EP0256955B1 - Verfahren und Vorrichtung zum Einstellen der Schlagparameter des Schlagkolbens einer von einem nicht zusammendrückbaren Fluid angetriebenen Vorrichtung - Google Patents

Verfahren und Vorrichtung zum Einstellen der Schlagparameter des Schlagkolbens einer von einem nicht zusammendrückbaren Fluid angetriebenen Vorrichtung Download PDF

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Publication number
EP0256955B1
EP0256955B1 EP87420203A EP87420203A EP0256955B1 EP 0256955 B1 EP0256955 B1 EP 0256955B1 EP 87420203 A EP87420203 A EP 87420203A EP 87420203 A EP87420203 A EP 87420203A EP 0256955 B1 EP0256955 B1 EP 0256955B1
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EP
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Prior art keywords
chamber
pressure
piston
valve
fluid
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Expired - Lifetime
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EP87420203A
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English (en)
French (fr)
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EP0256955A1 (de
Inventor
Jean Sylvain Comarmond
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Montabert SAS
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Montabert SAS
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Priority to AT87420203T priority Critical patent/ATE58082T1/de
Publication of EP0256955A1 publication Critical patent/EP0256955A1/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
    • B25D9/14—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator

Definitions

  • the subject of the present invention is a method for regulating the percussion parameters of the striking piston of an apparatus driven by an incompressible fluid under pressure, and an apparatus for implementing this method.
  • Percussion devices driven by an incompressible fluid under pressure are supplied with fluid, so that the result of the hydraulic forces applied successively on the striking piston, displaces the latter alternately in one direction then in the other.
  • This apparatus comprises a striking piston mounted to slide in a body comprising a cylinder-shaped cavity, in which is concentrically mounted a distributor ensuring a controlled supply of fluid under pressure so that the result of the forces is applied successively to the piston to move it one way and then the other.
  • devices of this type must be adjusted according to the hardness of the ground encountered by the tool.
  • the piston moves inside a bore or cylinder in which is provided, above the piston, a chamber which, delimited in part by the latter, is conventionally called: upper room.
  • a chamber which, delimited in part by the latter, is conventionally called: upper room.
  • this chamber is supplied with pressurized fluid, the hydraulic force which is created there allows the piston to describe its stroke.
  • a second chamber is formed, also partially delimited by the piston, conventionally called: lower chamber.
  • the striking piston can, in the instant following the impact against the tool, rebound more or less depending on the hardness of the ground. If the piston rebounds on the tool just after impact, the speed of the piston can be such that it generates a momentary overpressure in the upper chamber and a momentary decrease in pressure in the lower chamber.
  • the first consists in equipping the device with a regulator making it possible to adjust the supply pressure of pressurized fluid, which modifies the speed of impact.
  • Another solution consists in equipping the apparatus with a hydraulically actuated distributor, making it possible to modify the striking stroke, and consequently, the displacement and the impact speed of the piston.
  • the impact parameters such as impact speed and striking frequency, are at most manually adjustable using complex devices, but in no case do they allow automatic adaptation of the impact speed to the nature of the terrain in which the tool operates.
  • the present invention aims to remedy these drawbacks.
  • the regulation process which it relates to, intended for a percussion device driven by an incompressible fluid under pressure, comprising two upper and lower chambers formed in the cylinder in which the piston moves and equipped with devices for controlling the parameters of percussion, impact speed and striking frequency, allowing adjustment according to the hardness of the ground in which the device must work, is characterized in that it consists in measuring, at least during the possible rebound time of the impact piston on the tool, the pressure in the upper chamber, in the lower chamber or in a chamber connected to one of them, to compare this pressure to a reference pressure, then according to this comparison , to regulate the flow of fluid in a channel connected to the device for controlling the percussion parameters.
  • An apparatus for implementing this process of the type comprising a piston which can be moved alternately inside the cylinder, with which it delimits an upper chamber and a lower chamber, under the action of the resultant of hydraulic forces exerted successively in the upper and lower chambers, and equipped with hydraulically controllable devices capable of varying percussion parameters, impact speed and striking frequency, is characterized in that it comprises a channel opening directly into the upper chamber, or into the lower chamber, or in a chamber in communication with one of them at the time of impact, connected via a hydraulic element to means for controlling the device for controlling the percussion parameters.
  • the device represented in FIG. 1 is a percussion device of the type described in the request. of French patent 81.14043 (FR-A 2 509 217) or its European correspondent 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 is concentrically mounted a distributor 3.
  • This device is equipped with a regulator making it possible to adjust the supply pressure of the device and, consequently, the speed of impact of the piston.
  • this regulator comprises a drawer 4 in equilibrium under the force of a spring 5 and under the pressure of the supply fluid, brought by a channel 6 and a nozzle 7, acting in the chamber 8 at the end of the drawer .
  • a chamber 9 for piloting the drawer is located so as to act in an antagonistic manner to the effect of the pressure in the chamber 8.
  • the drawer 4 delimits with the walls of the cavity in which it is mounted, a throttled passage forming a nozzle 10 ensuring the passage of the fluid discharged through the channel 11 by the piston, during the return stroke thereof.
  • the back pressure created by the nozzle 10 is such that the supply pressure acting in the chamber 8 rises to the value necessary to compensate for the action of the spring 5, and this in the absence of pressure in the chamber 9.
  • a channel 12 opens into a chamber 13 called “upper chamber”, formed inside the cylinder in which the piston 1 moves, and partly delimited by it.
  • a sequence valve 14 ensuring the comparison between the pressure of the fluid contained in the upper chamber 13 and the pressure of the supply fluid under high pressure, the pressurized feed fluid being supplied from the channel 31 to the sequence valve through a channel 17.
  • This sequence valve allows the passage of fluid in a channel 15, when the pressure in the upper chamber is greater than the supply pressure of the device.
  • This sequence valve 14 is connected via a channel 15 to a device comprising a slide 16 mounted to slide in a bore 18 delimiting on one side a chamber 19 called “buffer chamber” into which the channel 15 opens and the other side a chamber 20, connected to the low pressure circuit 22 via a channel 23.
  • the chamber 20 also contains a spring tending to move the slide in a direction of reduction of the volume of the buffer chamber 19.
  • the chambers 19 and 20 are in communication with each other by means of a nozzle 25.
  • the buffer chamber 19 is also connected to the piloting chamber 9 of the pressure regulator by a channel 24.
  • the communication between the buffer chamber 19 and the low pressure circuit 22 by the nozzle 25 and the chamber 20 allows, under these conditions, the pressure of the chamber 19 to remain low.
  • the rebound speed of the piston on the latter is high, which generates, in the upper chamber 13, a pressure higher than the supply pressure of the device, due to the sudden discharge of fluid through the channels normally used to supply the upper chamber during the stroke.
  • the overpressure in the channel 12 actuates the sequence valve 14 which injects, into the buffer chamber 19 and through a nozzle 26 mounted on the channel 15, a certain quantity of fluid increasing the pressure in the chamber 19 and in the piloting chamber 9 of the regulator.
  • the slide valve 4 of the regulator tends to further throttle the nozzle 10, which results in an increase in the operating pressure of the device and in an increase in the speed of impact of the piston.
  • the slide 16 is in equilibrium for a pressure in the buffer chamber 19 such that the flow of fluid that this pressure allows to pass through the nozzle 25 is equal to the flow injected through the nozzle 26 by the valve of sequence 14.
  • the upper chamber 13 is connected either to the supply channel 31 or to the low pressure channel 22.
  • the control chamber 29 of the distributor 28 is supplied with pressurized fluid through a channel 32 opening into an annular recess delimited by a groove 33 of a drawer 34 slidably mounted in a bore 35.
  • the groove 33 is susceptible, depending on the position of the drawer 34, to put the chamber 29 in communication via the channel 32 with one or more of a series of channels 36-39 opening into the cylinder in which the piston moves.
  • the function of the drawer 34 is to select the active control channel 36-39 which, supplied from the lower chamber 40, will pressurize the control section 29.
  • the supply of pressurized fluid to the upper chamber intervenes more or less early in the piston operating cycle, varying the stroke, the striking frequency and the impact speed of the piston.
  • the control of the position of the drawer 34 is obtained, as in the previous embodiment, by means of a channel 12 opening into the upper chamber 13 and of a valve. sequence 14 which supplies the buffer chamber 19 with fluid delimited in part by the drawer 34.
  • the rebound is zero as well as the amount of fluid injected into the buffer chamber 19, which allows the drawer 34, pushed by the spring 21, to select a channel 36-39 corresponding to a striking stroke. lower and a decrease in impact speed.
  • FIG. 3 represents a variant of the apparatus of FIG. 2 in which the channel 12 is equipped with a non-return valve 43 allowing the passage of fluid only from the chamber 13 towards the chamber 19, and in which the chamber 20 , located on the other side of the drawer 34 relative to the chamber 19, is in communication via a channel 17 with the source of pressurized fluid.
  • the non-return valve 43 When the pressure in the chamber 13 is higher than the supply pressure, a certain quantity of fluid can flow through the channel 12, the non-return valve 43 and the channel 15 in the buffer chamber 19.
  • the non-return valve return avoids a flow of fluid from the chamber 19 to the upper chamber when the latter is connected by the distributor 28 to the low pressure channel 22 during the return stroke of the piston.
  • the slide valve 34 is in equilibrium for a pressure in the buffer chamber 19 such that the flow rate which this pressure allows to pass during each cycle in the nozzle 25 is equal to the pulsed flow rate coming from the upper chamber 13 through the nozzle 26.
  • FIG. 4 represents a variant of the apparatus of FIG. 2 in which the channel 12 no longer opens into the upper chamber 13, but into the lower chamber 40.
  • this channel 12 is arranged a sequence valve which, when the pressure at the interior of the lower chamber 40, becomes lower than the pressure for supplying pressurized fluid supplied to the valve through the channel 17, makes it possible to inject into the buffer chamber 19 through the nozzle 26 a certain quantity of fluid supplied through channel 17.
  • the apparatus advantageously comprises, on the channel 47 for supplying the lower chamber 40 with pressurized fluid, a non-return valve 45 allowing free passage of the reflux fluid from the chamber 40 to the channel d 'supply 31.
  • a nozzle 46 mounted on a bypass channel 48, makes it possible to supply the chamber 40 with pressurized fluid to obtain the ascent of the piston 1.
  • the slide valve 34 is in equilibrium for a pressure in the chamber 19 such that the flow rate which this pressure passes through the nozzle 25 is equal to the pulsed flow rate injected by the sequence valve 44 into the buffer chamber 19.
  • the sequence valve 44 injects fluid at the supply pressure into the chamber 19, which increases the pressure inside the latter, and causes the slide to move. against the action of spring 21.
  • the slide 34 discovers control channels 36 to 39 supplying the distributor 28 in a direction of increase in the stroke and the impact speed of the impact piston.
  • the rebound is zero as well as the amount of fluid to be injected into the buffer chamber, which allows the drawer 34 to occupy a position selecting a channel 36 to 39 corresponding to a lower striking stroke.
  • This element 53 relates the high pressure supply channel 31 to the lower chamber 40 when the pressure of the chamber 40 drops below a predetermined value or when the difference between the supply pressure and the pressure of the chamber 40 exceeds a predetermined value.
  • This element 53 therefore makes it possible to maintain a minimum pressure in the chamber 40 avoiding any cavitation in the latter.
  • FIG. 6 represents another variant of this device in which the channel 12 always opens into the lower chamber 40.
  • This channel 12 is equipped with a non-return valve 49 oriented so as to make the passage of fluid from the chamber 40 impossible. towards chamber 19 and allowing only reverse circulation.
  • the chamber 20, located on the other side of the drawer 34, is connected to the duct 31 for supplying fluid under high pressure by a channel 17.
  • the slide valve 34 is in equilibrium for a pressure in the buffer chamber 19, such that the flow rate coming from the chamber 20 via the nozzle 25 is equal to the pulsed flow rate which this pressure allows to evacuate into the chamber 40 through the nozzle 26 and the non-return valve 49.
  • the invention brings a great improvement to the existing technique by providing a method and a device of simple design ensuring an automatic adjustment of the impact parameters to the hardness of the ground in which the tool works.
  • the measurement of the momentary pressure variation following the rebound of the piston on the tool could be carried out by a pressure tap not in the upper chamber or in the lower chamber, as indicated above, but in a chamber communicating with one or the other of these, at the moment of impact and rebound of the piston on the tool.

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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)
  • Fluid-Pressure Circuits (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Fluid-Damping Devices (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Earth Drilling (AREA)
  • Consolidation Of Soil By Introduction Of Solidifying Substances Into Soil (AREA)

Claims (11)

1. Verfahren zum Einstellen der Schlagparameter einer von einem inkompressiblen, unter Druck stehenden Fluid angetriebenen Schlagvorrichtung, mit einer oberen und einer unteren Kammer, die in dem Zylinder angeordnet sind, in dem sich der Kolben verschiebt, und mit Steuereinrichtungen für die Schlagparameter, Aufprallgeschwindigkeit und Schlagfrequenz, die eine Einstellung in Abhängigkeit der Härte des Terrains gestatten, in dem die Vorrichtung arbeiten soll, dadurch gekennzeichnet, dass es darin besteht, wenigstens während der Dauer eines einstellbaren Abprallens des Schlagkolbens auf dem Werkzeug den Druck in der oberen Kammer, in der unteren Kammer oder in einer mit einer derselben verbundenen Kammer zu messen, diesen Druck mit einem Referenzdruck zu vergleichen und dann in Abhängigkeit dieses Vergleichs die Fluidströmung in einem Kanal einzustellen, der mit der Steuereinrichtung für die Schlagparameter verbunden ist.
2. Vorrichtung zur Durchführung des Verfahrens nach Anspruch 1, mit einem Kolben (1), der im Inneren des Zylinders, mit dem er eine obere Kammer (13) und eine untere Kammer (40) abgrenzt, unter der Wirkung der Resultierenden von hydraulischen, nacheinander in der oberen und unteren Kammer ausgeübten Kräften hin- und herverschiebbar ist, und mit hydraulisch steuerbaren Vorrichtung zum Verändern der Schlagparameter, Aufprallgeschwindigkeit und Schlagfrequenz, dadurch gekennzeichnet, dass ein direkt in der oberen Kammer (13) oder in der unteren Kammer (40) oder auch noch in einer zum Zeitpunkt des Aufpralls und des Abprallens des Kolbens mit einer dieser Kammern in Verbindung stehenden Kammer mündender Kanal (12) vorgesehen ist, der mittels eines hydraulischen Elements (14, 43, 44, 49) zum Vergleich des Drucks mit einem Referenzdruck mit Steuerungsmitteln der Steuereinrichtung für die Schlagparameter verbunden ist.
3. Schlagvorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die Steuerungsmittel der Steuereinrichtung für die Schlagparameter eine Dämpfungskammer (19) aufweisen, wobei eine der Wände der Dämpfungskammern von einem verschiebbaren Schieber (16, 34) gebildet wird, der ausgehend vom eingebrachten Fluid im Kanal (12) das Herstellen eines stabilisierten Drucks ermöglicht, dessen Wert vom Widerstand des Werkzeugs in dem Terrain abhängt und er zum Steuern der Steuereinrichtungen für die Schlagparameter verwendet wird.
4. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass ein einerseits in der oberen Kammer (13) und andererseits in der Dämpfungskammer (19) mündender Kanal (12) vorgesehen ist, in dem ein Reihenventil angeordnet ist, das die Versorgung der Dämpfungskammer mit Fluid ausgehend von der Druckversorgung der Vorrichtung gewährleistet; wenn der Druck im Inneren der oberen Kammer höher als der Versorgungsdruck der Vorrichtung ist, und dass die Dämpfungskammer (19) mit der Steuerkammer (9) eines Druckreglers und mittels einer kalibrierten und eine Düse bildenden Öffnung (25) mit einer Kammer (20) in Verbindung steht, die auf der anderen Seite des Schiebers (16) angeordnet und mit dem Niederdruckkreis der Vorrichtung verbunden ist.
5. Schlagvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der die Dämpfungskammer (19) zum Teil begrenzende Schieber (34) 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 (34) eine Umfangsvertiefung (33) aufweist, die in Abhängigkeit von der Schieberposition mit dem einen oder dem anderen der vorgenannten Kanäle (36-39) in Verbindung gebracht werden kann, die ihrerseits über eine Vertiefung im Schlagkolben mit dem Hochdruck-Versorgungsnetz verbunden sind, und wobei ein anderer Kanal (32) an einer dem durch die Vertiefung (33) des Schiebers (34) gebildeten Ringvolumen gegenüberliegenden Stelle in der Bohrung (35) mündet, der andauernd mit diesem Volumen verbunden bleibt und der mit einem Hauptverteiler (28) der Vorrichtung verbunden ist.
6. Schlagvorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Kanal (12) in der oberen Kammer (13) mündet und mit einem Reihenventil (14) versehen ist, wodurch mittels einer kalibrierten Öffnung nach Art einer Düse (26) die fluidische Druckversorgung der Vorrichtung sichergestellt wird, wenn der Druck in der oberen Kammer höher als der Versorgungsdruck ist, und dass die an der anderen Seite des Schiebers (34) angeordnete und mit der Kammer (19) über eine kalibrierte Öffnung nach Art einer Düse (25) in Verbindung stehende Kammer (20) an das Niederdruck-Versorgungsnetz (22) angeschlossen ist.
7. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Kanal (12) in der oberen Kammer (13) mündet und mit einem Rückschlagventil (43) versehen ist, wodurch der Durchfluss von Fluid nur von der oberen Kammer (13) zur Dämpfungskammer (19) über eine kalibrierte Öffnung nach Art einer Düse (26) gestattet wird, und dass die an der anderen Seite des Schiebers (34) angeordnete und mit der der Dämpfungskammer (19) über eine kalibrierte, düssenförmige Öffnung (25) in Verbindung stehende Kammer (20) an den Druckversorgungskreis (31) der Vorrichtung angeschlossen ist.
8. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Kanal (12) in der unteren Kammer (40) mündet und mit einem Reihenventil (44) versehen ist, wodurch mittels einer kalibrierten Offnung nach Art einer Düse (26) die Versorgung der Dämpfungskammer (19) mit Fluid ausgehend von der Druckversorgung der Vorrichtung gestattet wird, wenn der Druck in der Kammer (40) niedriger als der Versorgungsdruck ist, und dass die an der anderen Seite des Schreibers (34) angeordnete Kammer (20) an den Niederdruckkreis (22) der Vorrichtung angeschlossen ist.
9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass der Kanal (47) zur fluidischen Druckversorgung der unteren Kammer zwei zueinander parallele Kanäle aufweist, von denen der eine (48) mit einer die fluidische Druckversorgung der Kammer gestattenden Düse (46) und der andere mit einem Rückschlagventil (45) versehen ist, das den Durchfluss von Fluid von der unteren Kammer (40) zum fluidischen Druckversorgungskanal (31) erlaubt.
10. Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass ein hydraulisches Element (53) nach Art eines mit einer Feder versehen Rückschlagventils oder eines Reihenventils vorgesehen ist, das parallel zum Rückschlagventil (45) und zur Düse (46) angeordnet ist und den fluidischen Versorgungskanal (31) mit der unteren Kammer (40) in Verbindung setzt, wenn der Druck in dieser letzter unter einen vorbestimmten Wert fällt oder wenn die Differenz zwischen dem Versorgungsdruck und dem Druck in der unteren Kammer (40) einen vorbestimmten Wert übersteigt.
11. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Kanal (12) in der unteren Kammer (40) mündet und mit einem Rückschlagventil (49) versehen ist, wodurch mittels einer kalibrierten Öffnung nach Art einer Düse (26) der Durchfluss von Fluid von der Dämpfungskammer (19) zur unteren Kammer (40) gestattet wird, und dass die an der anderen Seite des Schiebers (34) angeordnete und mit der Dämpfungskammer (19) über eine kalibrierte, düsenförmige Öffnung (26) in Verbindung stehende Kammer (20) an das fluidische Druckversorgungsnetz angeschlossen ist.
EP87420203A 1986-08-07 1987-07-27 Verfahren und Vorrichtung zum Einstellen der Schlagparameter des Schlagkolbens einer von einem nicht zusammendrückbaren Fluid angetriebenen Vorrichtung Expired - Lifetime EP0256955B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87420203T ATE58082T1 (de) 1986-08-07 1987-07-27 Verfahren und vorrichtung zum einstellen der schlagparameter des schlagkolbens einer von einem nicht zusammendrueckbaren fluid angetriebenen vorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8611710A FR2602448B1 (fr) 1986-08-07 1986-08-07 Procede de regulation des parametres de percussion du piston de frappe d'un appareil mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procede
FR8611710 1986-08-07

Publications (2)

Publication Number Publication Date
EP0256955A1 EP0256955A1 (de) 1988-02-24
EP0256955B1 true EP0256955B1 (de) 1990-11-07

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EP87420203A Expired - Lifetime EP0256955B1 (de) 1986-08-07 1987-07-27 Verfahren und Vorrichtung zum Einstellen der Schlagparameter des Schlagkolbens einer von einem nicht zusammendrückbaren Fluid angetriebenen Vorrichtung

Country Status (12)

Country Link
US (1) US4800797A (de)
EP (1) EP0256955B1 (de)
JP (1) JPS63174884A (de)
AT (1) ATE58082T1 (de)
AU (1) AU610513B2 (de)
CA (1) CA1295533C (de)
DE (2) DE3766043D1 (de)
ES (1) ES2018292B3 (de)
FI (1) FI92477C (de)
FR (1) FR2602448B1 (de)
NO (1) NO165180C (de)
ZA (1) ZA875789B (de)

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FI104959B (fi) 1994-06-23 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
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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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
DE102013207860B4 (de) * 2013-04-30 2017-06-22 MTU Aero Engines AG Verfahren zum Betreiben eines pneumatischen Nadlers sowie zugehöriger pneumatischer Nadler
FR3027543B1 (fr) * 2014-10-28 2016-12-23 Montabert Roger Appareil a percussions
US9840000B2 (en) * 2014-12-17 2017-12-12 Caterpillar Inc. Hydraulic hammer having variable stroke control
US20160199969A1 (en) * 2015-01-12 2016-07-14 Caterpillar Inc. Hydraulic hammer having variable stroke control
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
KR101709673B1 (ko) * 2016-12-13 2017-03-09 대모 엔지니어링 주식회사 2단 오토스트로크 유압 브레이커
WO2019022021A1 (ja) * 2017-07-24 2019-01-31 古河ロックドリル株式会社 液圧式打撃装置
FI128135B (fi) * 2017-10-20 2019-10-31 Pneumaxpert Oy Oskillointisylinterijärjestely
FR3077753B1 (fr) * 2018-02-14 2020-01-31 Montabert Procede de reglage de la course de frappe d’un piston de frappe d’un appareil a percussions, et un appareil a percussions pour la mise en œuvre de ce procede
CN108331582B (zh) * 2018-03-16 2024-02-02 王代朋 全液压石材矿用开采机

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CA1295533C (fr) 1992-02-11
EP0256955A1 (de) 1988-02-24
NO873291L (no) 1988-02-08
ES2018292B3 (es) 1991-04-01
ATE58082T1 (de) 1990-11-15
ZA875789B (en) 1988-04-27
NO165180B (no) 1990-10-01
FI873351A (fi) 1988-02-08
FI92477C (fi) 1994-11-25
JPS63174884A (ja) 1988-07-19
DE256955T1 (de) 1988-06-09
AU610513B2 (en) 1991-05-23
FR2602448B1 (fr) 1988-10-21
JPH0585311B2 (de) 1993-12-07
US4800797A (en) 1989-01-31
FI92477B (fi) 1994-08-15
AU7662087A (en) 1988-02-11
FI873351A0 (fi) 1987-08-03
FR2602448A1 (fr) 1988-02-12
DE3766043D1 (de) 1990-12-13
NO165180C (no) 1991-01-09
NO873291D0 (no) 1987-08-06

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