EP0475171B1 - Hydraulisch betriebenes Schlagwerk - Google Patents

Hydraulisch betriebenes Schlagwerk 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
Authority
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
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0475171A2 (de
EP0475171A3 (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Krupp Maschinentechnik GmbH filed Critical Krupp Maschinentechnik GmbH
Publication of EP0475171A2 publication Critical patent/EP0475171A2/de
Publication of EP0475171A3 publication Critical patent/EP0475171A3/de
Application granted granted Critical
Publication of EP0475171B1 publication Critical patent/EP0475171B1/de
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
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • the 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.

Landscapes

  • 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)
EP91114231A 1990-09-08 1991-08-24 Hydraulisch betriebenes Schlagwerk Expired - Lifetime EP0475171B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4028595 1990-09-08
DE4028595A DE4028595A1 (de) 1990-09-08 1990-09-08 Hydraulisch betriebenes schlagwerk

Publications (3)

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

Family

ID=6413902

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91114231A Expired - Lifetime EP0475171B1 (de) 1990-09-08 1991-08-24 Hydraulisch betriebenes Schlagwerk

Country Status (5)

Country Link
US (1) US5129466A (xx)
EP (1) EP0475171B1 (xx)
JP (1) JPH05138549A (xx)
AT (1) ATE128895T1 (xx)
DE (2) DE4028595A1 (xx)

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Publication number Priority date Publication date Assignee Title
US5398772A (en) * 1993-07-01 1995-03-21 Reedrill, Inc. Impact hammer
SE508064C2 (sv) * 1993-10-15 1998-08-17 Atlas Copco Rock Drills Ab Bergborrningsanordning med reflexdämpare
DE4343589C1 (de) * 1993-12-21 1995-04-27 Klemm Guenter Fluidbetätigter Schlaghammer
ES2144125T3 (es) * 1994-02-28 2000-06-01 Berema Atlas Copco Ab Sistema de valvulas en motores de aire comprimido.
DE4424081C2 (de) * 1994-07-08 1996-08-14 Klemm Bohrtech Fluidbetätigter Schlaghammer
JPH11508187A (ja) * 1995-06-21 1999-07-21 ヒドロプルソール アーベー 衝撃装置
US5752571A (en) * 1995-12-15 1998-05-19 Sapozhnikov; Zinoviy A. Apparatus for generating impacts
KR100260308B1 (ko) * 1997-06-11 2000-07-01 최해성 개선된 실링을 갖는 유압헤머
JP3817617B2 (ja) * 1999-05-10 2006-09-06 新日本製鐵株式会社 さく孔装置
DE19923680B4 (de) * 1999-05-22 2004-02-26 Atlas Copco Construction Tools Gmbh Verfahren zur Ermittlung der Betriebsdauer und des Einsatz-Zustands eines hydraulischen Schlagaggregats, insbesondere Hydraulikhammer, sowie Vorrichtung zur Durchführung des Verfahrens
US6308779B1 (en) 1999-09-16 2001-10-30 Mcneilly A. Keith Hydraulically driven fishing jars
AUPR430201A0 (en) * 2001-04-09 2001-05-17 Russell Mineral Equipment Pty Ltd Linerbolt removing tool
US6932166B1 (en) * 2002-12-03 2005-08-23 Paul Kirsch Pneumatic tool
FI116968B (fi) * 2004-07-02 2006-04-28 Sandvik Tamrock Oy Menetelmä iskulaitteen ohjaamiseksi, ohjelmistotuote sekä iskulaite
FI121027B (fi) * 2004-09-24 2010-06-15 Sandvik Mining & Constr Oy Menetelmä iskevän kallionporauksen ohjaamiseksi, ohjelmistotuote sekä kallionporauslaite
FI123740B (fi) * 2005-01-05 2013-10-15 Sandvik Mining & Constr Oy Menetelmä painenestekäyttöisen iskulaitteen ohjaamiseksi ja iskulaite
FI118052B (fi) * 2005-06-27 2007-06-15 Sandvik Tamrock Oy Menetelmä ja ohjelmistotuote porausyksikön paikoittamiseksi sekä kallionporauslaite
SE529615C2 (sv) * 2006-02-20 2007-10-09 Atlas Copco Rock Drills Ab Slagverk och bergborrmaskin samt förfarande för att styra slagkolvens slaglängd
SE530781C2 (sv) * 2007-01-11 2008-09-09 Atlas Copco Rock Drills Ab Bergborrutrustning och metod i anslutning till denna
SE534815C2 (sv) * 2010-05-03 2012-01-10 Atlas Copco Rock Drills Ab Bergborrmaskin med dämpkolv
SE535801C2 (sv) * 2011-04-27 2012-12-27 Atlas Copco Rock Drills Ab Slagverk, bergborrmaskin och borrigg
US10493610B2 (en) * 2014-01-31 2019-12-03 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커

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DE3523219C1 (de) * 1985-06-28 1986-06-26 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Hydraulischer Bagger

Also Published As

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

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