EP0475171B1 - Hydraulically operated percussion mechanism - Google Patents

Hydraulically operated percussion mechanism Download PDF

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Publication number
EP0475171B1
EP0475171B1 EP91114231A EP91114231A EP0475171B1 EP 0475171 B1 EP0475171 B1 EP 0475171B1 EP 91114231 A EP91114231 A EP 91114231A EP 91114231 A EP91114231 A EP 91114231A EP 0475171 B1 EP0475171 B1 EP 0475171B1
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EP
European Patent Office
Prior art keywords
pressure
line
percussion piston
piston
percussion
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 - Lifetime
Application number
EP91114231A
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German (de)
French (fr)
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EP0475171A3 (en
EP0475171A2 (en
Inventor
Robert-Jan Dr.-Ing. Bartels
Hans-Dieter Piotrowski
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.)
SIG Plastics GmbH and Co KG
Original Assignee
Krupp Maschinentechnik GmbH
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Publication date
Application filed by Krupp Maschinentechnik GmbH filed Critical Krupp Maschinentechnik GmbH
Publication of EP0475171A2 publication Critical patent/EP0475171A2/en
Publication of EP0475171A3 publication Critical patent/EP0475171A3/en
Application granted granted Critical
Publication of EP0475171B1 publication Critical patent/EP0475171B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D9/00Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14Control devices for the reciprocating piston
    • B25D9/145Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D9/00Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14Control devices for the reciprocating piston
    • B25D9/26Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • the invention relates to a hydraulically operated hammer mechanism according to the preamble of claim 1.
  • the invention has for its object to design a hydraulically operated striking mechanism in such a way that the number of blows depending on the pressure force by an internal control in the striking mechanism itself, ie by the shortest route, can be adjusted and, accordingly, faults occurring outside the striking mechanism, by longer cable routes Conditional delays in the transmission of impulses or signals or incorrect control by the operator can be excluded.
  • the invention should be designed so that it can - for performing the drilling operations mentioned above - be embodied on a striking mechanism, the Tool insertion end can be rotated under the action of an additional rotating mechanism.
  • the object is achieved by a striking mechanism with the features of claim 1.
  • the solution underlying the invention is to act via a pressure control element on the control switching the percussion piston movement in such a way that the reversal from the return stroke to the working stroke movement takes place at a later point in time if the pressure force transmitted from the insertion end to the pressure control element is greater than that Restoring force acting in the direction of impact:
  • the increase in the pressing force beyond the size of the restoring force therefore has the result that the stroke of the impact piston is increased by the control of the associated shifting of the pressing control element against the direction of impact via the control; associated with this is a drop in the number of strokes and an increase in the individual impact energy.
  • the pressure control element can be displaced depending on the size of the pressure force in relation to that of the restoring force between two working positions; these result in a different effect of the switching element influencing the control, which can be actuated via a control line.
  • the two working positions are (at least temporarily) determined by the position of the insertion end or by the position of a fixed stop.
  • the pressure control element is designed as an adjusting nozzle with an annular surface oriented in the working stroke direction and acted on via the pressure line and a separate annular groove, which on the Junction of the control line and - depending on the position of the adjusting sleeve with respect to the stop - either at the junction of the pressure line or the return line.
  • the adjusting sleeve (depending on the further embodiment of the subject matter of the invention) is at least temporarily held in contact with the insertion end. If the adjustment sleeve is displaced, a connection can alternately be established via the annular groove between the pressure line or the return line and the control line, as a result of which the switching element (or shut-off valve or the adjustment piston) is actuated in a suitable manner.
  • the pressure control element of the control line, on the one hand, and the return line, which is kept depressurized, and the pressure line which is pressurized with the working pressure in the operating state, on the other hand, is assigned and designed in such a way that the control line is connected to the return line if the pressure control element (contrary to the effect of the reset) on the stop is present (claim 2).
  • the control line is therefore connected to the pressure line if the pressure control element (due to the restoring force exceeding the pressure force) only (at least temporarily) is held in contact at the insertion end.
  • the restoring force acting on the pressure control element can be generated in any way - for example by means of a mechanical spring element.
  • An advantageous embodiment of the subject matter of the invention is characterized in that the pressure control element has a holding surface which is effective in the working stroke direction and is connected to the pressure line (claim 3); in this case the reset works hydraulically.
  • the invention can be further developed in such a way that the percussion piston in the percussion mechanism housing is assigned a changeover channel opening into the percussion piston bore, under the influence of which, depending on the position of the percussion piston, the control is switched to its working stroke position during its return stroke.
  • At least one additional channel can be connected to the switching channel by means of the switching element (claim 4). So if the pressure force is greater than the restoring force, the at least one additional channel is blocked against the changeover channel under the influence of the switching element, with the result that the control only switches to the working stroke position at the next possible time and the percussion piston accordingly executes the greatest possible stroke.
  • the range of motion of the pressure control element is expediently dimensioned to be smaller than that of the insertion end in the direction of the percussion piston axis (claim 5).
  • the freedom of movement of the pressure control element in the working stroke direction of the percussion piston is limited by a counter bearing, with respect to which the insertion end can be moved back and forth in the direction of its longitudinal extent (claim 6).
  • the size of the range of motion results from the function of the pressure control element, which must be able to alternately connect the control line for the switching element to the pressure line or the return line.
  • the switching element can be designed as a spring-loaded shut-off valve, the closing body of which can be moved into an opening or blocking position with respect to the additional channel (claim 7).
  • the shut-off valve must be designed and switched such that its closing body assumes the blocking position if the pressure control element bears against the stationary stop under the action of the pressure force.
  • the switching element is designed as a spring-loaded adjusting piston, via which, depending on the size of the pressurization, at least one additional channel is connected to the return line in addition to the switching channel (claim 8);
  • the advantage achieved with the use of an adjusting piston is that - depending on the size of the pressure force acting on the adjusting piston - several additional channels can be switched on and off in succession.
  • the pressure line and the control line are equipped with damping throttles (claim 9); these are preferably located in the vicinity of their openings in the area of the pressure control element.
  • the adjusting sleeve - enclosing the percussion piston on part of its longitudinal extent - is guided in the longitudinal direction in the percussion mechanism housing (claim 10).
  • DE-OS 26 54 200 discloses the use of an adjusting sleeve which is movable within a striking mechanism housing and which is temporarily supported on the tool insertion end and which surrounds the striking piston over part of its longitudinal extent.
  • the adjusting sleeve which controls itself in terms of its position, is used exclusively to dampen the vibrations occurring in the tool.
  • the impact rotary drilling apparatus shown as an example has, as main components, an impact mechanism 1 with an impact mechanism housing 2, a percussion piston 3 which can be reciprocated therein and a control 4, and a rotating mechanism 5 with a rotating mechanism housing 6, which - composed of the components 6a and 6b - via the the latter component is flanged to the striking mechanism housing 2.
  • a hydraulic motor 7 is fastened to the component 6b, with which a hydraulic motor 7 in supported drive pinion 8 can be driven in both directions of rotation.
  • the slewing gear housing further receives - supported on two axial bearings 9 and 10 - a counter bearing 11 designed as a gearwheel, in whose toothing 11a the drive pinion 8 engages.
  • a tool insertion end 12 for a drilling tool, not shown, is movably connected to the counter bearing 11 via a torque connection in the form of a spline profile 12a; the possibility of movement of the insertion end with respect to the slewing gear housing 6 and the counter bearing 11 is limited by a paragraph 12b.
  • the insertion end 12, set in rotation under the action of the hydraulic motor 7, the drive pinion 8 and the counter bearing 11, transmits the single impact energy generated by the percussion piston 3 to the drilling tool, not shown; the percussion piston tip 3a and the impact surface 12c interacting therewith are exposed to considerable stress.
  • the percussion mechanism housing 2 there are three spaces separated from each other by the percussion piston, namely (as viewed in sequence from the percussion piston tip 3a) a pressure space 13, a reversing space 14 and a space 15 into which the rear end of the percussion piston 3b protrudes more or less.
  • the latter space is kept depressurized in the illustrated embodiment; if necessary, however, it can also be filled with compressed gas.
  • the striking mechanism housing 2 is equipped with two sealing elements 16 in the area between the rooms 14 and 15.
  • the range of motion of the percussion piston 3 with respect to the percussion mechanism housing is limited by an annular projection 3c located in the pressure space 13, which is located on the end of the percussion piston 3b facing side merges into a narrower cylinder section 3d.
  • the annular projection 3c On the side facing the percussion piston tip 3a, the annular projection 3c has a truncated cone section 3e, which enables the formation of a pressure cushion that brakes the percussion piston movement.
  • the diameter of the cylinder section 3d is designed such that it may block off the bore section 17 against the pressure chamber 13, which adjoins the former in the direction of the piston end 3b.
  • the percussion piston 3 is pressurized under the action of the known control 4 in such a way that it alternately executes a working stroke in the direction of impact (arrow 18) or a return stroke in the opposite direction (arrow 19).
  • the control essentially consists of a control slide 20 with a through bore 20a, which is held in a cylinder chamber 21 so that it can be pushed back and forth in the longitudinal direction and via this with a pressure line 22 and via its extension 22a (following the control 4) with the pressure chamber 13 communicates; the pressure line 22 is acted upon by a pressure oil source (not shown) during operation with the working pressure p S provided for the striking mechanism 1.
  • the reversing chamber 14 can be connected via a reversing duct 23, the cylinder chamber 21 and a connecting duct 24 to a pressure-free return line 25 or via the components 23 and 21 to the pressure line 22.
  • the pressurization of the percussion piston 3 is such that its smaller, the Return stroke surface 3f causing the return stroke movement is continuously subjected to working pressure in the operating state via the pressure line 22, 22a.
  • the larger working stroke surface 3g of the percussion piston triggering the working stroke is only temporarily subjected to working pressure via the reversing chamber 14 if the control slide 20 moves (by executing a movement to the left) into the other working stroke position (not shown).
  • This movement of the control slide has the result that the connection between the channels 23 and 24 is interrupted by the section 20b and at the same time the reversing channel 23 is connected to the pressure line 22.
  • the control slide 20 is dimensioned with regard to the size of its two end faces 20c, 20d and the further two ring faces in such a way that it assumes the return stroke position shown in FIG. 1, as long as the ring face 20e adjacent to the end face 20c (as shown in the drawing) via a changeover channel 26 ) is pressurized; the switching channel 26 - which, according to the illustration, is connected to the pressure chamber 13 via the bore section 17 - also merges into a switching channel 27, which has an annular groove 27a on the side facing the percussion piston 3.
  • the area of the percussion piston 3 on the cylinder section 3d is formed with a continuous annular groove 3h, via which the control 4 is switched to the working stroke position during the return stroke.
  • the control slide 20 moves to the left with the already mentioned consequence that the working stroke of the percussion piston 3 is triggered in the direction of arrow 18 by the reversing chamber 14 being subjected to the working pressure.
  • the additional channel is connected to the changeover channel 26 with the interposition of a switching element in the form of a spring-loaded shut-off valve 30; the operation of the shut-off valve will be explained in detail below.
  • the impact rotary drilling device is further equipped with a pressure control element in the form of an adjusting sleeve 31; this is movably supported in the longitudinal direction on the one hand on the percussion piston 3 and on the other hand temporarily on the impact surface 12c of the insertion end 12.
  • a pressure control element in the form of an adjusting sleeve 31; this is movably supported in the longitudinal direction on the one hand on the percussion piston 3 and on the other hand temporarily on the impact surface 12c of the insertion end 12.
  • sealing elements 32 and 33 held in the adjusting sleeve or in the percussion mechanism housing are provided.
  • the range of motion of the adjusting sleeve is determined by the distance between the counter bearing 11 and a fixed stop surface 34 in the striking mechanism housing 2 and (in the longitudinal direction of the adjusting sleeve) 31) denoted by b.
  • the adjusting sleeve 31 has an annular surface 31a oriented in the working stroke direction (arrow 18) and an annular groove 31b separated therefrom.
  • the latter is designed and arranged in such a way that it connects a control line 35 connected to the shut-off valve 30 - depending on the position of the adjusting sleeve - alternately either to the extension 22a of the pressure line 22 or to the return line 25.
  • the annular surface 31a is continuously subjected to working pressure in the operating state via the extension 22a; in this way, an effective holding force is generated in the working stroke direction (arrow 18), under whose action the adjusting sleeve 31 (depending on the respective position of the insertion end 12) is held in contact with the insertion end or with the counter bearing 11.
  • the adjusting sleeve 31 is pressed under the action of the insertion end 12 against the stop surface 34 with the result that the control line 35 via the annular groove 31b and the return line 25 is kept depressurized. If the size of the restoring force R exceeds that of the pressing force A (FIG. 2), the adjusting sleeve 31 bears on the middle against the counter bearing 11; as a result, the control line 35 is acted upon via the annular groove 31b and the extension 22a with the working pressure p S ; at the same time the connection between the annular groove and the return line 25 is interrupted.
  • At least one relief groove 31c is provided on the side facing the stop surface 34; the environment of the Stop surface 34 is also relieved of pressure via a return channel 36 which opens into the return line 25.
  • the range of motion b of the adjusting sleeve 31 parallel to the longitudinal direction of the percussion piston 3 and the insertion end 12 is dimensioned considerably smaller than the range of motion of the insertion end within the rotating mechanism housing 6.
  • the shut-off valve 30 (cf. in particular FIG. 3) has an adjusting piston 30a, which is supported within a cylinder bore 37 on a prestressed return spring 38 and merges into a pin-like closing body 30b on the side facing the percussion piston 3.
  • the cylinder bore 37 is relieved of pressure via a leakage channel 39; this can be connected, for example, to the return line 25 shown in FIG. 1.
  • the valve piston 30a In the rest position shown in FIG. 3, the valve piston 30a is supported on a stop surface 35b under the action of the prestressed return spring 38. As long as the pressure applied to the valve piston 30a via the annular groove 35a from the control line 35 is less than the pretensioning force emanating from the return spring 38, the closing body 30b engages in the additional channel 29 and blocks it from the return channel 27: the additional channel 29 is thus in With regard to influencing the control 4 (see, for example, FIG. 1) ineffective.
  • the above-mentioned rest position of the shut-off valve 30 corresponds to the operating state shown in FIG. 1, in which the adjusting sleeve 31 abuts the stop surface 34 on average and connects the control line 35 to the return line 25.
  • the area of the striking mechanism housing 2 between the sealing elements 16 is relieved of pressure by means of the return channel 27, which opens into the return line 25.
  • the switching element for influencing the control 4 is designed as an adjusting piston 41 which, contrary to the action of a return spring 42, is displaceable within a cylinder space 43.
  • the rest position of the adjusting piston 41 is in turn due to the mentioned abutment surface 35b set.
  • the return channel 27 is connected to the return line 25 via an annular recess 41a together with a bore 41b and an extension 40a of the leakage channel 40. It is assigned two additional channels 44, 45 in the direction of the percussion piston tip 3a, which - depending on the pressurization of the adjusting piston and the resulting working position - may be opposite the annular recess 41a and thus become effective with regard to influencing the control 4.
  • the adjusting sleeve 31 bears against the stop surface 34, so that the control line 35 is relieved of pressure via the annular groove 31b and the return line 25. If the adjusting sleeve moves to the left against the action of the pressing force A, the adjusting piston 41 performs a correspondingly directed movement against the action of the return spring 42, in the course of which - depending on the pressurization via the control line 35 - either only the additional channel 44 or also the additional channel 45 is gripped by the ring recess 41a. The controller 4 is accordingly switched to the working stroke position if the annular groove 3h connects the additional channel 45 or the additional channel 44 to the switching channel 26.
  • the embodiment in question thus allows the operation of the rotary impact drilling device to be adapted in more than two stages to the changing size of the pressing force A transmitted by the insertion end 12.
  • the lines 22a and 35 are equipped with damping chokes 46, 47 in the vicinity of their openings in the area of the adjusting sleeve 31.
  • the advantage achieved by the invention is in particular that the number of blows and Single impact energy automatically sets depending on the size of the pressure force acting on a measuring element (adjusting sleeve).
  • the associated components are - with the saving of special supply and control lines - part of the percussion drilling device itself. Monitoring of the functioning of the percussion drilling device by an operator can therefore be dispensed with.
  • the invention is of course also applicable to devices which only have a hydraulically operated striking mechanism and whose tool insertion end is accordingly held back and forth only in the longitudinal direction of the striking mechanism housing.

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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)
  • Electrophonic Musical Instruments (AREA)

Abstract

The object of the invention is to configure a percussion mechanism in such a way that the number of blows - and hence the return stroke and the individual impact energy of the percussion piston - is matched automatically to changing working conditions via an internal control system as a function of the contact pressure on the tool insertion end. <??>For this purpose the invention proposes to hold a contact-pressure control element (31) at least temporarily in contact with the insertion end (12) under the action of a resetting arrangement (31a, 22) acting in the striking direction (arrow 18) and, via this contact-pressure control element, to connect a control conduit (35) either to a pressure conduit (22) or to a balanced return conduit (25). <??>Via the control conduit, a switching element (30) can be actuated in such a way that the control device (4) alternately switching over the movement of the piston performs the reversing movement into the working-stroke position at an earlier or later point in time during the return stroke (arrow 19) of the percussion piston, thereby triggering the working stroke of the percussion piston in the striking direction. <IMAGE>

Description

Die Erfindung betrifft ein hydraulisch betriebenes Schlagwerk gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a hydraulically operated hammer mechanism according to the preamble of claim 1.

Insbesondere beim Gesteins- und Ankerbohren werden vor allem während der Andruckphase, mit Rücksicht auf normalerweise ungünstige Ansatzbedingungen (beispielsweise schrägverlaufende und/oder zerklüftete Oberflächen) für das Bohrwerkzeug (Bohrkrone), hohe Schlagzahlen in Verbindung mit einer niedrigen Einzelschlagenergie und geringer Andruckkraft benötigt. Nach dem Zentrieren des Bohrwerkzeugs ist es zur Erzielung eines optimalen Bohrfortschritts erforderlich, das Schlagwerk bei gleichzeitiger Erhöhung der Einzelschlagenergie und der Andruckkraft auf eine geringe Schlagzahl umzuschalten.
Ein entsprechender Regelvorgang sollte ablaufen, falls weichere Schichten (beispielsweise Lehm) oder Hohlräume durchbohrt werden.
Especially when drilling rock and anchor, especially during the pressure phase, taking into account normally unfavorable starting conditions (e.g. sloping and / or jagged surfaces) for the drilling tool (core bit), high impact rates in connection with low single impact energy and low pressure force are required. After centering the drilling tool, to achieve optimal drilling progress, it is necessary to switch the hammer mechanism to a low number of strokes while increasing the individual impact energy and the pressing force.
A corresponding control process should take place if softer layers (e.g. clay) or cavities are pierced.

Zur Anpassung an sich ändernde Arbeitsverhältnisse ist bereits der Vorschlag unterbreitet worden, bei einem druckmittelbetriebenen Schlagwerk die Schlagfrequenz durch einen von außen zugeleiteten Steuerdruck zu beeinflussen (DE-PS 26 58 455). Dabei ist es denkbar, den Steuerdruck in Abhängigkeit vom Betriebsdruck der die Andruckkraft erzeugenden Andruckeinheit, in Abhängigkeit vom Arbeitsdruck eines etwa vorhandenen Drehwerks oder über eine von Hand einzustellende Druckzuführung zu beeinflussen.In order to adapt to changing employment relationships, the proposal has already been made to influence the stroke frequency in a pressure medium-operated striking mechanism by a control pressure supplied from outside (DE-PS 26 58 455). It is conceivable to control the control pressure as a function of the operating pressure of the pressure unit generating the pressure force, as a function of the working pressure of an existing rotating mechanism or influenced by a pressure feed that can be adjusted by hand.

Aus der Druckschrift EP-A2-0 080 446 ist ein Schlagwerk der eingangs erwähnten Gattung bekannt, welches es ermöglichen soll, die Schlagenergie besser als bisher auszunutzen; dies soll dadurch geschehen, daß die Schlagzahl in Abhängigkeit von den reflektierten Stoßwellen derart verändert wird, daß deren Energie möglichst gering ist.
Zu diesem Zweck ist das bekannte Schlagwerk mit einem Dämpfungskolben ausgestattet, welcher eine Steuerleitung blockiert, solange keine reflektierten Stoßwellen auf ihn einwirken, und dadurch den Hub des Schlagkolbens in Schlagrichtung verkleinert. Sobald der Dämpfungskolben unter der Einwirkung reflektierter Stoßwellen Rückprallbewegungen ausführt, wird die Veränderung der Größe des Schlagkolbenhubes unterbrochen, so daß sich eine den Gegebenheiten angepaßte Größe des Schlagkolbenhubes einstellt.
From the publication EP-A2-0 080 446 a percussion mechanism of the type mentioned at the outset is known, which should make it possible to make better use of the impact energy than before; this should be done by changing the number of blows in dependence on the reflected shock waves in such a way that their energy is as low as possible.
For this purpose, the known percussion mechanism is equipped with a damping piston which blocks a control line as long as no reflected shock waves act on it, thereby reducing the stroke of the percussion piston in the direction of impact. As soon as the damping piston makes rebound movements under the action of reflected shock waves, the change in the size of the percussion piston stroke is interrupted, so that a size of the percussion piston stroke adjusted to the circumstances is established.

Der Erfindung liegt die Aufgabe zugrunde, ein hydraulisch betriebens Schlagwerk in der Weise auszugestalten, daß die Schlagzahl in Abhängigkeit von der Andruckkraft durch eine interne Regelung im Schlagwerk selbst, d.h. auf kürzestem Weg, anpassbar ist und dementsprechend außerhalb des Schlagwerks auftretende Störungen, durch längere Leitungswege bedingte Verzögerungen bei der Impuls- bzw. Signalübermittlung oder eine Fehlsteuerung durch die Bedienungsperson ausgeschlossen werden. Die Erfindung soll dabei so ausgestaltet sein, daß sie - zur Durchführung der eingangs erwähnten Bohrvorgänge - auch an einem Schlagwerk verkörpert sein kann, dessen Werkzeug-Einsteckende unter Einwirkung eines zusätzlich vorhandenen Drehwerks in Drehung versetzt werden kann.The invention has for its object to design a hydraulically operated striking mechanism in such a way that the number of blows depending on the pressure force by an internal control in the striking mechanism itself, ie by the shortest route, can be adjusted and, accordingly, faults occurring outside the striking mechanism, by longer cable routes Conditional delays in the transmission of impulses or signals or incorrect control by the operator can be excluded. The invention should be designed so that it can - for performing the drilling operations mentioned above - be embodied on a striking mechanism, the Tool insertion end can be rotated under the action of an additional rotating mechanism.

Die Aufgabe wird durch ein Schlagwerk mit den Merkmalen des Anspruchs 1 gelöst. Der der Erfindung zugrundeliegende Lösungsgedanke besteht darin, über ein Andrucksteuerelement auf die die Schlagkolbenbewegung umschaltende Steuerung derart einzuwirken, daß die Umsteuerung von der Rückhub- auf die Arbeitshubbewegung zu einem späteren Zeitpunkt erfolgt, falls die von dem Einsteckende auf das Andrucksteuerelement übertragene Andruckraft größer ist als die in Schlagrichtung wirkende Rückstellkraft: Der Anstieg der Andruckkraft über die Größe der Rückstellkraft hinaus hat also zur Folge, daß durch die damit verbundene Verschiebung des Andrucksteuerelements entgegen der Schlagrichtung über die Steuerung der Hub des Schlagkolbens vergrößert wird; damit verbunden sind ein Absinken der Schlagzahl und eine Erhöhung der Einzelschlagenergie.
Das Andrucksteuerelement ist in Abhängigkeit von der Größe der Andruckkraft im Verhältnis zu derjenigen der Rückstellkraft zwischen zwei Arbeitsstellungen veschiebbar; diese haben eine unterschiedliche Wirkung des die Steuerung beeinflussenden Schaltelements zur Folge, welches über eine Steuerleitung betätigbar ist. Die beiden Arbeitsstellungen sind (zumindest zeitweilig) durch die Lage des Einsteckendes bzw. durch die Lage eines ortsfesten Anschlags festgelegt.
Das Andrucksteuerelement ist dabei als Verstelldüse mit einer in Arbeitshubrichtung ausgerichteten, über die Druckleitung beaufschlagten Ringfläche und einer davon getrennten Ringnut ausgebildet, welche an der Einmündung der Steuerleitung und - abhängig von der Lage der Verstellhülse bezüglich des Anschlags - entweder an der Einmündung der Druckleitung oder der Rücklaufleitung liegt. Mittels der an der Ringfläche angreifenden Rückstellkraft wird die Verstellhülse (abhängig von der weiteren Ausgestaltung des Erfindungsgegenstandes) zumindest zeitweilig an dem Einsteckende in Anlage gehalten. Über die Ringnut läßt sich bei einer Verschiebung der Verstellhülse ggf. wechselweise eine Verbindung zwischen der Druckleitung bzw. der Rücklaufleitung und der Steuerleitung herstellen, wodurch das Schaltelement (bzw. Absperrventil bzw. der Verstellkolben) in geeigneter Weise betätigt wird.
The object is achieved by a striking mechanism with the features of claim 1. The solution underlying the invention is to act via a pressure control element on the control switching the percussion piston movement in such a way that the reversal from the return stroke to the working stroke movement takes place at a later point in time if the pressure force transmitted from the insertion end to the pressure control element is greater than that Restoring force acting in the direction of impact: The increase in the pressing force beyond the size of the restoring force therefore has the result that the stroke of the impact piston is increased by the control of the associated shifting of the pressing control element against the direction of impact via the control; associated with this is a drop in the number of strokes and an increase in the individual impact energy.
The pressure control element can be displaced depending on the size of the pressure force in relation to that of the restoring force between two working positions; these result in a different effect of the switching element influencing the control, which can be actuated via a control line. The two working positions are (at least temporarily) determined by the position of the insertion end or by the position of a fixed stop.
The pressure control element is designed as an adjusting nozzle with an annular surface oriented in the working stroke direction and acted on via the pressure line and a separate annular groove, which on the Junction of the control line and - depending on the position of the adjusting sleeve with respect to the stop - either at the junction of the pressure line or the return line. By means of the restoring force acting on the ring surface, the adjusting sleeve (depending on the further embodiment of the subject matter of the invention) is at least temporarily held in contact with the insertion end. If the adjustment sleeve is displaced, a connection can alternately be established via the annular groove between the pressure line or the return line and the control line, as a result of which the switching element (or shut-off valve or the adjustment piston) is actuated in a suitable manner.

Vorzugsweise ist das Andrucksteuerelement der Steuerleitung einerseits sowie der drucklos gehaltenen Rücklaufleitung und der im Betriebszustand mit dem Arbeitsdruck beaufschlagten Druckleitung andererseits derart zugeordnet und derart ausgebildet, daß die Steuerleitung an die Rücklaufleitung angeschlossen ist, falls das Andrucksteuerelement (entgegen der Wirkung der Rückstellung) an dem Anschlag anliegt (Anspruch 2). Im Rahmen des erfindungsgemäßen Lösungsvorschlags ist es jedoch auch möglich, die von der Arbeitsstellung des Andruckelements ausgehende Wirkung umzukehren: Bei einer derartigen Ausführungsform ist also die Steuerleitung an die Druckleitung angeschlossen, falls das Andrucksteuerelement (aufgrund der die Andruckkraft übersteigenden Rückstellkraft) lediglich (zumindest zeitweilig) an dem Einsteckende in Anlage gehalten ist.Preferably, the pressure control element of the control line, on the one hand, and the return line, which is kept depressurized, and the pressure line which is pressurized with the working pressure in the operating state, on the other hand, is assigned and designed in such a way that the control line is connected to the return line if the pressure control element (contrary to the effect of the reset) on the stop is present (claim 2). Within the scope of the proposed solution according to the invention, however, it is also possible to reverse the effect emanating from the working position of the pressure element: in such an embodiment, the control line is therefore connected to the pressure line if the pressure control element (due to the restoring force exceeding the pressure force) only (at least temporarily) is held in contact at the insertion end.

Die an dem Andrucksteuerelement angreifende Rückstellkraft kann auf beliebige Weise - beispielsweise mittels eines mechanischen Federelements - erzeugt werden.
Eine vorteilhafte Ausgestaltung des Erfindungsgegenstandes ist dadurch gekennzeichnet, daß das Andrucksteuerelement eine in Arbeitshubrichtung wirksame Haltefläche aufweist, die mit der Druckleitung in Verbindung steht (Anspruch 3); die Rückstellung arbeitet in diesem Fall also hydraulisch.
The restoring force acting on the pressure control element can be generated in any way - for example by means of a mechanical spring element.
An advantageous embodiment of the subject matter of the invention is characterized in that the pressure control element has a holding surface which is effective in the working stroke direction and is connected to the pressure line (claim 3); in this case the reset works hydraulically.

Die Erfindung kann in der Weise weitergehend ausgestaltet sein, daß dem Schlagkolben im Schlagwerkgehäuse ein in dessen Schlagkolbenbohrung einmündender Umschaltkanal zugeordnet ist, unter dessen Einwirkung abhängig von der Stellung des Schlagkolbens während dessen Rückhub die Steuerung in ihre Arbeitshubstellung umgeschaltet wird. An den Umschaltkanal kann mittels des Schaltelements zumindest ein Zusatzkanal angeschlossen werden (Anspruch 4).
Falls also die Andruckkraft größer ist als die Rückstellkraft, ist der zumindest eine Zusatzkanal unter Einwirkung des Schaltelements gegen den Umschaltkanal abgesperrt mit der Folge, daß die Steuerung erst zum nächstmöglichen Zeitpunkt in die Arbeitshubstellung umschaltet und der Schlagkolben dementsprechend den größtmöglichen Hub ausführt.
The invention can be further developed in such a way that the percussion piston in the percussion mechanism housing is assigned a changeover channel opening into the percussion piston bore, under the influence of which, depending on the position of the percussion piston, the control is switched to its working stroke position during its return stroke. At least one additional channel can be connected to the switching channel by means of the switching element (claim 4).
So if the pressure force is greater than the restoring force, the at least one additional channel is blocked against the changeover channel under the influence of the switching element, with the result that the control only switches to the working stroke position at the next possible time and the percussion piston accordingly executes the greatest possible stroke.

Zweckmäßigerweise ist der Bewegungsspielraum des Andrucksteuerelements kleiner bemessen als derjenige des Einsteckendes in Richtung der Schlagkolbenachse (Anspruch 5).The range of motion of the pressure control element is expediently dimensioned to be smaller than that of the insertion end in the direction of the percussion piston axis (claim 5).

Allgemein ist der Bewegungsspielraum des Andrucksteuerelements in Arbeitshubrichtung des Schlagkolbens durch ein Gegenlager begrenzt, bezüglich dem das Einsteckende in Richtung seiner Längserstreckung hin- und herbeweglich ist (Anspruch 6).
Die Größe des Bewegungsspielraums ergibt sich dabei aus der Funktion des Andrucksteuerelements, welches in der Lage sein muß, die Steuerleitung für das Schaltelement wechselweise an die Druckleitung oder die Rücklaufleitung anzuschließen.
In general, the freedom of movement of the pressure control element in the working stroke direction of the percussion piston is limited by a counter bearing, with respect to which the insertion end can be moved back and forth in the direction of its longitudinal extent (claim 6).
The size of the range of motion results from the function of the pressure control element, which must be able to alternately connect the control line for the switching element to the pressure line or the return line.

Falls der Erfindungsgegenstand lediglich einen Zusatzkanal aufweist, kann das Schaltelement als federbelastetes Absperrventil ausgebildet sein, dessen Schließkörper bezüglich des Zusatzkanals in eine Öffnungs- bzw. Sperrstellung bewegt werden kann (Anspruch 7).
Das Absperrventil muß derart ausgebildet und geschaltet sein, daß sein Schließkörper die Sperrstellung einnimmt, falls das Andrucksteuerelement unter Einwirkung der Andruckkraft an dem ortsfesten Anschlag anliegt. Bei einer andersartigen Ausführungsform des Erfindungsgegenstandes ist das Schaltelement als federbelasteter Verstellkolben ausgebildet, über den - abhängig von der Größe der Druckbeaufschlagung - neben dem Umschaltkanal ggf. zumindest ein Zusatzkanal an die Rücklaufleitung angeschlossen wird (Anspruch 8); der mit der Verwendung eines Verstellkolbens erzielte Vorteil besteht darin, daß sich - abhängig von der Größe der auf den Verstellkolben einwirkenden Druckkraft - mehrere Zusatzkanäle nacheinander zu- und abschalten lassen.
If the subject matter of the invention has only one additional channel, the switching element can be designed as a spring-loaded shut-off valve, the closing body of which can be moved into an opening or blocking position with respect to the additional channel (claim 7).
The shut-off valve must be designed and switched such that its closing body assumes the blocking position if the pressure control element bears against the stationary stop under the action of the pressure force. In a different embodiment of the subject matter of the invention, the switching element is designed as a spring-loaded adjusting piston, via which, depending on the size of the pressurization, at least one additional channel is connected to the return line in addition to the switching channel (claim 8); the advantage achieved with the use of an adjusting piston is that - depending on the size of the pressure force acting on the adjusting piston - several additional channels can be switched on and off in succession.

Um unerwünschte Druckstöße im Bereich des Andrucksteuerelements und des Schaltelements nach Mögichkeit zu vermeiden, sind die Druckleitung und die Steuerleitung mit Dämpfungsdrosseln ausgestattet (Anspruch 9); diese befinden sich vorzugsweise in der Nähe ihrer Einmündungen in den Bereich des Andrucksteuerelements.In order to avoid undesirable pressure surges in the area of the pressure control element and the switching element, the pressure line and the control line are equipped with damping throttles (claim 9); these are preferably located in the vicinity of their openings in the area of the pressure control element.

Vorzugsweise ist die Verstellhülse - den Schlagkolben auf einem Teil seiner Längserstreckung umschließend - in Längsrichtung beweglich in dem Schlagwerkgehäuse geführt (Anspruch 10).
Die Verwendung einer innerhalb eines Schlagwerkgehäuses beweglichen Verstellhülse, die sich zeitweilig am Werkzeug-Einsteckende abstützt und den Schlagkolben auf einem Teil seiner Längserstreckung umschließt, ist aus der DE-OS 26 54 200 bekannt. Die sich hinsichtlich ihrer Lage selbst aussteuernde Verstellhülse dient jedoch ausschließlich dazu, die im Werkzeug auftretenden Schwingungen zu dämpfen.
Preferably, the adjusting sleeve - enclosing the percussion piston on part of its longitudinal extent - is guided in the longitudinal direction in the percussion mechanism housing (claim 10).
DE-OS 26 54 200 discloses the use of an adjusting sleeve which is movable within a striking mechanism housing and which is temporarily supported on the tool insertion end and which surrounds the striking piston over part of its longitudinal extent. However, the adjusting sleeve, which controls itself in terms of its position, is used exclusively to dampen the vibrations occurring in the tool.

Die Erfindung wird nachfolgend anhand mehrerer in der Zeichnung dargestellter Ausführungsbeispiele erläutert, die sich auf Schlagdrehbohrvorrichtungen - bestehend aus Schlagwerk nebst Drehwerk - beziehen.
Es zeigen:

Fig. 1
stark schematisiert einen Teilschnitt durch eine Schlagdrehbohrvorrichtung für den Fall, daß die auf das Werkzeug-Einsteckende einwirkende Andruckkraft größer ist als eine von einer Verstellhülse ausgehende, entgegengerichtete Rückstellkraft,
Fig. 2
einen Teilschnitt gemäß Fig. 1 für den Fall, daß die von der Verstellhülse ausgehende Rückstellkraft größer ist als die am Werkzeug-Einsteckende angreifende Andruckkraft,
Fig. 3
in gegenüber Fig. 1 vergrößertem Maßstab einen Teilschnitt im Bereich des als Absperrventil ausgebildeten Schaltelements und
Fig. 4
einen Teilschnitt durch eine Schlagdrehbohrvorrichtung mit einem als Verstellkolben ausgebildeten Schaltelement.
The invention is explained below on the basis of several exemplary embodiments shown in the drawing, which relate to percussion rotary drilling devices - consisting of percussion mechanism and rotating mechanism - Respectively.
Show it:
Fig. 1
highly schematic a partial section through a rotary impact drilling device in the event that the pressing force acting on the tool insertion end is greater than a counter-acting restoring force originating from an adjusting sleeve,
Fig. 2
1 for the case that the restoring force emanating from the adjusting sleeve is greater than the pressing force acting on the tool insertion end,
Fig. 3
on a larger scale compared to FIG. 1, a partial section in the area of the switching element designed as a shut-off valve and
Fig. 4
a partial section through a rotary impact drilling device with a switching element designed as an adjusting piston.

Die beispielhaft dargestellte Schlagdrehbohrvorrichtung weist als Hauptbestandteile ein Schlagwerk 1 mit einem Schlagwerkgehäuse 2, einem in diesem hin- und herbeweglichen Schlagkolben 3 und einer Steuerung 4 sowie ein Drehwerk 5 mit einem Drehwerkgehäuse 6 auf, das - zusammengesetzt aus den Bestandteilen 6a und 6b - über den letztgenannten Bestandteil an das Schlagwerkgehäuse 2 angeflanscht ist.
An dem Bestandteil 6b ist ein Hydraulikmotor 7 befestigt, mit dem ein im Drehwerkgehäuse 6 abgestütztes Antriebsritzel 8 in beiden Drehrichtungen angetrieben werden kann. Das Drehwerkgehäuse nimmt weiterhin - abgestützt an zwei Achsiallagern 9 und 10 - ein als Zahnrad ausgebildetes Gegenlager 11 auf, in dessen Verzahnung 11a das Antriebsritzel 8 eingreift.
Mit dem Gegenlager 11 ist über eine Drehmomentverbindung in Form eines Keilwellenprofils 12a ein Werkzeug-Einsteckende 12 für ein nicht dargestelltes Bohrwerkzeug in axialer Richtung beweglich verbunden; die Bewegungsmöglichkeit des Einsteckendes bezüglich des Drehwerkgehäuses 6 und des Gegenlagers 11 ist durch einen Absatz 12b begrenzt. Das unter Einwirkung des Hydraulikmotors 7, des Antriebsritzels 8 und des Gegenlagers 11 in Drehung versetzte Einsteckende 12 überträgt die vom Schlagkolben 3 erzeugte Einzelschlagenergie auf das nicht dargestellte Bohrwerkzeug; die Schlagkolbenspitze 3a und die mit dieser zusammenwirkende Aufschlagfläche 12c sind dabei einer erheblichen Beanspruchung ausgesetzt.
The impact rotary drilling apparatus shown as an example has, as main components, an impact mechanism 1 with an impact mechanism housing 2, a percussion piston 3 which can be reciprocated therein and a control 4, and a rotating mechanism 5 with a rotating mechanism housing 6, which - composed of the components 6a and 6b - via the the latter component is flanged to the striking mechanism housing 2.
A hydraulic motor 7 is fastened to the component 6b, with which a hydraulic motor 7 in supported drive pinion 8 can be driven in both directions of rotation. The slewing gear housing further receives - supported on two axial bearings 9 and 10 - a counter bearing 11 designed as a gearwheel, in whose toothing 11a the drive pinion 8 engages.
A tool insertion end 12 for a drilling tool, not shown, is movably connected to the counter bearing 11 via a torque connection in the form of a spline profile 12a; the possibility of movement of the insertion end with respect to the slewing gear housing 6 and the counter bearing 11 is limited by a paragraph 12b. The insertion end 12, set in rotation under the action of the hydraulic motor 7, the drive pinion 8 and the counter bearing 11, transmits the single impact energy generated by the percussion piston 3 to the drilling tool, not shown; the percussion piston tip 3a and the impact surface 12c interacting therewith are exposed to considerable stress.

Innerhalb des Schlagwerkgehäuses 2 sind voneinander durch den Schlagkolben getrennt drei Räume vorhanden, nämlich (in ihrer Aufeinanderfolge von der Schlagkolbenspitze 3a aus betrachtet) ein Druckraum 13, ein Umsteuerraum 14 und ein Raum 15, in den das rückwärtige Schlagkolbenende 3b mehr oder weniger hineinragt. Der letztgenannte Raum ist in dem dargestellten Ausführungsbeispiel drucklos gehalten; er kann ggf. jedoch auch mit Druckgas gefüllt sein.
Zur Abdichtung gegen die Umgebung ist das Schlagwerkgehäuse 2 im Bereich zwischen den Räumen 14 und 15 mit zwei Dichtelementen 16 ausgestattet. Der Bewegungsspielraum des Schlagkolbens 3 bezüglich des Schlagwerkgehäuses ist durch einen in dem Druckraum 13 liegenden Ringvorsprung 3c begrenzt, welcher auf der dem Schlagkolbenende 3b zugewandten Seite in einen schmaleren Zylinderabschnitt 3d übergeht. Auf der der Schlagkolbenspitze 3a zugewandten Seite weist der Ringvorsprung 3c einen Kegelstumpfabschnitt 3e auf, welcher die Bildung eines die Schlagkolbenbewegung abbremsenden Druckpolsters ermöglicht. Der Zylinderabschnitt 3d ist hinsichtlich seines Durchmessers derart ausgelegt, daß er ggf. den Bohrungsabschnitt 17 gegen den Druckraum 13 absperrt, der sich an ersteren in Richtung auf das Kolbenende 3b anschließt.
Within the percussion mechanism housing 2 there are three spaces separated from each other by the percussion piston, namely (as viewed in sequence from the percussion piston tip 3a) a pressure space 13, a reversing space 14 and a space 15 into which the rear end of the percussion piston 3b protrudes more or less. The latter space is kept depressurized in the illustrated embodiment; if necessary, however, it can also be filled with compressed gas.
For sealing against the environment, the striking mechanism housing 2 is equipped with two sealing elements 16 in the area between the rooms 14 and 15. The range of motion of the percussion piston 3 with respect to the percussion mechanism housing is limited by an annular projection 3c located in the pressure space 13, which is located on the end of the percussion piston 3b facing side merges into a narrower cylinder section 3d. On the side facing the percussion piston tip 3a, the annular projection 3c has a truncated cone section 3e, which enables the formation of a pressure cushion that brakes the percussion piston movement. The diameter of the cylinder section 3d is designed such that it may block off the bore section 17 against the pressure chamber 13, which adjoins the former in the direction of the piston end 3b.

Der Schlagkolben 3 wird unter Einwirkung der an sich bekannten Steuerung 4 derart druckbeaufschlagt, daß er wechselweise einen Arbeitshub in Schlagrichtung (Pfeil 18) oder einen Rückhub in dazu entgegengesetzter Richtung (Pfeil 19) ausführt.
Die Steuerung besteht im wesentlichen aus einem Steuerschieber 20 mit einer Durchgangsbohrung 20a, der in einer Zylinderkammer 21 in Längsrichtung hin- und herverschiebbar gehalten ist und über diese mit einer Druckleitung 22 sowie über deren Verlängerung 22a (im Anschluß an die Steuerung 4) mit dem Druckraum 13 in Verbindung steht; die Druckleitung 22 wird über eine nicht dargestellte Druckölquelle während des Betriebes mit dem für das Schlagwerk 1 vorgesehenen Arbeitsdruck pS beaufschlagt.
The percussion piston 3 is pressurized under the action of the known control 4 in such a way that it alternately executes a working stroke in the direction of impact (arrow 18) or a return stroke in the opposite direction (arrow 19).
The control essentially consists of a control slide 20 with a through bore 20a, which is held in a cylinder chamber 21 so that it can be pushed back and forth in the longitudinal direction and via this with a pressure line 22 and via its extension 22a (following the control 4) with the pressure chamber 13 communicates; the pressure line 22 is acted upon by a pressure oil source (not shown) during operation with the working pressure p S provided for the striking mechanism 1.

Abhängig von der Stellung des Steuerschiebers 20 innerhalb der Zylinderkammer 21 ist der Umsteuerraum 14 über einen Umsteuerkanal 23, die Zylinderkammer 21 und einen Verbindungskanal 24 an eine drucklos gehaltene Rücklaufleitung 25 bzw. über die Bestandteile 23 und 21 an die Druckleitung 22 anschließbar.Depending on the position of the control slide 20 within the cylinder chamber 21, the reversing chamber 14 can be connected via a reversing duct 23, the cylinder chamber 21 and a connecting duct 24 to a pressure-free return line 25 or via the components 23 and 21 to the pressure line 22.

Die Druckbeaufschlagung des Schlagkolbens 3 ist derart beschaffen, daß dessen kleinere, die Rückhubbewegung bewirkende Rückhubfläche 3f im Betriebszustand über die Druckleitung 22, 22a ständig mit Arbeitsdruck beaufschlagt ist. Im Gegensatz dazu wird die den Arbeitshub auslösende, größere Arbeitshubfläche 3g des Schlagkolbens über den Umsteuerraum 14 nur zeitweilig mit Arbeitsdruck beaufschlagt, falls der Steuerschieber 20 sich (durch Ausführen einer Bewegung nach links) in die andere, nicht dargestellte Arbeitshubstellung verschiebt. Diese Bewegung des Steuerschiebers hat zur Folge, daß durch den Abschnitt 20b die Verbindung zwischen den Kanälen 23 und 24 unterbrochen sowie gleichzeitig der Umsteuerkanal 23 an die Druckleitung 22 angeschlossen wird.The pressurization of the percussion piston 3 is such that its smaller, the Return stroke surface 3f causing the return stroke movement is continuously subjected to working pressure in the operating state via the pressure line 22, 22a. In contrast, the larger working stroke surface 3g of the percussion piston triggering the working stroke is only temporarily subjected to working pressure via the reversing chamber 14 if the control slide 20 moves (by executing a movement to the left) into the other working stroke position (not shown). This movement of the control slide has the result that the connection between the channels 23 and 24 is interrupted by the section 20b and at the same time the reversing channel 23 is connected to the pressure line 22.

Der Steuerschieber 20 ist hinsichtlich der Größe seiner beiden Stirnflächen 20c, 20d und der weiteren zwei Ringflächen derart bemessen, daß er die in Fig. 1 dargestellte Rückhubstellung einnimmt, solange über einen Umschaltkanal 26 die der Stirnfläche 20c benachbarte Ringfläche 20e (wie in der Zeichnung dargestellt) druckbeaufschlagt ist; der Umschaltkanal 26 - der gemaß der Darstellung über den Bohrungsabschnitt 17 mit dem Druckraum 13 in Verbindung steht - geht außerdem in einen Umschaltkanal 27 über, welcher auf der dem Schlagkolben 3 zugewandten Seite eine Ringnut 27a aufweist.
Der Bereich des Schlagkolbens 3 an dem Zylinderabschnitt 3d ist mit einer durchgehenden Ringnut 3h ausgebildet, über welche während des Rückhubes die Steuerung 4 in die Arbeitshubstellung umgeschaltet wird. Zu diesem Zweck ist im Bereich zwischen dem Bohrungsabschnitt 17 und dem Umschaltkanal 26 ein gegen den Schlagkolben 3 geöffneter Rücklaufkanal 27 vorhanden, der in die Rücklaufleitung 25 einmündet. Sobald - abhängig von der Stellung des Schlagkolbens - die Ringnut 3h die Ringnuten 26a und 27a miteinander verbindet und dadurch an die Rücklaufleitung 25 anschließt, führt dies zu einem Druckabfall auch im Umschaltkanal 26 (dessen Verbindung zum Druckraum 13 unter Einwirkung des Zylinderabschnitts 3d dann unterbrochen ist), über welchen die Ringfläche 20e des Steuerschiebers 20 bis dahin mit Arbeitsdruck beaufschlagt worden ist. Unter Einwirkung der nach Druckentlastung der Ringfläche 20e größeren Druckkraft an der Stirnfläche 20d verschiebt sich der Steuerschieber 20 nach links mit der bereits erwähnten Folge, daß durch Beaufschlagen des Umsteuerraums 14 mit dem Arbeitsdruck der Arbeitshub des Schlagkolbens 3 in Richtung des Pfeiles 18 ausgelöst wird.
Um die Arbeitsweise der Schlagdrehbohrvorrichtung selbsttätig an wechselnde Arbeitsbedingungen anpassen zu können, ist zwischen dem Rücklaufkanal 27 und dem Umschaltkanal 26 ein Zusatzkanal 29 vorhanden, dessen Ringnut 29a dem Schlagkolben 3 gegenüberliegt (vgl. dazu auch Fig. 3). Der Zusatzkanal steht unter Zwischenschaltung eines Schaltelements in Gestalt eines federbelasteten Absperrventils 30 mit dem Umschaltkanal 26 in Verbindung; die Wirkungsweise des Absperrventils wird nachfolgend noch im einzelnen erläutert werden.
The control slide 20 is dimensioned with regard to the size of its two end faces 20c, 20d and the further two ring faces in such a way that it assumes the return stroke position shown in FIG. 1, as long as the ring face 20e adjacent to the end face 20c (as shown in the drawing) via a changeover channel 26 ) is pressurized; the switching channel 26 - which, according to the illustration, is connected to the pressure chamber 13 via the bore section 17 - also merges into a switching channel 27, which has an annular groove 27a on the side facing the percussion piston 3.
The area of the percussion piston 3 on the cylinder section 3d is formed with a continuous annular groove 3h, via which the control 4 is switched to the working stroke position during the return stroke. For this purpose, in the area between the bore section 17 and the changeover channel 26 there is a return channel 27 which is open against the percussion piston 3 and which opens into the return line 25. As soon as - depending on the position of the percussion piston - the annular groove 3h connects the annular grooves 26a and 27a with one another and thereby connects to the return line 25, leads this also leads to a drop in pressure in the changeover channel 26 (whose connection to the pressure chamber 13 is then interrupted under the action of the cylinder section 3d), via which the annular surface 20e of the control slide 20 has previously been subjected to working pressure. Under the action of the greater pressure force on the end face 20d after relieving the pressure on the annular surface 20e, the control slide 20 moves to the left with the already mentioned consequence that the working stroke of the percussion piston 3 is triggered in the direction of arrow 18 by the reversing chamber 14 being subjected to the working pressure.
In order to be able to adapt the mode of operation of the rotary impact drilling device automatically to changing working conditions, there is an additional channel 29 between the return channel 27 and the changeover channel 26, the annular groove 29a of which lies opposite the percussion piston 3 (cf. also FIG. 3). The additional channel is connected to the changeover channel 26 with the interposition of a switching element in the form of a spring-loaded shut-off valve 30; the operation of the shut-off valve will be explained in detail below.

Die Schlagdrehbohrvorrichtung ist weiterhin mit einem Andrucksteuerelement in Gestalt einer Verstellhülse 31 ausgestattet; diese stützt sich in Längsrichtung beweglich einerseits an dem Schlagkolben 3 und andererseits zeitweilig an der Aufschlagfläche 12c des Einsteckendes 12 ab. Zur Abdichtung der Verstellhülse gegen den Schlagkolben 3 und das Schlagwerkgehäuse 2 sind in der Verstellhülse bzw. im Schlagwerkgehäuse gehaltene Dichtelemente 32 bzw. 33 vorgesehen.
Der Bewegungsspielraum der Verstellhülse ist durch den Abstand zwischen dem Gegenlager 11 und einer ortsfesten Anschlagfläche 34 im Schlagwerkgehäuse 2 festgelegt und (in Längsrichtung der Verstellhülse 31) mit b bezeichnet.
The impact rotary drilling device is further equipped with a pressure control element in the form of an adjusting sleeve 31; this is movably supported in the longitudinal direction on the one hand on the percussion piston 3 and on the other hand temporarily on the impact surface 12c of the insertion end 12. To seal the adjusting sleeve against the percussion piston 3 and the percussion mechanism housing 2, sealing elements 32 and 33 held in the adjusting sleeve or in the percussion mechanism housing are provided.
The range of motion of the adjusting sleeve is determined by the distance between the counter bearing 11 and a fixed stop surface 34 in the striking mechanism housing 2 and (in the longitudinal direction of the adjusting sleeve) 31) denoted by b.

Die Verstellhülse 31 weist eine in Arbeitshubrichtung (Pfeil 18) ausgerichtete Ringfläche 31a und eine davon getrennte Ringnut 31b auf. Letztere ist derart ausgebildet und angeordnet, daß sie eine an das Absperrventil 30 angeschlossene Steuerleitung 35 - abhängig von der Lage der Verstellhülse - wechselweise entweder mit der Verlängerung 22a der Druckleitung 22 oder mit der Rücklaufleitung 25 verbindet.
Über die Verlängerung 22a wird außerdem die Ringfläche 31a im Betriebszustand ständig mit Arbeitsdruck beaufschlagt; auf diese Weise wird also eine in Arbeitshubrichtung (Pfeil 18) wirksame Haltekraft erzeugt, unter deren Einwirkung die Verstellhülse 31 (abhängig von der jeweiligen Stellung des Einsteckendes 12) am Einsteckende oder am Gegenlager 11 in Anlage gehalten wird. Falls also die vom Einsteckende 12 übertragene Andruckkraft A größer ist als die ihr entgegengerichtete, mittels des Arbeitsdrucks erzeugte Rückstellkraft R, wird die Verstellhülse 31 unter Einwirkung des Einsteckendes 12 gegen die Anschlagfläche 34 gedrückt mit der Folge, daß die Steuerleitung 35 über die Ringnut 31b und die Rücklaufleitung 25 drucklos gehalten ist.
Übersteigt die Größe der Rückstellkraft R diejenige der Andruckkraft A (Fig. 2), liegt die Verstellhülse 31 im Mittel am Gegenlager 11 an; infolgedessen wird die Steuerleitung 35 über die Ringnut 31b und die Verlängerung 22a mit dem Arbeitsdruck pS beaufschlagt; gleichzeitig ist die Verbindung zwischen der Ringnut und der Rücklaufleitung 25 unterbrochen.
Um zu verhindern, daß sich zwischen der Verstellhülse 31 und der Anschlagfläche 34 ein nicht erwünschtes Druckpolster aufbaut, ist auf der der Anschlagfläche 34 zugewandten Seite zumindest eine Entlastungsnut 31c vorhanden; die Umgebung der Anschlagfläche 34 ist außerdem über einen Rücklaufkanal 36 druckentlastet, der in die Rücklaufleitung 25 einmündet.
Der Bewegungsspielraum b der Verstellhülse 31 parallel zur Längsrichtung des Schlagkolbens 3 und des Einsteckendes 12 ist erheblich kleiner bemessen als der Bewegungsspielraum des Einsteckendes innerhalb des Drehwerkgehäuses 6.
The adjusting sleeve 31 has an annular surface 31a oriented in the working stroke direction (arrow 18) and an annular groove 31b separated therefrom. The latter is designed and arranged in such a way that it connects a control line 35 connected to the shut-off valve 30 - depending on the position of the adjusting sleeve - alternately either to the extension 22a of the pressure line 22 or to the return line 25.
In addition, the annular surface 31a is continuously subjected to working pressure in the operating state via the extension 22a; in this way, an effective holding force is generated in the working stroke direction (arrow 18), under whose action the adjusting sleeve 31 (depending on the respective position of the insertion end 12) is held in contact with the insertion end or with the counter bearing 11. So if the pressure force A transmitted from the insertion end 12 is greater than the opposite force R generated by the working pressure, the adjusting sleeve 31 is pressed under the action of the insertion end 12 against the stop surface 34 with the result that the control line 35 via the annular groove 31b and the return line 25 is kept depressurized.
If the size of the restoring force R exceeds that of the pressing force A (FIG. 2), the adjusting sleeve 31 bears on the middle against the counter bearing 11; as a result, the control line 35 is acted upon via the annular groove 31b and the extension 22a with the working pressure p S ; at the same time the connection between the annular groove and the return line 25 is interrupted.
In order to prevent an undesired pressure cushion from building up between the adjusting sleeve 31 and the stop surface 34, at least one relief groove 31c is provided on the side facing the stop surface 34; the environment of the Stop surface 34 is also relieved of pressure via a return channel 36 which opens into the return line 25.
The range of motion b of the adjusting sleeve 31 parallel to the longitudinal direction of the percussion piston 3 and the insertion end 12 is dimensioned considerably smaller than the range of motion of the insertion end within the rotating mechanism housing 6.

Das Absperrventil 30 (vgl. dazu insbesondere Fig. 3) weist einen Verstellkolben 30a auf, der sich innerhalb einer Zylinderbohrung 37 an einer vorgespannten Rückstellfeder 38 abstützt und auf der dem Schlagkolben 3 zugewandten Seite in einen zapfenartigen Schließkörper 30b übergeht. Die Zylinderbohrung 37 wird über einen Leckagekanal 39 druckentlastet; dieser kann beispielsweise mit der in Fig. 1 dargestellten Rücklaufleitung 25 in Verbindung stehen.The shut-off valve 30 (cf. in particular FIG. 3) has an adjusting piston 30a, which is supported within a cylinder bore 37 on a prestressed return spring 38 and merges into a pin-like closing body 30b on the side facing the percussion piston 3. The cylinder bore 37 is relieved of pressure via a leakage channel 39; this can be connected, for example, to the return line 25 shown in FIG. 1.

In der in Fig. 3 dargestellten Ruhelage stützt sich der Ventilkolben 30a unter Einwirkung der vorgespannten Rückstellfeder 38 an einer Anschlagfläche 35b ab.
Solange die von der Steuerleitung 35 ausgehende Druckbeaufschlagung des Ventilkolbens 30a über die Ringnut 35a kleiner ist als die von der Rückstellfeder 38 ausgehende Vorspannkraft, greift der Schließkörper 30b in den Zusatzkanal 29 ein und sperrt diesen gegen den Rücklaufkanal 27 ab: Der Zusatzkanal 29 ist somit im Hinblick auf die Beeinflussung der Steuerung 4 (vgl. dazu beispielsweise Fig. 1) wirkungslos.
Der erwähnten Ruhelage des Absperrventils 30 entspricht der in Fig. 1 dargestellte Betriebszustand, in dem die Verstellhülse 31 im Mittel an der Anschlagfläche 34 anliegt und die Steuerleitung 35 mit der Rücklaufleitung 25 verbindet.
Falls die Andruckkraft A kleinere Werte annimmt als die an der Verstellhülse 31 angreifende Rückstellkraft (Fig. 2), wird die Steuerleitung 35 über die Verlängerung 22a der Druckleitung mit dem Arbeitsdruck beaufschlagt, der Ventilkolben 30a nebst Schließkörper 30b entgegen der Wirkung der Rückstellfeder 38 verschoben und dadurch eine Verbindung zwischen den Kanälen 29 und 27 hergestellt. Falls nunmehr die Ringnut 3h (Fig. 1) im Laufe der Rückhubbewegung des Schlagkolbens den Bereich der Ringnut 29a des Zusatzkanals 29 erreicht, wird bereits zu dem sich daraus ergebenden früheren Zeitpunkt eine Verbindung zwischen dem Umschaltkanal 26, dem Zusatzkanal 29 und dem drucklos gehaltenen Rücklaufkanal 27 hergestellt: Da die Steuerung 4 dementsprechend zu einem früheren Zeitpunkt in die Arbeitshubstellung umgeschaltet wird, führt der Schlagkolben 3 bei erhöhter Schlagzahl und herabgesetzter Einzelschlagenergie einen kleineren Hub aus: Die erfindungsgemäß ausgestaltete Schlagdrehbohrvorrichtung paßt sich unter Einwirkung der Verstellhülse 31 und des Absperrventils 30 selbsttätig der durch die Arbeitsbedingungen hervorgerufenen Änderung der Andruckkraft an, und zwar unabhängig von der Überwachung und Handhabung durch eine Bedienungsperson.
In the rest position shown in FIG. 3, the valve piston 30a is supported on a stop surface 35b under the action of the prestressed return spring 38.
As long as the pressure applied to the valve piston 30a via the annular groove 35a from the control line 35 is less than the pretensioning force emanating from the return spring 38, the closing body 30b engages in the additional channel 29 and blocks it from the return channel 27: the additional channel 29 is thus in With regard to influencing the control 4 (see, for example, FIG. 1) ineffective.
The above-mentioned rest position of the shut-off valve 30 corresponds to the operating state shown in FIG. 1, in which the adjusting sleeve 31 abuts the stop surface 34 on average and connects the control line 35 to the return line 25.
If the pressure force A takes on smaller values than the restoring force acting on the adjusting sleeve 31 (FIG. 2), the control line 35 is subjected to the working pressure via the extension 22a of the pressure line, the valve piston 30a together with the closing body 30b is displaced against the action of the return spring 38, and thereby a connection between the channels 29 and 27 manufactured. If the annular groove 3h (FIG. 1) now reaches the area of the annular groove 29a of the additional channel 29 in the course of the return stroke movement of the percussion piston, a connection between the changeover channel 26, the additional channel 29 and the unpressurized return channel is already established at the earlier point in time resulting therefrom 27: Since the control 4 is accordingly switched to the working stroke position at an earlier point in time, the percussion piston 3 executes a smaller stroke with an increased number of strokes and reduced individual impact energy: the impact rotary drilling device designed according to the invention adjusts itself automatically under the action of the adjusting sleeve 31 and the shut-off valve 30 changes in the pressing force caused by the working conditions, regardless of the monitoring and handling by an operator.

Bei der in Rede stehenden Ausführungsform (Fig. 1 bis 3) ist der Bereich des Schlagwerkgehäuses 2 zwischen den Dichtelementen 16 mittels des Rücklaufkanals 27 druckentlastet, der in die Rücklaufleitung 25 einmündet.In the embodiment in question (FIGS. 1 to 3), the area of the striking mechanism housing 2 between the sealing elements 16 is relieved of pressure by means of the return channel 27, which opens into the return line 25.

Bei der Ausführungsform gemäß Fig. 4 ist das Schaltelement zur Beeinflussung der Steuerung 4 als Verstellkolben 41 ausgebildet, der entgegen der Wirkung einer Rückstellfeder 42 innerhalb eines Zylinderraums 43 verschiebbar ist. Die Ruhelage des Verstellkolbens 41 ist wiederum durch die bereits erwähnte Anschlagfläche 35b festgelegt.
Über eine Ringausnehmung 41a nebst Bohrung 41b und eine Verlängerung 40a des Leckagekanals 40 ist der Rücklaufkanal 27 an die Rücklaufleitung 25 angeschlossen. Ihm sind in Richtung auf die Schlagkolbenspitze 3a zwei Zusatzkanäle 44, 45 zugeordnet, die - abhängig von der Druckbeaufschlagung des Verstellkolbens und der sich daraus ergebenden Arbeitslage - ggf. der Ringausnehmung 41a gegenüberliegen und damit im Hinblick auf die Beeinflussung der Steuerung 4 wirksam werden.
In dem dargestellten Betriebszustand liegt die Verstellhülse 31 an der Anschlagfläche 34 an, so daß die Steuerleitung 35 über die Ringnut 31b und die Rücklaufleitung 25 druckentlastet ist.
Falls sich die Verstellhülse entgegen der Wirkung der Andruckkraft A nach links verschiebt, führt der Verstellkolben 41 entgegen der Wirkung der Rückstellfeder 42 eine entsprechend gerichtete Bewegung aus, in deren Verlauf - abhängig von der Druckbeaufschlagung über die Steuerleitung 35 - entweder nur der Zusatzkanal 44 oder auch der Zusatzkanal 45 von der Ringausnehmung 41a erfaßt wird. Die Steuerung 4 wird dementsprechend in die Arbeitshubstellung umgeschaltet, falls die Ringnut 3h den Zusatzkanal 45 oder den Zusatzkanal 44 mit dem Umschaltkanal 26 verbindet.
Die in Rede stehende Ausführungsform gestattet es also, die Arbeitsweise der Schlagdrehbohrvorrichtung in mehr als zwei Stufen an die sich ändernde Größe der vom Einsteckende 12 übertragenen Andruckkraft A anzupassen.
In the embodiment according to FIG. 4, the switching element for influencing the control 4 is designed as an adjusting piston 41 which, contrary to the action of a return spring 42, is displaceable within a cylinder space 43. The rest position of the adjusting piston 41 is in turn due to the mentioned abutment surface 35b set.
The return channel 27 is connected to the return line 25 via an annular recess 41a together with a bore 41b and an extension 40a of the leakage channel 40. It is assigned two additional channels 44, 45 in the direction of the percussion piston tip 3a, which - depending on the pressurization of the adjusting piston and the resulting working position - may be opposite the annular recess 41a and thus become effective with regard to influencing the control 4.
In the operating state shown, the adjusting sleeve 31 bears against the stop surface 34, so that the control line 35 is relieved of pressure via the annular groove 31b and the return line 25.
If the adjusting sleeve moves to the left against the action of the pressing force A, the adjusting piston 41 performs a correspondingly directed movement against the action of the return spring 42, in the course of which - depending on the pressurization via the control line 35 - either only the additional channel 44 or also the additional channel 45 is gripped by the ring recess 41a. The controller 4 is accordingly switched to the working stroke position if the annular groove 3h connects the additional channel 45 or the additional channel 44 to the switching channel 26.
The embodiment in question thus allows the operation of the rotary impact drilling device to be adapted in more than two stages to the changing size of the pressing force A transmitted by the insertion end 12.

Die Leitungen 22a und 35 sind in der Nähe ihrer Einmündungen im Bereich der Verstellhülse 31 mit Dämpfungsdrosseln 46, 47 ausgestattet.The lines 22a and 35 are equipped with damping chokes 46, 47 in the vicinity of their openings in the area of the adjusting sleeve 31.

Der mit der Erfindung erzielte Vorteil besteht insbesondere darin, daß sich die Schlagzahl und Einzelschlagenergie in Abhängigkeit von der Größe der auf ein Meßglied (Verstellhülse) einwirkenden Andruckkraft selbsttätig einstellt. Die zugehörigen Bestandteile sind dabei - unter Einsparung besonderer Versorgungs- und Steuerleitungen - Bestandteil der Schlagdrehbohrvorrichtung selbst. Auf eine Überwachung der Arbeitsweise der Schlagdrehbohrvorrichtung durch eine Bedienungsperson kann daher insoweit verzichtet werden.The advantage achieved by the invention is in particular that the number of blows and Single impact energy automatically sets depending on the size of the pressure force acting on a measuring element (adjusting sleeve). The associated components are - with the saving of special supply and control lines - part of the percussion drilling device itself. Monitoring of the functioning of the percussion drilling device by an operator can therefore be dispensed with.

Die Erfindung ist selbstverständlich auch anwendbar auf Vorrichtungen, die lediglich ein hydraulisch betriebenes Schlagwerk aufweisen und deren Werkzeug-Einsteckende dementsprechend lediglich in Längsrichtung des Schlagwerkgehäuses hin- und herbeweglich gehalten ist.The invention is of course also applicable to devices which only have a hydraulically operated striking mechanism and whose tool insertion end is accordingly held back and forth only in the longitudinal direction of the striking mechanism housing.

Claims (10)

  1. Hydraulically operated percussion mechanism with a percussion piston (3), a control means (4) selectively switching over the movement of said piston and a tool insert end (12), which is subjected to the impact of the percussion piston (3), is held to slide independently thereof in its longitudinal direction and against which a contact pressure control element (31) is held in abutment at least temporarily under the action of a restoring element (31a, 22) effective in the direction of impact (arrow 18), wherein a switching element (30 or 41) is operated via a control line (35) in such a way that the control means (4) executes the switchover movement into the working stroke position during the return stroke of the percussion piston (arrow 19) at an earlier or later point in time and thus triggers the working stroke of the percussion piston in the direction of impact (arrow 18), characterised in that the control line (35) is connected either to a pressure line (22) or to a pressure-vented return line (25) via the contact pressure control element (31), depending on whether this merely abuts against the insert end (12) or also against a stop (34) lying opposite this insert end relative to the contact pressure control element (31) at a contact pressure (A) exceeding the restoring force (R); and that the contact pressure control element is constructed as an adjusting sleeve (31) with a ring surface (31a), which is aligned in the direction of the working stroke (arrow 18) and subjected to load via the pressure line (22), and with an annular groove (31b) separate from said ring surface located at the entrance of the control line (35) and - depending on the position of the adjusting sleeve relative to the stop (34) - either at the entrance of the pressure line (extension 22a) or the return line (25).
  2. Device according to Claim 1, characterised in that the control line (35) is connected to the return line (25) if the contact pressure control element (31) abuts against the stop (34).
  3. Device according to at least one of the preceding claims, characterised in that the contact pressure control element (31) has a holding surface (31a) effective in the direction of the working stroke (arrow 18) and connecting to the pressure line (22).
  4. Device according to at least one of the preceding claims, characterised in that the percussion piston (3) is provided with a switchover channel (27) feeding into the percussion piston hole in the housing (2) of the percussion mechanism, and the control means (4) is switched over into its working stroke position under the action of said switchover channel, depending on the position of the percussion piston during its return stroke; and that at least one additional channel (29 or 44, 45) is connected to the switchover channel (27) by means of the switching element (30 or 41).
  5. Device according to at least one of the preceding claims, characterised in that the dimension of the movement clearance (b) of the contact pressure element (31) is smaller than that of the insert end (12) in the direction of the axis (3i) of the percussion piston.
  6. Device according to at least one of the preceding claims, characterised in that the movement clearance (b) of the contact pressure element (31) in the direction of the working stroke (arrow 18) of the percussion piston (3) is restricted by an abutment (11), in relation to which the insert end (12) may be moved back and forth in the direction of its longitudinal extension.
  7. Device according to at least one of the preceding claims, equipped with only one additional channel, characterised in that the switching element is constructed as a spring-loaded stop valve (30), the closing body (30b) of which can be moved relative to the additional channel (29) into an opening or locking position.
  8. Device according to at least one of Claims 1 to 6, characterised in that the switching element is constructed as a spring-loaded adjusting piston (41), via which - depending on the magnitude of the pressure load applied - optionally at least one additional channel (44, 45) is connected to the return line (25) next to the switchover channel (27).
  9. Device according to at least one of the preceding claims, characterised in that the pressure line (22) and the control line (35) have dampers (46 or 47).
  10. Device according to Claim 1, characterised in that the adjusting sleeve (31) is directed in the housing (2) of the percussion mechanism to move longitudinally to enclose the percussion piston (3) on a portion of its longitudinal extension.
EP91114231A 1990-09-08 1991-08-24 Hydraulically operated percussion mechanism Expired - Lifetime EP0475171B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4028595A DE4028595A1 (en) 1990-09-08 1990-09-08 HYDRAULICALLY OPERATED PERFORMANCE
DE4028595 1990-09-08

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EP0475171A2 EP0475171A2 (en) 1992-03-18
EP0475171A3 EP0475171A3 (en) 1992-05-20
EP0475171B1 true EP0475171B1 (en) 1995-10-11

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EP91114231A Expired - Lifetime EP0475171B1 (en) 1990-09-08 1991-08-24 Hydraulically operated percussion mechanism

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US (1) US5129466A (en)
EP (1) EP0475171B1 (en)
JP (1) JPH05138549A (en)
AT (1) ATE128895T1 (en)
DE (2) DE4028595A1 (en)

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Also Published As

Publication number Publication date
EP0475171A3 (en) 1992-05-20
DE4028595C2 (en) 1993-08-05
DE59106668D1 (en) 1995-11-16
EP0475171A2 (en) 1992-03-18
ATE128895T1 (en) 1995-10-15
DE4028595A1 (en) 1992-03-12
US5129466A (en) 1992-07-14
JPH05138549A (en) 1993-06-01

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