EP0214064B1 - Verfahren und Vorrichtung zum Steuern der Bewegung des Schlagkolbens einer von einem nichtzusammendrückbaren Fluidum angetriebenen Schlagvorrichtung - Google Patents

Verfahren und Vorrichtung zum Steuern der Bewegung des Schlagkolbens einer von einem nichtzusammendrückbaren Fluidum angetriebenen Schlagvorrichtung 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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Prior art keywords
piston
conduit
pressure
chamber
communication
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EP86420181A
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English (en)
French (fr)
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EP0214064A1 (de
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/fr
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Priority to AT86420181T priority Critical patent/ATE55080T1/de
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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)
  • Fluid-Pressure Circuits (AREA)

Claims (16)

1. Verfahren zum Steuern der Bewegung des Schlagkolbens einer Schlagvorrichtung, die durch ein unter Druck stehendes inkompressibles Fluid angetrieben wird, das derart zugeführt wird, daß die Resultierende der hydraulischen Kräfte aufeinanderfolgend in einer Richtung und dann in die andere Richtung wirksam ist, wobei die Vorrichtung mit hydraulisch steuerbaren Regulierungsvorrichtungen zum Verändern der Schlagparameter, der Schlaggeschwindigkeit und der Schlagfrequenz des Kolbens ausgestattet ist, dadurch gekennzeichnet, daß man bei jedem Schlag des Kolbens (1) auf das Werkzeug in Abhängigkeit der Verweildauer des Kolbens in der Nähe seiner theoretischen Schlagzone den Fluß des Fluids mit einem mit den Reguliervorrichtungen (4, 30, 65) für die Schlagparameter verbundenen Kanal verändert.
2. Schlagvorrichtung zum Durchführen des Verfahrens nach Anspruch 1, mit einem im Inneren eines Zylinders unter der Wirkung der Resultierenden der hydraulischen Kräfte hin und her bewegbaren Kolben (1) und mit hydraulisch steuerbaren Reguliervorrichtungen (4, 30, 65) zum Verändern der Schlagparameter, der Schlaggeschwindigkeit und der Schlagfrequenz des Kolbens, dadurch gekennzeichnet, daß es einen in das Innere des den Schlagkolben (1) enthaltenden Zylinders mündenden, zur Vermeidung jeder funktionalen Interferenz mit der die abwechselnde Bewegung des Kolbens gewährleistenden Vorrichtung vorgesehenen und mit einem Primärkreis, der mit den Steuervorrichtungen der Schlagparameter verbunden ist, kommunizierenden Kanal (12) enthält, während eine am Kolben angeordnete Vertiefung (15, 55, 63) bei jedem Schlag und während der Verweildauer des Kolbens in der Nähe seiner theoretischen Schlagzone das Herstellen einer augenblicklichen Zirkulation des Fluids zwischen dem Primärkreis und einem Sekundärkreis ermöglicht, der einen gegenüber dem Primärkreis unterschiedlichen Druck aufweist.
3. Schlagvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Primärkreis eine Dämpfungskammer (51) enthält, bei der eine der Wände von einem verschiebbaren Schieber (17, 35, 66) gebildet wird, wobei der Primärkreis mit einem an einer Seite des Schiebers befindlichen Volumen in Verbindung steht und wobei der Schieber ausgehend vom eingebrachten Fluid im Kanal (12) einen stabilisierten Druck erzeugt, dessen Wert vom Widerstand beim Eindringen des Werkzeugs in das Terrain abhängt und der zum Steuern der Reguliervorrichtungen der Schlagparameter verwendet wird.
4. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der Sekundärkreis mit dem unter Hochdruck stehenden Fluidversorgungskreis in Verbindung steht und augenblicklich mit dem Primärkreis verbunden ist, wenn die im Kolben (1) ausgebildete Vertiefung (15, 55) sich der in den Zylinder mündenden Öffnung (80) des Kanals (12) gegenüber befindet, und daß die durch den Kanal (12) versorgte Dämpfungskammer (51) mit einer an der anderen Seite des zugehörigen Schiebers angeordneten Kammer (52) über eine eine Düse bildende Öffnung (19) in Verbindung steht, wobei die zweite Kammer oder hinter dem Schieber befindliche Kammer mit dem Niederdruck des Rückkreises (50) verbunden ist.
5. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der Sekundärkreis (61) mit dem Rückkreis (50) der Vorrichtung in Verbindung steht und über die Vertiefung (63) des Kolbens (1) augenblicklich mit dem Primärkreis verbunden ist, wenn der Kolben das Werkzeug berührt, während die mit dem vorgenannten Kanal verbundene Dämpfungskammer (51) über eine eine Düse bildende Öffnung (19) mit der hinter dem Schieber (17) befindlichen Kammer (52) in Verbindung steht, die selbst über einen Druckregler oder eine Düse (71) vom unter Hochdruck stehenden Versorgungsfluid des Gerätes gespeist wird.
6. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der Sekundärkreis (61) mit dem Rückkreis (50) der Vorrichtung in Verbindung steht und über die Vertiefung (63) des Kolbens augenblicklich mit dem Primärkreis verbunden ist, wenn sich der Kolben in der theoretischen Schlagposition befindet, während der in die Dämpfungskammer (51) mündende Kanal (12) eine Düse (14) enthält und über einen Mengenregler oder eine Düse (78) mit dem unter dem Versorgungsdruck der Vorrichtung stehenden Fluid versorgt wird, wenn die hintere Kammer (52), die an der der Dämpfungskammer entgegengesetzten Seite des Schiebers (66) angeordnet ist, mit dem Niederdruck-Rückkreis (50) verbunden ist.
7. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß in den Zylinder, in dem sich der Kolben (1) verschiebt, außer dem mit dem Primärkreis verbundenen Kanal (12) zum einen ein eine Düse (78) enthaltender und dauernd mit dem Hochdruck-Versorgungskreis der Vorrichtung verbundener Kanal (79) und zum anderen mit dem Niederdruckkreis (50) der Vorrichtung in Verbindung stehender Kanal (61) münden, wobei die beiden letzteren Kanäle (79, 61) beiderseits des erstgenannten Kanals (12) angeordnet sind und sich jeweils in einem Abstand von diesem befinden, der kleiner als die Höhe der am Kolben (1) ausgebildeten Vertiefung (63) ist, wobei die Dämpfungskammer (51) mit dem Kanal (12) in Verbindung seht und die hintere Kammer (52), die an der entgegengesetzten Seite des Schiebers angeordnet ist, ihrerseits mit dem Niederdruck-Rückkreis (50) der Vorrichtung verbunden ist, und wobei die verschiedenen Kanäle (79, 12, 61) derart angeordnet sind, daß während des Betriebszyklus die Vertiefung (63) des Kolbens den Kanal (12) momentan und abwechselnd zum einen mit dem Versorgungskreis der Vorrichtung und zum anderen mit dem Rückkreis der Vorrichtung verbindet, während der Kolben in seiner theoretischen Schlagposition ankommt.
8. Schlagvorrichtung nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, daß der Fluiddruck zum Steuern eines Druckreglers verwendet wird, der zum Einstellen des Versorgungsdrucks der Vorrichtung dient, derart, daß bei einer Veränderung des Drucks in der Dämpfungskammer (51) und am Schieber (4, 65) des Reglers der Regler eine Variation des Versorgungsdrucks und somit eine Variation der Schlaggeschwindigkeit des Kolbens steuert.
9. Vorrichtung nach einem der Ansprüche 3 bis 7, dadurch gekennzeichnet, daß der die Dämpfungskammer (51) zum Teil begrenzende Schieber (35) in einem Zylinder geführt angeordnet ist, in den mehrere axial versetzte Kanäle (36-39) münden, die in gleicher Weise in den Führungszylinder des Kolbens (1) münden, wobei der Schieber eine Umfangsvertiefung aufweist, die in Abhängigkeit von der Schieberposition mit dem einen oder dem anderen der vorgenannten Kanäle in Verbindung gebracht werden kann, die ihrerseits über die Vertiefung des Kolbens mit dem Hochdruck-Versorgungsnetz verbunden sind, und wobei ein anderer Kanal an einer dem durch die Kolbenvertiefung gebildeten Ringvolumen gegenüberliegenden Stelle in den Zylinder mündet, der andauernd mit diesem Volumen verbunden bleibt und der mit einem Verteiler zum Regulieren der Schlagfrequenz verbunden ist, derart, daß mit zunehmender Verweildauer des Kolbens im Schlagpunkt die Schlagfrequenz höher wird.
10. Schlagvorrichtung nach Anspruch 8 oder 9, dadurch gekennzeichnet, daß der im Primärkreis herrschende Druck gleichzeitig zum Steuern eines Druckreglers, der zum Einstellen des Versorgungsdrucks der Vorrichtung dient, und, um den Kolbenhub und somit die Schlagfrequenz einzustellen, zum Verschieben des die Dämpfungskammer zum Teil begrenzenden Schiebers dient.
11. Schlagvorrichtung nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, daß in das Innere des den teilweise die Dämpfungskammer (51) begrenzenden Schiebers. (17, 35, 66) enthaltenden Zylinders ein mit dem Niederdruck-Rückkreis (50) der Vorrichtung verbundener Kanal (22) mündet, der normalerweise durch den Schieber verschlossen ist und mit der Dämpfungskammer (51) in Verbindung gebracht werden kann, wenn der Druck in der Dämpfungskammer einen vorbestimmten Wert übersteigt.
12. Schlagvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß sie eine Dämpfungskammer (51) enthält, bei der eine der Wände durch einen bewegbaren, die Erzeugung eines konstanten Druckes ermöglichenden und mit einem Kanal (12), der in das Innere des den Schlagkolben enthaltenden Zylinders mündet, in Verbindung stehenden Schieber (51) begrenzt ist, wobei die Dämpfungskammer (51) außerdem mit einem Kanal verbunden ist, in dem ein Organ (85) zur Regulierung der Fluidmenge angeordnet ist, das von einer volumetrischen Pumpe gebildet wird.
13. Schlagvorrichtung nach Anspruch 12, dadurch gekennzeichnet, daß das Organ zur Regulierung der Fluidmenge von einer volumetrischen Pumpe gebildet wird, die synchron zum Schlagkolben betrieben wird.
14. Schlagvorrichtung nach Anspruch 13 oder 14, dadurch gekennzeichnet, daß der mit dem unter Hochdruck stehenden Fluidversorgungskreis verbundene Sekundärkreis augenblicklich mit dem Primärkreis verbunden ist, wenn die im Kolben (1) ausgebildete Vertiefung (55) sich der Öffnung (80) des in den Zylinder mündenden Kanals (12) gegenüber befindet, und daß die durch diesen Kanal (12) versorgte Dämpfungskammer (51) mit dem Niederdruckkreis (50) über einen Fluidentleerungskanal (86) verbunden ist, in dem das Organ (85) zum Regulieren der Fluidmenge angeordnet ist.
15. Schlagvorrichtung nach Anspruch 12 oder 13, dadurch gekennzeichnet, daß der mit dem Niederdruck-Rückkreis (50) der Vorrichtung verbundene Sekundärkreis über die Vertiefung (63) des Kolbens (1) augenblicklich mit dem Primärkreis verbunden ist, wenn der Kolben (1) in Berührung mit dem Werkzeug steht, und daß die mit dem Kanal (12) verbundene Dämpfungskammer (51) ausgehend vom Niederdruckkreis über das Organ (85a) zum Regulieren der Fluidmenge mit Fluid versorgt wird.
16. Schlagvorrichtung nach einem der Ansprüche 12 bis 15, dadurch gekennzeichnet, daß der die Dämpfungskammer (51) teilweise begrenzende verschiebbare Schieber (87) zwei koaxiale Partien enthält, von denen die der Dämpfungskammer zugewandte Partie einen größeren Querschnitt als die andere Partie aufweist, wobei der Schieber in zwei koaxialen Bohrungen (82, 20) mit den Querschnitten der beiden Schieberpartien entsprechenden Querschnitten geführt angeordnet ist und wobei zwischen dem Schieber und der Bohrung größeren Querschnitts eine Ringkammer (84) vorhanden ist, die mit der Hochdruck-Fluidversorgungsquelle verbunden ist.
EP86420181A 1985-07-16 1986-07-07 Verfahren und Vorrichtung zum Steuern der Bewegung des Schlagkolbens einer von einem nichtzusammendrückbaren Fluidum angetriebenen Schlagvorrichtung Expired - Lifetime EP0214064B1 (de)

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AT86420181T ATE55080T1 (de) 1985-07-16 1986-07-07 Verfahren und vorrichtung zum steuern der bewegung des schlagkolbens einer von einem nichtzusammendrueckbaren fluidum angetriebenen schlagvorrichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8511346 1985-07-16
FR8511346A FR2584968B1 (fr) 1985-07-16 1985-07-16 Procede de commande du mouvement du piston de frappe d'un appareil a percussions mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre du procede
FR8604302 1986-03-18
FR868604302A FR2595972B2 (fr) 1985-07-16 1986-03-18 Appareil a percussions

Publications (2)

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

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EP (1) EP0214064B1 (de)
JP (1) JPH0698578B2 (de)
AU (1) AU592357B2 (de)
CA (1) CA1288317C (de)
DE (2) DE3673100D1 (de)
ES (1) ES8706506A1 (de)
FI (1) FI86762C (de)
FR (1) FR2595972B2 (de)
NO (1) NO167266C (de)

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FR2727891B1 (fr) 1994-12-08 1997-01-24 Montabert Ets Procede et appareil pour la regulation de la course de frappe d'un appareil a percussion mu par un fluide incompressible sous pression
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FI104960B (fi) * 1995-07-06 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
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SE528745C2 (sv) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Ventilanordning för slagverk och slagverk för bergborrmaskin
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FR2902684B1 (fr) * 2006-06-27 2010-02-26 Montabert Roger Procede de commutation de la course de frappe d'un appareil a percussions mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procede
SE530885C2 (sv) * 2007-02-23 2008-10-07 Atlas Copco Rock Drills Ab Förfarande vid slagverk, slagverk och bergborrmaskin
FR2916377B1 (fr) * 2007-05-25 2009-07-24 Montabert Soc Par Actions Simp Procede de protection contre les suralimentations en debit d'un appareil a percussions mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procede.
FI123634B (fi) * 2007-10-05 2013-08-30 Sandvik Mining & Constr Oy Kallionrikkomislaite, suojaventtiili sekä menetelmä kallionrikkomislaitteen käyttämiseksi
CN101927479B (zh) * 2009-06-23 2014-10-22 蒙塔博特公司 液压冲击设备
CA2810914A1 (en) * 2010-09-10 2012-03-15 Rockdrill Services Australia Pty Ltd Improved rock drill
FR2983760B1 (fr) 2011-12-09 2014-08-15 Montabert Roger Procede de commutation de la course de frappe d'un piston de frappe d’un appareil a percussions
US9701003B2 (en) * 2014-05-23 2017-07-11 Caterpillar Inc. Hydraulic hammer having delayed automatic shutoff
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Also Published As

Publication number Publication date
ES556161A0 (es) 1987-07-01
NO862855D0 (no) 1986-07-15
JPS6219386A (ja) 1987-01-28
DE214064T1 (de) 1987-07-02
DE3673100D1 (de) 1990-09-06
NO862855L (no) 1987-01-19
AU592357B2 (en) 1990-01-11
FI862952A0 (fi) 1986-07-15
FR2595972B2 (fr) 1989-10-20
FI86762C (fi) 1992-10-12
NO167266B (no) 1991-07-15
FI86762B (fi) 1992-06-30
FR2595972A2 (fr) 1987-09-25
JPH0698578B2 (ja) 1994-12-07
NO167266C (no) 1991-10-23
ES8706506A1 (es) 1987-07-01
CA1288317C (fr) 1991-09-03
US4899836A (en) 1990-02-13
FI862952A (fi) 1987-01-17
EP0214064A1 (de) 1987-03-11
AU6018286A (en) 1987-01-22

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