EP0047944B1 - Percussion tool - Google Patents

Percussion tool Download PDF

Info

Publication number
EP0047944B1
EP0047944B1 EP81106994A EP81106994A EP0047944B1 EP 0047944 B1 EP0047944 B1 EP 0047944B1 EP 81106994 A EP81106994 A EP 81106994A EP 81106994 A EP81106994 A EP 81106994A EP 0047944 B1 EP0047944 B1 EP 0047944B1
Authority
EP
European Patent Office
Prior art keywords
valve
pilot valve
impact
percussion piston
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP81106994A
Other languages
German (de)
French (fr)
Other versions
EP0047944A1 (en
Inventor
Alfred Paikert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT81106994T priority Critical patent/ATE10871T1/en
Publication of EP0047944A1 publication Critical patent/EP0047944A1/en
Application granted granted Critical
Publication of EP0047944B1 publication Critical patent/EP0047944B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • E21B6/06—Drives for drilling with combined rotary and percussive action the rotation being intermittent, e.g. obtained by ratchet device

Definitions

  • the invention relates to a hammering and drilling device which is operated by means of hydraulic fluid, in particular water under high pressure, and which has an outer, stationary part provided at the rear with a hydraulic fluid supply line and an inner, movable part carrying a hammering and drilling tool at the front end a main control valve for the hydraulic control of an oscillating movement of the movable part designed as a percussion piston and with a pilot spool controlled by the oscillating movement of the percussion piston for the hydraulic control of the main control valve, recoil nozzles or a linkage for the propulsion being arranged at the rear end of the stationary part.
  • Such a striking and drilling device is known from DE-PS 22 57 753.
  • the reciprocating movement of the pilot spool is carried out mechanically as a result of the oscillating movement of the percussion piston, while the control of the main control valve is carried out hydraulically by the pilot spool.
  • the pilot spool With every change of direction of the percussion piston there is an impact on the pilot spool, which reduces the usable force of the percussion piston.
  • the respective impact results in a particularly safe function of the pilot spool, since the oscillating movement takes place with great certainty even when the pressure fluid is dirty and the pilot spool is correspondingly difficult to operate.
  • control spool is therefore no longer displaced by a mechanical impact of the percussion piston on the pilot spool, but the displacement of the pilot spool is carried out on the basis of hydraulic forces. Because of the lack of impact, the full impact force of the percussion piston is available to the outside, so that the performance of the device according to the invention is significantly increased compared to the known device.
  • the device according to the invention makes use of known practices for cleaning pipes and ducts with the aid of an impact and drilling tool at the front end of the device, the effect of which can be supported by the escape of liquid under high pressure and its drive with the aid of a rod or with With the help of recoil nozzles at the rear end of the device.
  • the percussion piston, the pilot spool and the main control valve are nested essentially concentrically with one another in a manner known per se, and the percussion piston is designed as a differential piston.
  • the small piston area is continuously pressurized, while the larger piston area is alternately pressurized and vented.
  • the pilot spool is subjected to a similar, preliminary hydraulic effect, in which the resulting forces initially shift the pilot spool in one direction and the alternating pressurization and venting of an additional shoulder creates a temporary displacement of the pilot spool in the other direction.
  • the movements of the pilot spool cause the main control valve to oscillate between two end positions, the end positions each leading to the opening of one valve and the closing of another valve which are followed by hydraulic paths which result in pressurization or venting of the larger piston area of the differential piston.
  • the device according to the invention is provided with a device which, from the oscillating movement of the percussion piston, forces a known rotary movement of the piston about its longitudinal axis.
  • the resulting rotary movement takes place step-by-step, with supporting members being used under frictional engagement which slip when the rotary movement is impeded, so that damage to the device causing the rotary movement is virtually impossible.
  • a housing cover 1 with a hydraulic fluid supply line 2 or 2 ' is fastened, while on the other side the percussion piston 10 provided with a tool holder protrudes.
  • the majority of the pressure fluid passes through an opening 6 in the main control valve 7 and through one or more bores 8 in an insert 9 into the interior of the percussion piston 10, which opening is large as a blind bore, and via openings 11 into a cylinder space 12 which passes through the cylinder barrel 13 and is limited backwards by a seal 15 on the percussion piston 10; a further seal 14 mounted in the guide ring 54 prevents the pressure fluid from escaping at this point.
  • the space 12 is constantly pressurized by the liquid, so it is under high pressure.
  • a further part of the liquid under pressure is fed via channels 16 and 17 to a drilling tool 18 and 19, from which the liquid emerges at high speed for washing and cutting purposes.
  • pressures of 40-300 bar are used at a volume flow of approximately 100-500 liters per minute, with conventional sewer cleaning vehicles being used to generate these pressures and these flows.
  • the percussion piston has run over and opened a control bore 21 with a control edge 20 during an oscillating movement in the direction of arrow 22, a control edge 23 having closed a vent bore 24.
  • a pressure shoulder 25 is pressurized on the pilot spool 50, as a result of which the pilot spool 50 is shifted to the left (in the direction of arrow 22), because the forces acting on it to the left from the hydraulic loading of surfaces 25, 26 and 27 are greater overall than those after right-hand force from a piston surface 28.
  • the decisive pressure shoulder 25 is located within a control chamber 21 ', which, as shown, can be pressurized or vented.
  • the main control valve 7 is constantly acted upon by the pressure of the liquid with an end face 60, while a space 29 is continuously vented via vent holes 30, 31 and 32 and is therefore depressurized.
  • a space 33 is also constantly vented via bores 34, a space 35, a channel 36, an annular space 37 and openings 38 and is therefore depressurized.
  • a space 39 is constantly vented through the bores 31 and 32 and is therefore depressurized.
  • a control bore 40 is connected to the space 39, whereby a space 41 is depressurized, and the main control valve 7 is shifted so far to the left by the pressure on the surface 60 that valve surfaces 42 and 43 lie one on top of the other and the passage of the bottom Pressurized liquid from the opening 6 through a bore 44 into a cylinder space 45 is interrupted.
  • a passage is created between valve surfaces 46 and 47, and as a result the cylinder space 45 is connected to the environment via the channels 34 to 38 and is therefore depressurized.
  • the pilot spool 50 remains under the influence of the hydrau acting on it Lical forces on the surfaces 25, 27 and 28 and on the end face 60 of the main control valve 7 in its position until the control edge 20 of the percussion piston has passed over the control bore 21 and closed again, the vent bore 24 being run over by the control edge 23 and at the same time is opened.
  • the resulting relief of the pressure shoulder 25 and as a result of the pressure shoulder 26 already relieved in a cylinder space 45 now exceeds the hydraulic force acting on the pilot valve 50 on the surface 28 and the opposing forces on the surfaces 27 and 60, so that the pilot valve 50 follows moved to the right until it strikes the boundary of room 39.
  • a compression spring 61 holds the main control valve 7 in a position in which the valve surfaces 46 and 47 abut one another. This prevents valve displacement during transport, i.e. outside of the company. It ensures that the starting position is always ready for operation; the spring 61 has no function during operation.
  • the two exemplary embodiments do not differ from one another.
  • the insert 9 is guided and adjustable in length by means of a thread in the pilot valve 50, as a result of which the free cross section on the valve surfaces 42 and 43 can be set.
  • the two exemplary embodiments also have in common a device for forced rotation from the oscillating movement of the percussion piston 10, which is only shown in FIG. 1. It comprises two opposing members 55 and 56, the axis of rotation of which extends radially and which are rotatably mounted in the wall of the percussion piston 10.
  • a cantilever is arranged at its respective outer end, which projects in the circumferential direction from the central axis of the respective links 55 and 56.
  • an extension with a double wedge surface points once in the direction of the drilling tool 18 (link 55) and in the direction of the feed line 2 (link 56).
  • the double wedge surfaces dive into a keyway 58 and 59 and are each biased with the aid of a spring 57 so that they form a frictional engagement with the keyway 58 or 59 before reaching the end position of the percussion piston 10, that is to say a support point.
  • the further movement of the percussion piston 10 causes each link 55 or 56 to perform a rotary movement about the point of frictional engagement, so that the central axis of each link 55 or 56 performs a circular movement with respect to the point of frictional engagement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Electrophonic Musical Instruments (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

1. Impact and drilling device, which is operated by means of pressure liquid, in particular water under high pressure, and having an outer, rearward stationary part (1, 53), provided with a pressure liquid supply line line (2, 2') as well as an inner, moveable part (10), which bears an impact and drilling tool (18, 19) at the front end, with a main control valve (7) for the hydraulic control of a swinging movement of the moveable part, designed as a percussion piston (10), and with a pilot valve (50) for the hydraulic control of the main control valve (7), which pilot valve is for its part controlled by the swinging movement of the percussion piston (10), there being recoil jets (4) or a linkage for the advance arranged at the rear end of the stationary part (1, 53), characterised in that the pilot valve (50) and the percussion piston (10) are pushed into one another in the region of a neck on the percussion piston (10) and form a control chamber (21'), in that a thrust shoulder (25) is arranged on the pilot valve inside the control chamber (21'), and in that a displacement of the percussion piston (10) opens a control bore (21), radially arranged in the pilot valve (50) and serving to pressurize the control chamber (21') and closes a bore (24) serving to vent the chamber, or, in the case of an opposed displacement, closes and opens these bores respectively.

Description

Die Erfindung betrifft eine Schlag- und Bohrvorrichtung, die mittels Druckflüssigkeit, insbesondere Wasser unter Hochdruck betrieben wird und einen äußeren, rückwärtig mit einer Druckflüssigkeit-Zuführleitung versehenen ruhenden Teil sowie einen inneren, am vorderen Ende ein Schlag- und Bohrwerkzeug tragenden beweglichen Teil aufweist, mit einem Hauptsteuerventil zur hydraulischen Steuerung einer Schwingbewegung des als Schlagkolben ausgebildeten beweglichen Teiles und mit einem von der Schwingbewegung des Schlagkolbens seinerseits gesteuerten Vorsteuerschieber zur hydraulischen Steuerung des Hauptsteuerventils, wobei am hinteren Ende des ruhenden Teils Rückstoßdüsen oder ein Gestänge für den Vortrieb angeordnet sind.The invention relates to a hammering and drilling device which is operated by means of hydraulic fluid, in particular water under high pressure, and which has an outer, stationary part provided at the rear with a hydraulic fluid supply line and an inner, movable part carrying a hammering and drilling tool at the front end a main control valve for the hydraulic control of an oscillating movement of the movable part designed as a percussion piston and with a pilot spool controlled by the oscillating movement of the percussion piston for the hydraulic control of the main control valve, recoil nozzles or a linkage for the propulsion being arranged at the rear end of the stationary part.

Eine derartige Schlag- und Bohrvorrichtung ist nach der DE-PS 22 57 753 bekannt. Bei dieser Vorrichtung wird die hin- und hergehende Bewegung des Vorsteuerschiebers mechanisch als Folge der Schwingbewegung des Schlagkolbens ausgeführt, während die Steuerung des Hauptsteuerventils durch den Vorsteuerschieber hydraulisch erfolgt. Bei jedem Richtungswechsel des Schlagkolbens findet also ein Aufprall auf den Vorsteuerschieber statt, der die nutzbare Kraft des Schlagkolbens mindert. Allerdings bewirkt der jeweilige Aufprall eine besonders sichere Funktion des Vorsteuerschiebers, da auch bei verschmutzter Druckflüssigkeit und entsprechend schwergängigem Vorsteuerschieber die Oszillierbewegung mit sehr großer Sicherheit stattfindet.Such a striking and drilling device is known from DE-PS 22 57 753. In this device, the reciprocating movement of the pilot spool is carried out mechanically as a result of the oscillating movement of the percussion piston, while the control of the main control valve is carried out hydraulically by the pilot spool. With every change of direction of the percussion piston there is an impact on the pilot spool, which reduces the usable force of the percussion piston. However, the respective impact results in a particularly safe function of the pilot spool, since the oscillating movement takes place with great certainty even when the pressure fluid is dirty and the pilot spool is correspondingly difficult to operate.

Es ist demnach Aufgabe der Erfindung, eine Schlag- und Bohrvorrichtung dieser Art zu verbessern, bei der die nutzbare Kraft des Schlagkolbens vergrößert und die bisher erzielbare Betriebssicherheit erhalten wird.It is therefore an object of the invention to improve a striking and drilling device of this type, in which the usable force of the percussion piston is increased and the operational reliability that can be achieved to date is maintained.

Die Lösung besteht darin, daß der Vorsteuerschieber und der Schlagkolben im Bereich eines Ansatzes an den Schlagkolben ineinander geschoben sind und eine Steuerkammer bilden, daß innerhalb der Steuerkammer an dem Vorsteuerschieber eine Druckschulter angebracht ist, und daß eine Verschiebung des Schlagkolbens eine zur Druckbeaufschlagung der Steuerkammer dienende, in dem Vorsteuerschieber radial angeordnete Steuerbohrung öffnet und eine zur Entlüftung dienende Bohrung schließt bzw. bei einer entgegengesetzten Verschiebung schließt und öffnet.The solution is that the pilot spool and the percussion piston are pushed into one another in the area of an attachment to the percussion piston and form a control chamber, that a pressure shoulder is attached to the pilot spool within the control chamber, and that a displacement of the percussion piston serves to pressurize the control chamber , in the pilot slide valve opens a radially arranged control hole and closes a hole used for ventilation or closes and opens in the case of an opposite displacement.

Bei der Erfindung erfolgt die Verschiebung des Steuerschieber also nicht mehr durch einen mechanischen Aufprall des Schlagkolbens auf den Vorsteuerschieber, sondern die Verschiebung des Vorsteuerschiebers wird aufgrund hydraulischer Kräfte vorgenommen. Wegen des fehlenden Aufprall steht nach außen hin die volle Schlagkraft des Schlagkolbens zur Verfügung, so daß die Leistungsfähigkeit der erfindungsgemä-Ben Vorrichtung gegenüber der bekannten Vorrichtung wesentlich erhöht ist.In the invention, the control spool is therefore no longer displaced by a mechanical impact of the percussion piston on the pilot spool, but the displacement of the pilot spool is carried out on the basis of hydraulic forces. Because of the lack of impact, the full impact force of the percussion piston is available to the outside, so that the performance of the device according to the invention is significantly increased compared to the known device.

In einer Weiterbildung der Erfindung ist vorgesehen, daß bei versagender hydraulischer Bewegung des Vorsteuerschiebers eine mechanisch bewirkte, von dem Schlagkolben ausgehende Bewegung stattfindet, die sich in den beiden Endlagen umkehrt und zu einer oszillierenden Bewegung des Vorsteuerschiebers führt. Im Störfall greift also die Erfindung auf die bisher benutzte Art der Vorsteuerschieberbewegung zurück, und zwar unter Inkaufnahme eines gewissen Leistungsverlustes. Dieser Leistungsverlust ist dem völligen Ausfall der Vorrichtung stets vorzuziehen, da die Chance besteht, daß die Vorrichtung auch mit verminderter Leistung in einem entsprechenden Kanal weiterläuft. Es sei darauf hingewiesen, daß dieser Störfall relativ selten ist und daß in der Regel die Bewegung des Vorsteuerschiebers hydraulisch bewirkt wird.In a further development of the invention it is provided that if the hydraulic spool of the pilot spool fails, a mechanically effected movement starting from the percussion piston takes place, which reverses in the two end positions and leads to an oscillating movement of the pilot spool. In the event of a fault, the invention therefore falls back on the type of pilot spool movement used hitherto, with the acceptance of a certain loss in performance. This loss of power is always preferable to the complete failure of the device, since there is a chance that the device will continue to run in a corresponding channel even with reduced power. It should be noted that this accident is relatively rare and that the movement of the pilot spool is usually effected hydraulically.

Im übrigen bedient sich die erfindungsgemäße Vorrichtung bekannter Praktiken zur Reinigung von Rohren und Kanälen mit Hilfe eines Schlag-und Bohrwerkzeuges am vorderen Ende der Vorrichtung, dessen Wirkung durch den Austritt von Flüssigkeit unter hohem Druck unterstützt werden kann und deren Antrieb mit Hilfe eines Gestänges oder mit Hilfe von Rückstoßdüsen am hinteren Ende der Vorrichtung erfolgt.In addition, the device according to the invention makes use of known practices for cleaning pipes and ducts with the aid of an impact and drilling tool at the front end of the device, the effect of which can be supported by the escape of liquid under high pressure and its drive with the aid of a rod or with With the help of recoil nozzles at the rear end of the device.

Der Schlagkolben, der Vorsteuerschieber sowie das Hauptsteuerventil sind in an sich bekannter Weise im wesentlichen konzentrisch zueinander ineinandergeschachtelt, und der Schlagkolben ist als Differenzialkolben ausgebildet. Die kleine Kolbenfläche wird dauernd mit Druck beaufschlagt, während die größere Kolbenfläche abwechselnd druckbeaufschlagt und entlüftet wird. Der Vorsteuerschieber wird einer ähnlichen, vorlaufenden hydraulischen Wirkung unterworfen, bei der zunächst die resultierenden Kräfte eine Verschiebung des Vorsteuerschiebers in der einen Richtung und die abwechselnde Druckbeaufschlagung und Entlüftung einer zusätzlich geschaffenen Schulter eine vorübergehende Verschiebung des Vorsteuerschiebers in die andere Richtung bewirkt. Die Bewegungen des Vorsteuerschiebers lassen das Hauptsteuerventil zwischen zwei Endlagen oszillieren, wobei die Endlagen jeweils zu der Öffnung eines Ventils und zur Schließung eines anderen Ventiles führt, denen Hydraulikwege nachgeschaltet sind, die zu einer Druckbeaufschlagung bzw. Entlüftung der größeren Kolbenfläche des Differenzkolbens führen.The percussion piston, the pilot spool and the main control valve are nested essentially concentrically with one another in a manner known per se, and the percussion piston is designed as a differential piston. The small piston area is continuously pressurized, while the larger piston area is alternately pressurized and vented. The pilot spool is subjected to a similar, preliminary hydraulic effect, in which the resulting forces initially shift the pilot spool in one direction and the alternating pressurization and venting of an additional shoulder creates a temporary displacement of the pilot spool in the other direction. The movements of the pilot spool cause the main control valve to oscillate between two end positions, the end positions each leading to the opening of one valve and the closing of another valve which are followed by hydraulic paths which result in pressurization or venting of the larger piston area of the differential piston.

Die letztgenannten Ventile werden z. B. durch eine radial nach außen sich erstreckende Erweiterung an dem Hauptsteuerventil gebildet, so daß angesichts des relativ großen Durchmessers bei kleinen Bewegungen des Hauptsteuerventils relativ große Ventilquerschnitte entstehen, die einen ungehinderten Zutritt der Druckflüssigkeit zu dem Differentialkolben und eine entsprechend rasche Ableitung während der Entlüftung sicherstellen. In dieser Weise entsteht eine besonders kräftige Schlagwirkung des Schlagkolbens, der identisch mit dem Differentialkolben ist.The latter valves are e.g. B. formed by a radially outwardly extending extension on the main control valve, so that in view of the relatively large diameter with small movements of the main control valve, relatively large valve cross sections are created, which ensure unimpeded access of the pressure fluid to the differential piston and a correspondingly rapid discharge during the venting . In this way, a special one arises powerful impact of the impact piston, which is identical to the differential piston.

In einer Weiterbildung ist die erfindungsgemäße Vorrichtung mit einer Einrichtung versehen, die aus der Schwingbewegung des Schlagkolbens eine an sich bekannte Drehbewegung des Kolbens um dessen Längsachse erzwingt. Die resultierende Drehbewegung erfolgt schrittweise, wobei unter Reibschluß sich abstützende Glieder verwendet werden, die bei einer Behinderung der Drehbewegung durchrutschen, so daß eine Beschädigung der die Drehbewegung hervorrufenden Einrichtung so gut wie ausgeschlossen ist.In a further development, the device according to the invention is provided with a device which, from the oscillating movement of the percussion piston, forces a known rotary movement of the piston about its longitudinal axis. The resulting rotary movement takes place step-by-step, with supporting members being used under frictional engagement which slip when the rotary movement is impeded, so that damage to the device causing the rotary movement is virtually impossible.

Nachfolgend werden Ausführungsbeispiele der Erfindung, die in der Zeichnung dargestellt sind, näher erläutert ; darin bedeuten :

  • Figur 1 eine Längsschnittansicht durch eine Schlag- und Bohrvorrichtung gemäß der Erfindung mit einer ausschließlich hydraulisch hervorgerufenen Oszillationsbewegung des Vorsteuerschiebers und
  • Figur 2 eine Längsschnittansicht in Form eines Ausschnittes eines weiteren Ausführungsbeispieles der erfindungsgemäßen Schlag- und Bohrvorrichtung mit einer hilfsweise mechanischen Bewegung des Vorsteuerschiebers.
Exemplary embodiments of the invention which are illustrated in the drawing are explained in more detail below; mean:
  • Figure 1 is a longitudinal sectional view through a striking and drilling device according to the invention with an exclusively hydraulically induced oscillation movement of the pilot spool and
  • Figure 2 is a longitudinal sectional view in the form of a section of a further embodiment of the impact and drilling device according to the invention with an auxiliary mechanical movement of the pilot spool.

Die in der Fig. 1 dargestellte Schlag- und Bohrvorrichtung besteht im wesentlichen aus einem äußeren Mantelrohr 52, in welchem ein druckfestes Zylinderrohr 13, ein Lagerblock 53 sowie ein Führungsring 54 gehalten ist und aus einem Schlagkolben 10 einschließlich der nachfolgend noch erläuterten Steuerteile. An den Stirnseiten des Mantelrohres 52 ist einerseits ein Gehäusedeckel 1 mit einer Druckflüssigkeit-Zuführleitung 2 bzw. 2' befestigt, während auf der anderen Seite der mit einem Werkzugträger versehene Schlagkolben 10 herausragt.1 consists essentially of an outer jacket tube 52, in which a pressure-resistant cylinder tube 13, a bearing block 53 and a guide ring 54 is held, and a percussion piston 10 including the control parts to be explained below. On the end faces of the casing tube 52, on the one hand, a housing cover 1 with a hydraulic fluid supply line 2 or 2 'is fastened, while on the other side the percussion piston 10 provided with a tool holder protrudes.

Bei dem in der Fig. 1 dargestellten Ausführungsbeispiel erfolgt die Verschiebung eines Vorsteuerschiebers 50 und damit die Ansteuerung eines Hauptsteuerventils 7 aufgrund hydraulischer Kräfte, was nachfolgend im einzelnen beschrieben wird :

  • Durch die Zuführleitung 2 bzw. 2' an dem rückwärtigen Gehäusedeckel 1 der Schlag- und Bohrvorrichtung wird einem Raum 3 Flüssigkeit unter Hochdruck zugeführt, welche zum Teil über Rückstoßdüsen 4 austritt und dabei als Rückstoßdüsenstrahl 5 zum Vortrieb der Vorrichtung ausgenutzt wird. Abweichend davon kann der Vortrieb auch durch ein Gestänge erfolgen, durch das zweckmäßigerweise dann die Flüssigkeit unter Hochdruck der Vorrichtung zugeführt wird.
In the exemplary embodiment shown in FIG. 1, the displacement of a pilot valve 50 and thus the activation of a main control valve 7 takes place on the basis of hydraulic forces, which is described in detail below:
  • Through the feed line 2 or 2 'on the rear housing cover 1 of the hammering and drilling device, liquid 3 is fed under high pressure to a chamber 3, which partly exits via recoil nozzles 4 and is used as a recoil nozzle jet 5 to propel the device. Deviating from this, the propulsion can also take place through a linkage through which the liquid is then expediently fed to the device under high pressure.

Der Großteil der Druckflüssigkeit tritt durch eine Öffnung 6 in dem Hauptsteuerventil 7 und durch eine oder mehrere Bohrungen 8 in einem Einsatz 9 in den als Sackbohrung großen Öffnungsquerschnittes ausgebildeten Innenraum des Schlagkolbens 10 und über Öffnungen 11 in einen Zylinderraum 12, welcher durch das Zylinderrohr 13 und nach rückwärts durch eine Dichtung 15 an dem Schlagkolben 10 begrenzt wird ; eine weitere, in dem Führungsring 54 gelagerte Dichtung 14 verhindert das Austreten der Druckflüssigkeit an dieser Stelle. Der Raum 12 ist ständig von der Flüssigkeit beaufschlagt, er steht also unter Hochdruck.The majority of the pressure fluid passes through an opening 6 in the main control valve 7 and through one or more bores 8 in an insert 9 into the interior of the percussion piston 10, which opening is large as a blind bore, and via openings 11 into a cylinder space 12 which passes through the cylinder barrel 13 and is limited backwards by a seal 15 on the percussion piston 10; a further seal 14 mounted in the guide ring 54 prevents the pressure fluid from escaping at this point. The space 12 is constantly pressurized by the liquid, so it is under high pressure.

Bei dem dargestellten Ausführungsbeispiel in der Fig. 1 wird ein weiterer Teil der unter Druck stehenden Flüssigkeit über Kanäle 16 und 17 einem Bohrwerkzeug 18 und 19 zugeführt, aus dem zu Spül- und Schneidzwecken die Flüssigkeit mit hoher Geschwindigkeit austritt. Bei ausgeführten Vorrichtungen werden Drücke von 40-300 bar verwendet bei einem Volumenstrom von etwa 100-500 Liter pro Minute, wobei zur Erzeugung dieser Drücke und dieser Ströme übliche Kanalspülfahrzeuge verwendet werden. In der in der Fig. 1 wiedergegebenen Stellung der Schlag- und Bohrvorrichtung hat der Schlagkolben bei einer in Pfeilrichtung 22 gerichteten Schwingbewegung mit einer Steuerkante 20 eine Steuerbohrung 21 überfahren und geöffnet, wobei eine Steuerkante 23 eine Entlüftungsbohrung 24 verschlossen hat. Hierdurch ist eine Druckschulter 25 an dem Vorsteuerschieber 50 druckbeaufschlagt, wodurch der Vorsteuerschieber 50 nach links (in Pfeilrichtung 22) verschoben wird, weil die auf ihn nach links einwirkenden Kräfte aus der hydraulischen Belastung von Flächen 25, 26 und 27 insgesamt größer sind als die nach rechts wirkende Kraft aus einer Kolbenfläche 28. Die ausschlaggebende Druckschulter 25 befindet sich innerhalb einer Steuerkammer 21', die, wie gezeigt, druckbeaufschlagt oder entlüftet sein kann.In the exemplary embodiment shown in FIG. 1, a further part of the liquid under pressure is fed via channels 16 and 17 to a drilling tool 18 and 19, from which the liquid emerges at high speed for washing and cutting purposes. In the case of implemented devices, pressures of 40-300 bar are used at a volume flow of approximately 100-500 liters per minute, with conventional sewer cleaning vehicles being used to generate these pressures and these flows. In the position of the percussion and drilling device shown in FIG. 1, the percussion piston has run over and opened a control bore 21 with a control edge 20 during an oscillating movement in the direction of arrow 22, a control edge 23 having closed a vent bore 24. As a result, a pressure shoulder 25 is pressurized on the pilot spool 50, as a result of which the pilot spool 50 is shifted to the left (in the direction of arrow 22), because the forces acting on it to the left from the hydraulic loading of surfaces 25, 26 and 27 are greater overall than those after right-hand force from a piston surface 28. The decisive pressure shoulder 25 is located within a control chamber 21 ', which, as shown, can be pressurized or vented.

Das Hauptsteuerventil 7 ist mit einer Stirnfläche 60 ständig von dem Druck der Flüssigkeit beaufschlagt, während ein Raum 29 über Entlüftungsbohrungen 30, 31 und 32 ständig entlüftet und somit drucklos ist. Auch ein Raum 33 ist über Bohrungen 34, einen Raum 35, einen Kanal 36, einen Ringraum 37 und Öffnungen 38 ständig entlüftet und somit drucklos. Ebenso ist ein Raum 39 über die Bohrungen 31 und 32 ständig entlüftet und damit drucklos.The main control valve 7 is constantly acted upon by the pressure of the liquid with an end face 60, while a space 29 is continuously vented via vent holes 30, 31 and 32 and is therefore depressurized. A space 33 is also constantly vented via bores 34, a space 35, a channel 36, an annular space 37 and openings 38 and is therefore depressurized. Likewise, a space 39 is constantly vented through the bores 31 and 32 and is therefore depressurized.

In der dargestellten Stellung ist eine Steuerbohrung 40 mit dem Raum 39 verbunden, wodurch ein Raum 41 drucklos ist, und das Hauptsteuerventil 7 von dem auf der Fläche 60 lastenden Druck so weit nach links verschoben, daß Ventilflächen 42 und 43 aufeinanderliegen und der Durchgang der unter Druck stehenden Flüssigkeit von der Öffnung 6 über eine Bohrung 44 in einen Zylinderraum 45 unterbrochen ist. Durch diese Verschiebung ist zwischen Ventilflächen 46 und 47 ein Durchgang geschaffen und hierdurch der Zylinderraum 45 über die Kanäle 34 bis 38 mit der Umgebung verbunden und somit drucklos. Durch den Wegfall der Druckbelastung auf der größeren Kolbenfläche 48 des als Differentialkolben ausgebildeten Schlagkolbens 10 überwiegt nunmehr die nach rechts in Pfeilrichtung 49 gerichtete Kraft auf die kleinere Kolbenfläche des Schlagkolbens, wodurch letzterer wieder nach rechts (in Pfeilrichtung 49) bewegt wird.In the position shown, a control bore 40 is connected to the space 39, whereby a space 41 is depressurized, and the main control valve 7 is shifted so far to the left by the pressure on the surface 60 that valve surfaces 42 and 43 lie one on top of the other and the passage of the bottom Pressurized liquid from the opening 6 through a bore 44 into a cylinder space 45 is interrupted. As a result of this displacement, a passage is created between valve surfaces 46 and 47, and as a result the cylinder space 45 is connected to the environment via the channels 34 to 38 and is therefore depressurized. By eliminating the pressure load on the larger piston surface 48 of the percussion piston 10 designed as a differential piston, the force directed to the right in the direction of arrow 49 now predominates on the smaller piston surface of the percussion piston, whereby the latter is moved to the right again (in the direction of arrow 49).

Der Vorsteuerschieber 50 dagegen verharrt unter dem Einfluß der auf ihn einwirkenden hydraulischen Kräfte auf die Flächen 25, 27 und 28 sowie auf die Stirnfläche 60 des Hauptsteuerventils 7 in seiner Stellung so lange, bis die Steuerkante 20 des Schlagkolbens die Steuerbohrung 21 wieder überfahren und verschlossen hat, wobei gleichzeitig die Entlüftungsbohrung 24 von der Steuerkante 23 überfahren und geöffnet wird. Die daraus resultierende Entlastung der Druckschulter 25 sowie infolge der zuvor bereits entlasteten Druckschulter 26 in einem Zylinderraum 45 übersteigt nunmehr die auf den Vorsteuerschieber 50 wirkende hydraulische Kraft auf die Fläche 28 die entgegengerichteten Kräfte auf die Flächen 27 und 60, so daß der Vorsteuerschieber 50 sich nach rechts bewegt, bis er an die Begrenzung des Raumes 39 anschlägt.The pilot spool 50, however, remains under the influence of the hydrau acting on it Lical forces on the surfaces 25, 27 and 28 and on the end face 60 of the main control valve 7 in its position until the control edge 20 of the percussion piston has passed over the control bore 21 and closed again, the vent bore 24 being run over by the control edge 23 and at the same time is opened. The resulting relief of the pressure shoulder 25 and as a result of the pressure shoulder 26 already relieved in a cylinder space 45 now exceeds the hydraulic force acting on the pilot valve 50 on the surface 28 and the opposing forces on the surfaces 27 and 60, so that the pilot valve 50 follows moved to the right until it strikes the boundary of room 39.

Die Steuerbohrung 40 wird hierdurch mit einer Bohrung 51 verbunden und der Zylinderraum 41 mit Druckflüssigkeit beaufschlagt. Die in diesem Zylinderraum 41 auf das Hauptsteuerventil 7 einwirkende Kraft übersteigt jetzt die entgegengesetzt auf ihn wirkende Kraft infolge der Fläche 60, so daß sich das Hauptsteuerventil 7 nach rechts bewegt, bis die Ventilflächen 46 und 47 aneinanderliegen und so den Auslaß aus dem Zylinderraum 45 verschließen. Dieser Zylinderraum 45 wird nun über den zwischen den Ventilflächen 42 und 43 entstandenen Ringspalt wieder mit Druckflüssigkeit gefüllt. Das führt zu einer Bewegung des Schlagkolbens 10 nach links in Pfeilrichtung 22, während der Vorsteuerschieber 50 unter dem Einfluß der auf ihn einwirkenden hydraulischen Kräfte in seiner Stellung verharrt, bis die Steuerbohrung 21 geöffnet und die Entlüftungsbohrung 24 durch den sich verschiebenden Schlagkolben 10 bzw. dessen Steuerkanten verschlossen wird. Der eingangs beschriebene Vorgang wiederholt sich dann wieder.The control bore 40 is thereby connected to a bore 51 and the cylinder chamber 41 is pressurized with hydraulic fluid. The force acting on the main control valve 7 in this cylinder space 41 now exceeds the force acting on it in opposition to it due to the surface 60, so that the main control valve 7 moves to the right until the valve surfaces 46 and 47 abut one another and thus close the outlet from the cylinder space 45 . This cylinder space 45 is now filled again with hydraulic fluid via the annular gap formed between the valve surfaces 42 and 43. This leads to a movement of the percussion piston 10 to the left in the direction of the arrow 22, while the pilot spool 50 remains in its position under the influence of the hydraulic forces acting on it until the control bore 21 opens and the vent bore 24 through the displacing percussion piston 10 or its Control edges is closed. The process described above is then repeated again.

. Eine Druckfeder 61 hält in drucklosem Zustand das Hauptsteuerventil 7 in einer Lage, in der die Ventilflächen 46 und 47 aneinanderliegen. Dadurch wird eine Ventilverlagerung während eines Transportes, also außerhalb des Betriebes verhindert. Sie stellt eine stets funktionsbereite Ausgangslage sicher, während des Betriebes hat die Feder 61 keine Funktion.. In the depressurized state, a compression spring 61 holds the main control valve 7 in a position in which the valve surfaces 46 and 47 abut one another. This prevents valve displacement during transport, i.e. outside of the company. It ensures that the starting position is always ready for operation; the spring 61 has no function during operation.

In der Fig. 2 ist ein weiteres Ausführungsbeispiel der erfindungsgemäßen Schlag- und Bohrvorrichtung dargestellt, das sich von dem vorangehend beschriebenen Ausführungsbeispiel dadurch unterscheidet, daß der Vorsteuerschieber 50 hilfsweise aufgrund mechanischer Wirkung infolge der Schwingbewegung des Schlagkolbens 10 bewegt wird, wenn die im Regelfall tätige hydraulische Umsteuerung versagt. Dazu ist eine Stirnfläche 62 an dem Schlagkolben 10 in sich eben ausgebildet, so daß sie mit der Stirnfläche 28 des Vorsteuerschiebers 50 zusammenwirken kann. Die weitere Prallflächenpaarung besteht aus der Druckschulter 25, die bei Ausfall der hydraulischen Umsteuerung von der Steuerkante 23 mitgenommen wird, was zu einer Oszillierbewegung des Vorsteuerschiebers 50 führt.In Fig. 2, another embodiment of the impact and drilling device according to the invention is shown, which differs from the embodiment described above in that the pilot spool 50 is moved auxiliary due to mechanical action due to the swinging movement of the percussion piston 10 when the hydraulic, which is usually active Reversal fails. For this purpose, an end face 62 on the percussion piston 10 is flat in itself, so that it can interact with the end face 28 of the pilot valve 50. The further baffle pairing consists of the pressure shoulder 25, which is carried along by the control edge 23 if the hydraulic reversal fails, which leads to an oscillating movement of the pilot spool 50.

Im übrigen weichen beide Ausführungsbeispiele nicht voneinander ab. Zum Beispiel ist in beiden Fällen der Einsatz 9 mit Hilfe eines Gewindes in dem Vorsteuerschieber 50 geführt und längenverstellbar, wodurch der freie Druchtrittsquerschnitt an den Ventilflächen 42 und 43 eingestellt werden kann. Auch ist beiden Ausführungsbeispielen eine Einrichtung zur zwangsweisen Drehung aus der Schwingbewegung des Schlagkolbens 10 gemeinsam, die nur in der Fig. 1 dargestellt ist. Sie umfaßt zwei sich gegenüberliegende Glieder 55 und 56, deren Drehachse radial verläuft und die in der Wandung des Schlagkolbens 10 drehbar gelagert sind. An ihrem jeweils äußeren Ende ist ein Ausleger angeordnet, der von der Mittelachse der jeweiligen Glieder 55 und 56 in Umfangsrichtung absteht. An dessen jeweils freiem Ende weist ein Ansatz mit einer Doppelkeilfläche einmal in Richtung auf das Bohrwerkzeug 18 (Glied 55) und in Richtung auf die Zuleitung 2 (Glied 56). Die Doppelkeilflächen tauchen in eine Keilnut 58 und 59 ein und sind mit Hilfe einer Feder 57 jeweils so vorgespannt, daß sie noch vor Erreichen der Endlage des Schlagkolbens 10 mit der Keilnut 58 bzw. 59 einen Reibschluß bilden, also einen Abstützpunkt. Die weitere Bewegung des Schlagkolbens 10 bewirkt, daß jedes Glied 55 bzw. 56 um den Punkt des Reibschlusses eine Drehbewegung ausführt, so daß die Mittelachse jedes Gliedes 55 bzw. 56, bezogen auf den Punkt des Reibschlusses eine Kreisbewegung ausführt. Da der Punkt des Reibschlusses in einer und die Drehachse jedes Gliedes 55 bzw. 56 in einer anderen Ebene liegt, geht mit der Axialbewegung des Schlagkolbens auch eine Drehbewegung einher, die dann bendet ist, wenn der Schlagkolben seine Endlage erreicht hat. Auf dem entgegengesetzten Weg wiederholt sich der Vorgang mit Hilfe des an der entsprechenden Seite angeordneten Gliedes 55 bzw. 56, so daß in beiden Bewegungsrichtungen die Drehbewegung erzeugt wird.Otherwise, the two exemplary embodiments do not differ from one another. For example, in both cases, the insert 9 is guided and adjustable in length by means of a thread in the pilot valve 50, as a result of which the free cross section on the valve surfaces 42 and 43 can be set. The two exemplary embodiments also have in common a device for forced rotation from the oscillating movement of the percussion piston 10, which is only shown in FIG. 1. It comprises two opposing members 55 and 56, the axis of rotation of which extends radially and which are rotatably mounted in the wall of the percussion piston 10. A cantilever is arranged at its respective outer end, which projects in the circumferential direction from the central axis of the respective links 55 and 56. At its free end, an extension with a double wedge surface points once in the direction of the drilling tool 18 (link 55) and in the direction of the feed line 2 (link 56). The double wedge surfaces dive into a keyway 58 and 59 and are each biased with the aid of a spring 57 so that they form a frictional engagement with the keyway 58 or 59 before reaching the end position of the percussion piston 10, that is to say a support point. The further movement of the percussion piston 10 causes each link 55 or 56 to perform a rotary movement about the point of frictional engagement, so that the central axis of each link 55 or 56 performs a circular movement with respect to the point of frictional engagement. Since the point of the frictional engagement lies in one plane and the axis of rotation of each link 55 or 56 lies in a different plane, the axial movement of the percussion piston also goes hand in hand with a rotary movement which is stopped when the percussion piston has reached its end position. In the opposite way, the process is repeated with the aid of the link 55 or 56 arranged on the corresponding side, so that the rotational movement is generated in both directions of movement.

Für eine besonders gleichmäßige Drehbewegung, die bezüglich der Umfangskräfte ausgeglichen ist, sind drei Gruppen von Gliedern 55 und 56 gleichmäßig um den Umfang verteilt, von denen nur eine in der Fig. 1 dargestellt ist. Der Reibschluß zwischen den Gliedern 55 und 56 und den Keilnuten 58 und 59 ist durch die Wahl des Keilwinkels so gewählt, daß bei einer ernsthaften Behinderung der Drehbewegung der Reibschluß verloren geht und statt einer Drehbewegung des Schlagkolbens 10 eine Rutschbewegung zwischen den Gliedern und den Ringnuten eintritt. In dieser Weise wird die erfindungsgemäße Vorrichtung gegen Beschädigungen geschützt. In der Praxis treten Schlagfolgen von 1 000-1 500 pro Minute auf, die zu einer Drehzahl von 100-200 Umdrehungen pro Minute führen.For a particularly uniform rotary movement, which is balanced with respect to the circumferential forces, three groups of links 55 and 56 are distributed uniformly around the circumference, only one of which is shown in FIG. 1. The frictional engagement between the members 55 and 56 and the splines 58 and 59 is selected by the choice of the spline angle so that the frictional engagement is lost in the event of a serious hindrance to the rotational movement and instead of a rotational movement of the percussion piston 10, a slipping movement occurs between the members and the annular grooves . In this way, the device according to the invention is protected against damage. In practice, impact sequences of 1,000-1,500 per minute occur, which lead to a speed of 100-200 revolutions per minute.

Bei größeren Kanaldurchmessern, die zu reinigen und von Rückständen zu befreien sind, wird ein entsprechend großes Werkzeug an dem Werkzeugträger angebracht, damit der theoretisch nutzbare Querschnitt des Kanals auch tatsächlich erfaßt wird. Damit dabei die erfindungsgemäße Schlag- und Bohrvorrichtung etwa in der Mitte des Werkzeuges gehalten ist, kann die Vorrichtung auf einen Schlitten gestellt werden, dessen Kufen in weiten Bereichen verstellbar und damit verschiedenen Durchmessern anpaßbar sind.For larger duct diameters that have to be cleaned and cleaned of residues, a correspondingly large tool is attached to the tool carrier so that the theoretically usable cross section of the duct is actually recorded. Thus the impact and drilling device according to the invention is held approximately in the middle of the tool, the device can be placed on a slide, the runners of which are adjustable over a wide range and can therefore be adapted to different diameters.

Claims (11)

1. Impact and drilling device, which is operated by means of pressure liquid, in particular water under high pressure, and having an outer, rearward stationary part (1, 53), provided with a pressure liquid supply line line (2, 2'), as well as an inner, moveable part (10), which bears an impact and drilling tool (18, 19) at the front end, with a main control valve (7) for the hydraulic control of a swinging movement of the moveable part, designed as a percussion piston (10), and with a pilot valve (50) for the hydraulic control of the main control valve (7), which pilot valve is for its part controlled by the swinging movement of the percussion piston (10), there being recoil jets (4) or a linkage for the advance arranged at the rear end of the stationary part (1, 53), characterised in that the pilot valve (50) and the percussion piston (10) are pushed into one another in the region of a neck on the percussion piston (10) and form a control chamber (21'), in that a thrust shoulder (25) is arranged on the pilot valve inside the control chamber (21'), and in that a displacement of the percussion piston (10) opens a control bore (21), radially arranged in the pilot valve (50) and serving to pressurize the control chamber (21'), and closes a bore (24) serving to vent the chamber, or, in the case of an opposed displacement, closes and opens these bores respectively.
2. Impact and drilling device according to claim 1, characterised in that the percussion piston (10) is designed in a way known per se as a differential piston, in that inside the pilot valve (50) the main control valve (7) is mounted moveably, and in that the larger piston area of the differential piston is pressurized or vented by means of valves (42, 43 ; 46, 47) actuated by the displacement of the main valve (7).
3. Impact and drilling device according to claim 2, characterised in that the pressure fluid is supplied through one or more bores (6 ; 8) in the main control valve (7) and in the pilot valve (50) to the percussion piston (10), which is provided with a blind bore of large cross-section, under constant impingement of the smaller piston area of the differential piston.
4. Impact and drilling device according to claim 1, characterised in that the control bore (21) for pressurizing the control chamber (21') is arranged in the region of a neck on the pilot valve and is opened and closed by means of a control edge (20) forming one limitation of the control chamber (21').
5. Impact and drilling device according to claim 1 or claim 4, characterised in that the venting bore (24) is likewise arranged in the pilot valve (50) and is led to the outside via an annular chamber (39) and bores (31, 32) and this venting bore is opened and closed by means of a control edge (23) forming the other limitation of the control chamber (21').
6. Impact and drilling device according to one of claims 1-5, characterised in that an outer, radial neck on the main control valve (7) is led in a cylindrical extension to form a cylinder space (41) and in that the cylinder space (41) is either pressurized or vented via a control bore (40) of the pilot valve (50).
7. Impact and drilling device according to claim 3, characterised in that the pilot valve (7) in that a tubular, longitudinally adjustable insert (9) together with the adjacent end face (43) of the main control valve (7) forms a first valve seat (42), in that a valve face (46) on the periphery of the main control valve (7) together with a valve face (47) on the pilot valve (50) forms a second valve, and in that, with the first valve (42, 43) open and the second valve (46, 47) closed, the larger piston area of the differential piston is pressurized and, with reversed valve position, is vented.
8. Impact and drilling device according to claim 7, characterised in that the valve faces (43, 46) of the main control valve (7) are formed by an extension stretching radially to the outside.
9. Impact and drilling device according to one of claims 7 or 8, characterised in that the insert (9) is adjustable inside the pilot valve (50) via a threaded connection.
10. Impact and drilling device according to one of claims 1-9, characterised in that, in the two end positions of the percussion piston (10), with frictional grip between the percussion piston (10), and the stationary part (13, 54) of the impact and drilling device, members (55, 56) exact an angular turning known per se from the swinging movement of the percussion piston (10).
11. Impact and drilling device according to claim 1 or claim 4, characterised in that the thrust shoulder (25) and an area (28) lying opposite it or the neck on the pilot valve (50) interacts with the control edge (23) for control of the venting bore (24) and with another area (62) on the percussion piston (10) in such a way that, in the absence of hydraulic movement of the pilot valve (50) with respect to the percussion piston (10), a movement of the pilot valve (50) is induced mechanically by the collision of the interacting areas or else edge or shoulder.
EP81106994A 1980-09-11 1981-09-07 Percussion tool Expired EP0047944B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81106994T ATE10871T1 (en) 1980-09-11 1981-09-07 IMPACT AND DRILL DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3034211 1980-09-11
DE3034211A DE3034211C2 (en) 1980-09-11 1980-09-11 Impact and drilling device that can be acted upon by a hydraulic fluid

Publications (2)

Publication Number Publication Date
EP0047944A1 EP0047944A1 (en) 1982-03-24
EP0047944B1 true EP0047944B1 (en) 1984-12-19

Family

ID=6111680

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81106994A Expired EP0047944B1 (en) 1980-09-11 1981-09-07 Percussion tool

Country Status (3)

Country Link
EP (1) EP0047944B1 (en)
AT (1) ATE10871T1 (en)
DE (2) DE3034211C2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102168523A (en) * 2011-04-27 2011-08-31 兰桥昌 Main driving and speed-changing system of drilling machine as well as operating mechanism of the drilling machine
CN102817555A (en) * 2012-08-31 2012-12-12 涂文斌 Hydroenergy impactor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59209775A (en) * 1983-05-13 1984-11-28 株式会社ランドマ−クウエスト Rock drill
SE444127B (en) * 1984-06-25 1986-03-24 Atlas Copco Ab PRESSURE WASHING DRIVE SINGLE DRILLING MACHINE
DE4131070C2 (en) * 1991-09-18 1993-11-18 Ingenieurkontor Fuer Maschinen Hydraulically driven hammer drill
CN113236156B (en) * 2021-04-19 2022-12-13 中煤科工集团淮北***技术研究院有限公司 In-hole supercharger based on steering valve

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2257753C3 (en) * 1972-11-24 1975-06-05 Georg Haerke Ag Rohr- Und Kanal-Reinigungsgeraete-Maschinen- Und Fahrzeugbau, 5630 Remscheid Impact and drilling device that can be acted upon by a hydraulic fluid
DE2425046A1 (en) * 1974-05-24 1975-12-04 Demag Drucklufttechnik Gmbh Hydraulic stroke control of reciprocating impact tool - has hollow impact piston and rotatable control piston with tapered outer recess
DE2536143C2 (en) * 1975-08-13 1982-01-28 Institut gornogo dela Akademii Nauk Kazachskoj SSR, Alma-Ata Hydraulic impact device
US4072198A (en) * 1976-04-30 1978-02-07 Chicago Pneumatic Tool Company Hydraulic rock drill
US4157121A (en) * 1977-02-04 1979-06-05 Chicago Pneumatic Tool Co. Hydraulic powered rock drill

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102168523A (en) * 2011-04-27 2011-08-31 兰桥昌 Main driving and speed-changing system of drilling machine as well as operating mechanism of the drilling machine
CN102817555A (en) * 2012-08-31 2012-12-12 涂文斌 Hydroenergy impactor

Also Published As

Publication number Publication date
ATE10871T1 (en) 1985-01-15
DE3034211A1 (en) 1982-03-25
DE3167834D1 (en) 1985-01-31
DE3034211C2 (en) 1983-03-17
EP0047944A1 (en) 1982-03-24

Similar Documents

Publication Publication Date Title
DE2813694C2 (en) Pressurized medium-actuated toggle lever clamping device with a double acting clamping cylinder in which a differential piston is guided in a longitudinally displaceable manner
EP0475171B1 (en) Hydraulically operated percussion mechanism
CH636407A5 (en) VALVE CONTROL FOR RAMM DRILLING DEVICES.
DE2400925A1 (en) IMPACT DEVICE
DE2754489A1 (en) HYDRAULIC ACTUATOR
DE1778952C3 (en) Hydraulic mold clamping device for a plastic injection molding machine
EP0203282B1 (en) Control of a hydraulic percussive drilling device
EP0047944B1 (en) Percussion tool
DE2461633C2 (en) Hydraulic impact device
EP0125232B1 (en) Process for cutting rock, and device for carrying out this process
DE2407177C3 (en) Release valve
DE2734214C2 (en) Rotary slide valve for directional control of the pressure medium for a double-acting hydraulic servomotor
DE412139C (en) Valve
EP0847836B1 (en) Percussive tool with fluid pressure drive
DE1239948B (en) Double-acting pressure cylinder activated by pressure medium
DE2726118B2 (en) Hydraulic impact device, in particular for rock drilling machines
DE722160C (en) Air hammer
DE2857176C1 (en) Hydraulic drive for the protection of a weaving machine
DE2257753C3 (en) Impact and drilling device that can be acted upon by a hydraulic fluid
DE1297510B (en) Device for periodic axial back and forth movement of a machine tool spindle, in particular a grinding spindle
DE68846C (en) Hydraulic ship steering apparatus with duplex steam pump
DE829824C (en) Compressed air control device for double-acting pistons of compressed air motors with the help of axial slides
DE2335731C2 (en) Hydraulically operated rock drill - allows quieter and more effective stable operation than pneumatic device
DE2235618C3 (en) Automatic control of the pressure medium supply to a hammer drill
DE240098C (en)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT DE FR GB SE

17P Request for examination filed

Effective date: 19820719

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT DE FR GB SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19841219

REF Corresponds to:

Ref document number: 10871

Country of ref document: AT

Date of ref document: 19850115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3167834

Country of ref document: DE

Date of ref document: 19850131

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19910930

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19920907

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19940919

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19950818

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19960531

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960907

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19960907

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19970927

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990701