EP1136189A2 - Marteau à coup actionné hydrauliquement - Google Patents

Marteau à coup actionné hydrauliquement Download PDF

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Publication number
EP1136189A2
EP1136189A2 EP01105981A EP01105981A EP1136189A2 EP 1136189 A2 EP1136189 A2 EP 1136189A2 EP 01105981 A EP01105981 A EP 01105981A EP 01105981 A EP01105981 A EP 01105981A EP 1136189 A2 EP1136189 A2 EP 1136189A2
Authority
EP
European Patent Office
Prior art keywords
empty
stroke
working
piston
line
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.)
Granted
Application number
EP01105981A
Other languages
German (de)
English (en)
Other versions
EP1136189B1 (fr
EP1136189A3 (fr
Inventor
Thomas Deimel
Marcus Dr.-Ing. Geimer
Markus Mellwig
Heinz-Jürgen Dr.-Ing. Prokop
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.)
Construction Tools GmbH
Original Assignee
Krupp Berco Bautechnik GmbH
Atlas Copco Construction Tools GmbH
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
Family has litigation
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Application filed by Krupp Berco Bautechnik GmbH, Atlas Copco Construction Tools GmbH filed Critical Krupp Berco Bautechnik GmbH
Publication of EP1136189A2 publication Critical patent/EP1136189A2/fr
Publication of EP1136189A3 publication Critical patent/EP1136189A3/fr
Application granted granted Critical
Publication of EP1136189B1 publication Critical patent/EP1136189B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • B25D9/265—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof with arrangements for automatic stopping when the tool is lifted from the working face or suffers excessive bore resistance

Definitions

  • the invention relates to a fluid-powered hammer mechanism with one in one Working cylinder movable and hitting a tool Percussion piston and a control with one in a control valve Movable spool, the percussion piston being two different has large piston areas, of which the smaller, towards the Return stroke effective piston area constantly with a working pressure standing pressure line and the larger, effective in the direction of the working stroke Piston area via the control valve alternately with the pressure line and an unpressurized return line is connected.
  • the spool has two different sizes, in opposite directions to each other effective slide surfaces, the smaller, in the direction of the return stroke position of the control slide acting on this slide surface constantly with the Pressure line and its larger slide area over a between the Piston surfaces arranged circumferential groove each only temporarily and alternately connected to the pressure or the return line.
  • a percussion mechanism of the type mentioned at the beginning is described in the publication DE 196 36 659 A1.
  • the known percussion mechanism is designed such that when a percussion piston limit position in the direction of the working stroke is exceeded, the control valve is switched over to the return stroke position. During the immediately following return stroke, the control valve is prematurely shifted into the working stroke position by pressurizing a short stroke line, so that the percussion piston only executes a short stroke. So if the tool interacting with the percussion piston penetrates the crushing material and the percussion piston leaves its normal impact level, the individual stroke energy is reduced by the automatic stroke change.
  • the working pressure present in the high-pressure circuit is present at the short stroke inlet.
  • the connection between the short stroke input and the high pressure circuit is interrupted in the normal operating position, with the result that the known impact device may work in short stroke mode. Due to the assignment of the stroke switch valve to the short stroke input, it is not possible to prevent the execution of empty strokes regardless of the effect of the short stroke input.
  • the invention is therefore based on the object of the generic type To develop percussion mechanism in such a way that the percussion piston - regardless of other control-related circumstances - is stopped if he has reached a predetermined extension position in the working stroke direction.
  • the innovation proposal consists in the fact that the interior of the working cylinder receiving the percussion piston additionally has an empty-blow opening, which is released from the front piston collar of the percussion piston, which has the smaller piston area, only in the direction of the interior after the percussion piston, which is in normal operation has reached the resulting extended position in the working stroke direction by a predetermined distance until an empty position is reached.
  • the empty blow mouth is a safety element which can be switched between two end positions - out of service position and active position - upstream, the input side of which is connected to the pressure line having the working pressure, the empty blow mouth in the active position acting on the safety element with the working pressure emanating from it and in the inoperative position, the connection via the securing element between the pressure line and the empty run junction is interrupted.
  • the additional empty blank junction continues into Moved towards the tool, it is - in Axial direction of the percussion piston seen - closer than the confluence of one such as existing short-stroke lines.
  • the securing element If the securing element is in the active position and the percussion piston reaches the empty position, it acts at the empty space confluence applied working pressure over the between the two piston collars of the Percussion piston located circumferential groove in such a way that the control Control spool is blocked in the working stroke position. Under the influence of the the working pressure applied at the empty blow junction becomes the Control prevented from working stroke to return stroke position to switch so that the percussion piston has no movement in the direction of its Can perform return strokes. As a result, the striking mechanism is switched off and can only be achieved by mechanically lifting the percussion piston - i.e. by Press the percussion piston against the tool - put into operation again become.
  • the position of the empty blank junction can be defined by the fact that it is closer to the tool (seen in the axial direction of the percussion piston) than the last preceding junction into the interior of the working cylinder, via which the control in the sense of switching between the working stroke and Return stroke position is affected.
  • disconnectable connection between the securing element and the empty blank junction lies within a housing which represents at least one component of the working cylinder (claim 2).
  • the disconnectable connection can then either be arranged within its own housing, which in turn is connected to the working cylinder, or located directly inside the working cylinder itself.
  • the securing element can - insofar as it is otherwise the aforementioned Meets requirements - be designed and arranged in any way.
  • a simple embodiment of the invention is to design the securing element as a rotary slide valve (claim 4).
  • the rotary slide valve can have a screw-in hollow cylinder and an adjusting pin rotatably held in it with a connecting channel, via which - depending on the rotary position of the adjusting pin - a connection can be made between the empty flap mouth and the pressure line, the rotating position of the adjusting pin being braced is fixed with the hollow cylinder (claim 5).
  • the securing element can also be one in several Positions within the component receiving it (housing, Working cylinder) have lockable locking pin, either in a first Locked position, a connection between the pressure line and the empty run junction present or in a second locking position this connection is interrupted (claim 6).
  • the securing element can be such be designed that the locking pin - against the effect of at least one as Spring washers serving abutments - in the longitudinal direction between the Locking positions is displaceable (claim 7).
  • a further advantageous embodiment of the subject matter of the invention is characterized in that the securing element has a threaded bolt which is accessible from the outside of the component receiving it (housing, working cylinder) and is screwed to it and has an exchange bolt which can be fixed therein within a receiving bore and which is either designed as a bridging element, by means of which the empty run mouth is connected to the pressure line, or represents a blocking element which blocks the connection between the pressure line and the empty run mouth (Claim 8).
  • the securing element has a threaded bolt which is accessible from the outside of the component receiving it (housing, working cylinder) and is screwed to it and has an exchange bolt which can be fixed therein within a receiving bore and which is either designed as a bridging element, by means of which the empty run mouth is connected to the pressure line, or represents a blocking element which blocks the connection between the pressure line and the empty run mouth (Claim 8).
  • the securing element has a threaded bolt which is accessible from the outside
  • the striking mechanism generally designated 1, with automatic stroke switching (cf. FIG. 1) has, in addition to the lines and drive and control elements still to be described, a working cylinder 2 in which a striking piston 3 is held in the longitudinal direction and can be moved back and forth.
  • This has two piston collars 3a and 3b lying in the interior of the working cylinder, which are separated from one another by a circumferential groove 3c.
  • the outwardly directed piston surface A1 and A2 of the piston collar 3b and 3a defines with the working cylinder 2 a rear and front cylinder space section 2a and 2b, the piston surface A1 being dimensioned smaller than the piston surface A2.
  • the percussion piston 3 merges into a piston tip 3d, which is opposite a tool in the form of a chisel 4; the range of motion in the direction of the percussion piston 3 is limited by a stop 4a.
  • the movement of the percussion piston 3 in the direction of the working stroke is indicated by an arrow 3e.
  • the illustration in question shows the striking mechanism in one state Impact of the percussion piston 3 on the chisel 4. This becomes normal operation provided that the chisel does not penetrate the material to be shredded and the percussion piston accordingly takes the normal intended Serve position.
  • the control for switching over the movement of the percussion piston 3 consists of a control slide 5a movable in a control valve 5, the smaller slide surface S1 of which is constantly acted upon by the working pressure (system pressure) via a return line 6; this is generated by an energy source in the form of a hydraulic pump 7.
  • the smaller piston area A1 is also constantly subjected to the working pressure via a pressure line 8, which is connected to the return line 6.
  • the opening 8a of the pressure line is arranged with respect to the working cylinder 2 such that it is in any case outside the piston collar 3b and thus inside the front cylinder space section 2b.
  • the larger slide area S2 of the control slide 5a is over a Reversing line 9 with the interior of the working cylinder 2 in such Connection that its mouth 9a in the state shown on the Circumferential groove 3c connected to a pressure-free return line 10 is.
  • the mouth 9a and the mouth 10a of the return line are located so - seen in the longitudinal direction of the percussion piston 3 - at a distance opposite, which is smaller than the axial length of the circumferential groove 3c.
  • the control valve 5 is connected on the one hand via a control line 11 to the pressure line 8 and on the other hand via a drain line 12 together with the tank 12a to the return line 10. Furthermore, the control valve 5 is connected to the rear cylinder chamber section 2a via an alternating pressure line 13, via which the larger piston area A2 can be subjected to working pressure if necessary.
  • the control valve can assume two valve positions, namely the illustrated (right) return stroke position, in which the larger piston area A2 is relieved of pressure via the alternating pressure line 13 and the discharge line 12, and the (left) working stroke position, in which the rear cylinder chamber section 2a via the pressure line 8, the control line 11 connected to this and the alternating pressure line 13 are acted upon by the working pressure. This state has the consequence that the percussion piston 3 - contrary to the restoring force emanating from the smaller piston surface A1 - executes a working stroke in the direction of the arrow 3e.
  • the striking mechanism 1 is further equipped with a pilot control in the form of a pilot valve 14 which can either assume the (upper) blocking position shown or a (lower) opening position.
  • the position of the pilot valve can be influenced over two surfaces, namely over the smaller adjustment surface V1 and over the larger adjustment surface V2.
  • the latter is connected via a pilot line 15 to the interior of the working cylinder 2, the opening 15a of which - seen in the direction of the working stroke (arrow 3e) - lies behind the opening 9a of the changeover line 9.
  • the pilot line 15 is in turn connected to the pilot valve 14 on the output side via a pilot branch line 15b equipped with an orifice 16.
  • the smaller adjustment surface V1 is connected via a pilot control return line 17a to the pressure line 8 and is constantly pressurized with the working pressure; Accordingly, the pilot valve 14, under the action of the restoring force acting on the adjustment surface V1, tends to assume the open position (not shown).
  • the pilot valve On the input side, the pilot valve is connected on the one hand to the interior of the working cylinder 2 via a short-stroke line 18 with a junction 18a, and on the other hand to the pressure line 8 via a pilot pressure line 17.
  • the junction 18a of the short stroke line 18 is - again seen in the direction of the working stroke (arrow 3e) - arranged behind the junction 15a of the pilot line 15.
  • the pilot valve 14 is on the one hand - as already mentioned - to the pilot line 15 via the pilot branch line 15b connected and on the other hand via an additional line 19 with the Changeover line 9 for the control valve 5 in connection.
  • the pilot pressure line 17 is connected to the pilot line 15 via the pilot branch line 15b and thereby generates an adjusting force which is effective in the direction of the blocking position, namely via the larger adjusting surface V2. Furthermore, in the illustrated blocking position, the short stroke line 18 and the additional line 19 are blocked in the direction of the pilot valve 14.
  • the (lower) open position of the pilot valve 14 is characterized in that the short stroke line 18 is simultaneously connected to the pilot branch line 15b and the additional line 19 and that the pilot pressure line 17 is blocked.
  • either the pressure conditions in lines 15, 15b, 19 and 18 or only the pressure conditions in lines 15, 15b and 19 can adapt to one another.
  • the latter is the case if - as shown - the mouth 18a of the short-stroke line is blocked by the piston collar 3b against the interior of the working cylinder 2.
  • pilot valve 14 takes the shown locking position and is by pressurization by means of Pilot pressure line 17 held in this locked position (because on both Adjustment surfaces V1 and V2 the working pressure is applied).
  • the working pressure is applied to the larger control surface S2, whereby the control slide 5a is brought into the (left) working stroke position, thereby the rear cylinder section 2a with the control line 11 connects the pressure line 8 and triggers a new working stroke.
  • the percussion piston 3 After switching the control valve 5 into the working stroke position and the pilot valve 14 into the blocking position, the percussion piston 3 first performs a working stroke. If the chisel 4 penetrates into the material to be shredded, the percussion piston 3 also leaves its normal impact plane and follows the chisel.
  • the lines 15b and 15 as well as the lines 19 and 9 are pressurized via the short-stroke line 18, which is thus under pressure, with the interposition of the pilot valve 14, with the result that the control valve 5 switches to the (left) working stroke position before reaching the maximum possible stroke and the working stroke is triggered again.
  • the larger adjustment surface V2 of the pilot valve 14, which is exposed to the working pressure causes the latter to be displaced into the blocking position shown, counter to the restoring force emanating from the smaller adjustment surface V2.
  • the described configuration thus makes it possible to react to the properties or the behavior of the material to be shredded with each individual blow of the percussion piston. If the tool penetrates the material to be shredded, the percussion piston only executes a small stroke, so that the single impact energy is low.
  • the interior of the working cylinder 2 additionally has an empty run opening 20a, which - with the interposition of an empty run line 20 - has a switchable fuse element 21 connected upstream; the input side of which is connected to the pressure line 8 via an intermediate line 22 and is therefore constantly subjected to the working pressure.
  • the securing element 21 can be switched between two end positions - namely the (right) non-operating position and the (left) active position. While the working pressure emanating from the securing element 21 is present at the empty run mouth 20a in the active position shown, the connection between the pressure line 8 and the empty run mouth 20a is interrupted in the non-operating position of the securing element 21.
  • the empty run junction 20a is from the mouth 18a of the short stroke line 18 is arranged separately.
  • the blank stroke protection can be used with the essential Components 20a and 21 regardless of the conditions in the long-stroke and short-stroke operation take effect if the percussion piston 3 the associated Extend position by a given distance until taking one Has run over the empty position.
  • the percussion piston 3 assumes the normal impact position in the illustration, the empty-blow opening 20a being closed in the direction of the interior of the working cylinder 2 by the front piston collar 3b having the smaller piston area A1. If the percussion piston is extended so far in the working stroke direction (arrow 3e) that the empty-blow mouth 20a is no longer closed by the front piston collar 3b, the working pressure applied to it can be interposed by the annular groove 3c and the control line 9 on the larger slide surface S2 of the control slide 5a act, so that the controller 5 is held in the existing (left) working stroke position during the working stroke.
  • the return line 10 has a correspondingly dimensioned outflow resistance, which is indicated by a throttle unit 10b.
  • the controller 5 is prevented from switching from the working stroke position to the (right) return stroke position under the circumstances mentioned above under the influence of the working pressure emanating from the empty stroke mouth 20a, as a result of which the percussion piston 3 is stopped. It is only by mechanically lifting the percussion piston 3 within the working cylinder 2 that the striking mechanism can be put into operation again, namely in that the front piston collar 3b closes the empty run mouth 20a in the direction of the interior of the working cylinder 2.
  • the controller 5 can switch from the working stroke position to the return stroke position, as a result of which the return stroke movement of the percussion piston 3 is triggered.
  • the empty blow protection can be switched off in a simple manner by switching the securing element 21 into its (right) non-operating position. In this, the empty stroke junction 20a has no effect, so that the striking mechanism can only work in long-stroke or short-stroke operation.
  • the empty impact protection (securing element 21) can also be used in connection with striking mechanisms configured differently, for example in connection with the striking mechanism designs according to FIG. 2 or 3.
  • the embodiment according to FIG. 2 differs differs from the embodiment according to FIG. 1 in that there is no automatically acting pilot control in the form of a pilot valve 14. Accordingly, in the embodiment in question, the lines 15, 15b, 17, 17a, 18 and 19, along with openings 15a, 18a and the orifice 16 associated with the line 15b, are also missing.
  • the control slide 5a of the control valve 5 - depending on the pressure conditions in the changeover line 9 - either assumes the illustrated return stroke position (right) or the working stroke position (left).
  • the control line 9 after passing the piston collar 3b in Direction of the working stroke (arrow 3e) via the empty conduit 20 with Working pressure is applied so that the controller 5 (as already shown in FIG. 1 explained) in the working stroke position assumed during the working stroke is held. Building up a sufficiently high pressure in the Control line 9 is thereby ensured that the return line 10th a correspondingly dimensioned outflow resistance (throttle unit 10b) having.
  • control 5 is assigned a reversing valve 14A, which can be moved arbitrarily (expediently remotely) between two end positions, namely the illustrated blocking position and an open position.
  • the reversing valve 14A is connected, on the one hand, to the interior of the working cylinder 2 via a short-stroke line 18 together with a junction 18a and, on the other hand, to the reversing line 9 via an additional line 19.
  • the reversing valve 14A In the blocking position shown, the reversing valve 14A has no influence on the position of the control slide 5a of the controller 5. If the reversing valve 14A assumes the (lower) open position, on the other hand - depending on the position of the percussion piston 3 within the working cylinder 2 - a connection can be made between the interior thereof and the reversing line 9, which may shift the control slide 5a into the (left) ) Has the result of a working stroke.
  • the reversing valve 14A thus makes it possible to arbitrarily influence the mode of operation of the striking mechanism 1 in such a way that it may temporarily work in short-stroke mode.
  • the effect of the empty impact protection (securing element 21) is independent of the position of the reversing valve 14A.
  • the reversing line 9 Under the action of the securing element 21 (taking the active position shown), the reversing line 9 is only subjected to a sufficiently high pressure after the piston collar 3b of the percussion piston 3 moved in the working stroke direction has released the opening 20a of the empty blow line 20; due to the then prevailing pressure conditions, the control slide 5a cannot switch into the return stroke position (shown), so that the striking mechanism 1 is stopped.
  • the empty stroke safeguard can be designed and arranged as desired.
  • the empty-blow protection is designed in such a way that the disconnectable connection between the securing element 21 and the empty-blow opening 20a lies within the working cylinder 2 and that the securing element - from the outside 2c accessible from the working cylinder - forms a detachable component which is arranged essentially within the working cylinder.
  • the disconnectable connection and the securing element accordingly in a separate housing, which is located outside the working cylinder.
  • the securing element 21 has a threaded bolt 23, which is accessible from the outside 2c of the working cylinder 2 screwed and there is provided with a hexagon socket 23a.
  • a threaded bolt 23 On the Interior 2d of the side facing the working cylinder 2 is the threaded bolt shielded from the environment by means of a sealing element 24.
  • an adjusting pin 25 is supported within the working cylinder 2 and on the threaded bolt 23, in which a connecting bore 25a runs. This is such that it connects the lines 20 and 22 to one another in the illustrated operative position of the securing element 21. Under the action of the threaded bolt 23, the adjusting pin 25 is clamped in the direction of the empty blow line 20 in the working cylinder 2.
  • the adjusting pin After removal of the threaded bolt 23, the adjusting pin can be rotated outside the working cylinder 2 by 180 ° with respect to its transverse axis and inserted in this position again in the working cylinder, with the result that the empty impact line 20 is closed in the direction of the threaded bolt 23 screwed in thereafter and that Securing element 21 thus takes the decommissioning position.
  • the embodiment in question thus makes it possible to move the empty-stroke safety device into the desired end position in a few simple steps, at the same time ensuring that the predetermined end position remains unchanged regardless of the working conditions.
  • the securing element 21 has a locking pin 26 which is held in a bore 27 and is equipped with a threaded bore 26a facing the outside 2c.
  • the bore 27 communicates with the lines 20 and 22.
  • the locking pin 26 is supported by two spring washers 28 on the working cylinder 2 and can be displaced from the position shown (corresponding to the active position of the securing element 21) against the action of the spring washers 28 so far in the direction of the empty run mouth 20a that the Connection between lines 20 and 22 (corresponding to the inoperative position of the fuse element 21) is interrupted.
  • the threaded bore 26a serves to lock the locking pin 26 by means of a screwed tool to move in the desired manner or to install or remove.
  • the embodiment in question can also within the scope of the invention be modified so that the transfer of the securing element In its inoperative position, the locking pin 26 shown removed and by a longer locking pin is replaced, the intermediate line in the installed state 22 closes against the empty conduit 20 and thus the connection between the empty blow mouth 20a and the pressure line 8 interrupts.
  • the securing element 21 - which is shown in the operative position - has a hollow cylinder 29 screwed into the working cylinder 2 from the outside 2c and an adjusting pin 30 rotatably held therein with a connecting channel 30a;
  • the latter can either be used to establish or interrupt the connection between the empty run mouth 20a and the pressure channel 8 (as shown).
  • the hollow cylinder 29 has a plurality of driving pins 31 which, seen from the outside 2c, protrude in front of the connecting channel 30a in the direction of the adjusting pin 30 and, when the hollow cylinder 29 is screwed in, in the direction of the empty stroke.
  • Carry mouth 20a ie in the axial direction.
  • the adjusting pin 30 is supported on the working cylinder 2 via a prestressed spring element 30c in the region of the connecting channel 30a. Under the action of the spring element 30c, the adjusting pin 30 is held in contact with the driving pins 31 and is thereby secured against an unwanted change in its rotational position with respect to the hollow cylinder 29.
  • the adjusting pin 30 is sealed by means of a sealing element 32 against the hollow cylinder 29, which in turn receives a sealing element 33 for sealing against the working cylinder 2.
  • the handling of the parts 29 and 30 is made possible by the fact that these have a plurality of countersunk bores 29a or a threaded bore 30b in the area of the outside 2c.
  • the rotational position of the adjusting pin 30 can be changed in that it is shifted - counter to the restoring effect of the spring element 30c - in the direction of the empty run mouth 20a (to the right). In this state, the adjusting pin 30 can be transferred with respect to the hollow cylinder 29 into the desired rotational position, in which it remains fixed after the axial force acting on it has ceased to exist.
  • the adjusting pin 30 can be rotated in the desired manner without removing the securing element under the action of an axial force acting on it and can be fixed in the desired rotational position in which it is under the action after the axial force has ceased to exist of the spring element 30c is supported in the axial direction on the driving pins 31.
  • the securing element 21 has an exchange bolt 34 serving as a locking element, which is held under the action of a threaded bolt 35 in a bore 36 connecting the lines 20 and 22 to one another.
  • the securing element 21 can be easily in the Convey active position that the replacement bolt 34 after loosening the Threaded bolt 35 removed and then the bore 36 only closed by means of the threaded bolt 35 in the direction of the outside 2c becomes.
  • an exchange bolt 38 is held in the direction of the empty run opening 20a within a receiving bore 2e.
  • the exchange bolt 38 is equipped with a connecting hole 38a in such a way that it connects the lines 20 and 22 to one another and thus enables the pressurization of the empty run junction 20a via the pressure line 8.
  • the threaded bolt 37 can be loosened by means of an internal hexagon bore 37a starting from the outside 2c or screwed in in the direction of the empty run mouth 20a.
  • the Securing element 21 thereby transferred into its non-operating position (Fig. 8b) be that the replacement bolt 38 is formed by a solid bolt Exchange bolt 39 is replaced. This fills the receiving hole 2e Elimination of the connecting bore 38a completely, so that the lines 20th and 22 are not linked.
  • the last-mentioned embodiment can also be modified within the scope of the invention in that the securing element 21 - based on the embodiment according to FIG. 6 - has an adjusting pin 30 similar to the adjusting pin 30 instead of the replacement bolts 38 and 39. This is thus designed such that it either creates a connection between the lines 20 and 22 by a rotation through 180 ° with respect to its longitudinal axis, or interrupts this connection.
  • the advantage achieved by the invention is, in particular, that it enables the impact piston to be stopped using simple means - independently of the long-stroke and / or short-stroke operation, if necessary, as soon as it has an extended position in the working stroke direction during normal operation by a predetermined distance up to Has taken over an empty position, which is defined by the position of the junction 20a of the empty line 20. If the securing element of the empty stroke protection assumes its operative position, the percussion piston is automatically blocked as it approaches the predetermined empty stroke position. The striking mechanism can only be switched on again by mechanically lifting the percussion piston. If the securing element assumes its inoperative position, the empty run junction 20a has no effect. Accordingly, the striking mechanism is not stopped if the percussion piston moves over its normally resulting extension position in the working stroke direction.

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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)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Earth Drilling (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
EP01105981A 2000-03-17 2001-03-10 Marteau à coup actionné hydrauliquement Expired - Lifetime EP1136189B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10013270 2000-03-17
DE10013270A DE10013270A1 (de) 2000-03-17 2000-03-17 Fluidbetriebenes Schlagwerk

Publications (3)

Publication Number Publication Date
EP1136189A2 true EP1136189A2 (fr) 2001-09-26
EP1136189A3 EP1136189A3 (fr) 2003-08-13
EP1136189B1 EP1136189B1 (fr) 2004-05-12

Family

ID=7635278

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01105981A Expired - Lifetime EP1136189B1 (fr) 2000-03-17 2001-03-10 Marteau à coup actionné hydrauliquement

Country Status (6)

Country Link
US (1) US6334495B2 (fr)
EP (1) EP1136189B1 (fr)
JP (1) JP4891484B2 (fr)
AT (1) ATE266503T1 (fr)
DE (2) DE10013270A1 (fr)
ES (1) ES2218294T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105710845A (zh) * 2014-12-17 2016-06-29 卡特彼勒公司 具有可变冲程控制的液压锤

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6557652B2 (en) * 2000-05-18 2003-05-06 Guenter Klemm Method for performing ground or rock work and hydraulic percussion device
DE10123202A1 (de) 2001-05-12 2002-11-14 Krupp Berco Bautechnik Gmbh Verfahren und Vorrichtung zur Absicherung eines fluidbetriebenen Schlagwerks gegen Leerschläge
DE102004035306A1 (de) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Druckmittelbetriebene Schlagvorrichtung insbesondere Hydraulikhammer
DE102004035289A1 (de) * 2004-07-21 2006-02-16 Kennametal Widia Gmbh & Co.Kg Werkzeug
EP1987255B1 (fr) * 2006-02-21 2012-06-06 FESTO AG & Co. KG Systeme pneumatique d'entrainement
FI123634B (fi) * 2007-10-05 2013-08-30 Sandvik Mining & Constr Oy Kallionrikkomislaite, suojaventtiili sekä menetelmä kallionrikkomislaitteen käyttämiseksi
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JP4891484B2 (ja) 2012-03-07
DE50102232D1 (de) 2004-06-17
DE10013270A1 (de) 2001-09-20
EP1136189B1 (fr) 2004-05-12
ATE266503T1 (de) 2004-05-15
ES2218294T3 (es) 2004-11-16
US20010022229A1 (en) 2001-09-20
US6334495B2 (en) 2002-01-01
JP2001315074A (ja) 2001-11-13
EP1136189A3 (fr) 2003-08-13

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