatus according to Claim 3, characterised in that the secondary circuit is in communication with the high pressure fluid supply circuit and is momentarily connected to the primary circuit when the groove (15, 55) formed in the piston (1) is opposite to the orifice (80) of the conduit (12) opening into the cylinder, and in that the buffer chamber (51), supplied by the said conduit (12), is placed in communication with a chamber (52) located at the other side of the connected slide valve by means of an orifice (19) forming a nozzle, this second chamber, or rear chamber, of the slide valve being connected to the low pressure return circuit (50).
5. A percussion apparatus according to Claim 3, characterised in that the secondary circuit (61) is in communication with the return circuit (50) of the apparatus and is momentarily connected to the primary circuit by means of the groove (63) of the piston (1) when the latter is in contact with the tool, whilst the buffer chamber (51), connected to the aforementioned conduit, is in communication, by means of an orifice (19) forming a nozzle, with the rear chamber (52) of the slide valve (17), which chamber is itself supplied by way of a pressure regulator or nozzle (71) by the high pressure fluid supply of the apparatus.
6. A percussion apparatus according to Claim 3, characterised 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 by means of the groove (63) of the piston when this latter is in the theoretical impact position, whilst the conduit (12), opening into the buffer chamber (51), has a nozzle (14) and is supplied through a flow regulator or nozzle (78) with fluid at the pressure of the supply to the apparatus, whilst the rear chamber (52), located to the side of the slide valve (66) opposite to the buffer chamber, is connected to the low pressure return circuit (50).
7. A percussion apparatus according to Claim 3, characterised in that, in addition to the conduit (12) in communication with the primary circuit, there opens into the cylinder in which the piston (1) moves, on the one hand a conduit (79) having a nozzle (78) and permanently connected to the high pressure supply circuit of the apparatus and, on the other hand a conduit (61) in communication with the low pressure circuit (50) of the apparatus, the two latter conduits (79, 61) being located to either side of the first aforementioned conduit (12) and each arranged at a distance from this latter less than the height of the groove (63) formed in the piston (1), the buffer chamber (51) being in communication with the conduit (12), and the rear chamber (52) located to the opposite side of the slide valve being for its part connected to the low pressure return circuit (50) of the apparatus, the various conduits (79, 12, 61) being arranged such that during the operational cycle, the groove (63) of the piston places the conduit (12) in momentary and alternate communication, on the one hand, with the supply circuit of the apparatus and, on the other hand, with the return circuit thereof when the piston reaches its theoretical impact position.
8. A percussion apparatus according to any one of Claims 2 to 7, characterised in that the fluid pressure is used to control a pressure regulator acting to adjust the supply pressure to the apparatus, such that, when the pressure in the buffer chamber (51) and on the regulator slide valve (4, 65) varies, the regulator controls a variation in the supply pressure, and consequently a variation in the impact speed of the piston.
9. A percussion apparatus according to any one of Claims 3 to 7, characterised in that the slide valve (35) delimiting, in part, the buffer chamber (51), is slidably mounted in a cylinder into which open several axially offset conduits (36-39), which also open into the guiding cylinder of the piston (1), the slide valve having a peripheral groove (40) adapted, as a function of the position of the slide valve, to be placed in communication with one or other of the aforementioned conduits, themselves in communication by means of the groove of the piston with the high pressure supply system, another conduit opening into the cylinder opposite to the annular volume formed by the groove of the slide valve, which remains permanently in communication with this volume, and which is connected to an impact frequency regulation distributor, in such a way that the longer the length of time for which the piston remains at the point of impact, the greater will be the frequency of impact.
10. A percussion apparatus according to one of Claims 8 and 9, characterised in that the pressure prevailing in the primary circuit acts simultaneously to control a pressure regulator acting to adjust the supply pressure of the apparatus and to move the slide valve limiting in part the buffer chamber to adjust the travel of the piston and thus the frequency of impact.
11. A percussion apparatus according to any one of Claims 2 to 10, characterised in that a conduit (22), connected to the low pressure return circuit (50) of the apparatus, opens into the interior of the cylinder containing the slide valve (17, 35, 66) delimiting in part the buffer chamber (51), this conduit normally being blocked by the slide valve and capable of being placed in communication with the buffer chamber (51) when the internal pressure of the latter exceeds a predetermined value.
12. A percussion apparatus according to Claim 2, characterised in that it includes a buffer chamber (51) of which one of the walls is delimited by a slide valve (87) allowing a constant pressure to be created and communicating with a conduit (12) opening into the interior of the cylinder containing the impacting piston, the buffer chamber (51) furthermore communicates with a conduit in which is disposed a component (85) for regulating the fluid flow, constituted by a volumetric pump.
13. A percussion apparatus according to Claim. 12, characterised in that the component for regulating the fluid flow is constituted by a volumetric pump actuated in synchronism with the impacting piston.
14. A percussion apparatus according to any one of Claims .12 and 13, characterised in that the secondary circuit, in communication with the high pressure fluid supply circuit, is momentarily connected to the primary circuit when the groove (55), formed in the piston (1), is opposite to the orifice (80) of the conduit (12) opening into the cylinder, and in that the buffer chamber (51), supplied by said conduit (12), is in communication with the low pressure circuit (50) by means of a fluid discharge conduit (86) in which is mounted the component (85) for regulating the rate of fluid flow.
15. A percussion apparatus according to any one of Claims 12 and 13, characterised in that the secondary circuit, in communication with the low pressure return circuit (50) of the apparatus, is momentarily connected to the primary circuit, by means 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 conduit (12), is supplied with fluid from the low pressure circuit by means of the component (85a) for regulating the fluid flow.
16. A percussion apparatus according to any one of Claims 12 to 15, characterised in the sliding valve (87), delimiting in part the buffer chamber (51), has two coaxial portions, of which that located on the buffer chamber side has a larger cross-section than that of the other portion, the slide valve being slidably mounted in two coaxial bores (82, 20) having cross-sections corresponding to those of the two portions of the slide valve, an annular chamber (84) being formed between the slide valve and the large section bore, in communication with the supply source of fluid under pressure to the apparatus.
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
FR8511346 1985-07-16
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

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

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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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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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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
EP3659752B1 (en) * 2017-07-24 2023-04-19 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
FR3077753B1 (en) 2018-02-14 2020-01-31 Montabert METHOD FOR ADJUSTING THE STRIKING STROKE OF A STRIKING PISTON OF A PERCUSSION APPARATUS, AND A PERCUSSION APPARATUS FOR CARRYING OUT SAID METHOD

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US4899836A (en) 1990-02-13
JPH0698578B2 (en) 1994-12-07
FI862952A0 (en) 1986-07-15
NO167266C (en) 1991-10-23
DE3673100D1 (en) 1990-09-06
ES556161A0 (en) 1987-07-01
ES8706506A1 (en) 1987-07-01
AU6018286A (en) 1987-01-22
NO862855L (en) 1987-01-19
EP0214064A1 (en) 1987-03-11
CA1288317C (en) 1991-09-03
NO167266B (en) 1991-07-15
DE214064T1 (en) 1987-07-02
FI862952A (en) 1987-01-17
FI86762B (en) 1992-06-30
NO862855D0 (en) 1986-07-15
FR2595972B2 (en) 1989-10-20
FR2595972A2 (en) 1987-09-25
JPS6219386A (en) 1987-01-28
AU592357B2 (en) 1990-01-11
FI86762C (en) 1992-10-12

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