EP0934804B1 - Dispositif à percussion actionné par fluide - Google Patents

Dispositif à percussion actionné par fluide Download PDF

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Publication number
EP0934804B1
EP0934804B1 EP99101199A EP99101199A EP0934804B1 EP 0934804 B1 EP0934804 B1 EP 0934804B1 EP 99101199 A EP99101199 A EP 99101199A EP 99101199 A EP99101199 A EP 99101199A EP 0934804 B1 EP0934804 B1 EP 0934804B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
line
control
shut
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
EP99101199A
Other languages
German (de)
English (en)
Other versions
EP0934804A2 (fr
EP0934804A3 (fr
Inventor
Heinz-Jürgen Dr.-Ing. Prokop
Marcus Dr.-Ing. Geimer
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
Atlas Copco Construction Tools GmbH
Atlas Copco Construction Tools AB
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 Atlas Copco Construction Tools GmbH, Atlas Copco Construction Tools AB filed Critical Atlas Copco Construction Tools GmbH
Publication of EP0934804A2 publication Critical patent/EP0934804A2/fr
Publication of EP0934804A3 publication Critical patent/EP0934804A3/fr
Application granted granted Critical
Publication of EP0934804B1 publication Critical patent/EP0934804B1/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
    • 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 fluid-operated impact device, in particular hydraulic hammer, consisting of a pressure medium-driven percussion with a reciprocating under the action of a control percussion piston and a guide unit on which the striking mechanism is supported, the impact device to adapt to the supplied input power in addition to a Pressure monitor trained control valve is equipped.
  • a fluid-operated impact device in particular hydraulic hammer, consisting of a pressure medium-driven percussion with a reciprocating under the action of a control percussion piston and a guide unit on which the striking mechanism is supported, the impact device to adapt to the supplied input power in addition to a Pressure monitor trained control valve is equipped.
  • Pressure medium-operated impact devices - which are used in particular for crushing rock, concrete or other building materials - are used in most cases as auxiliary or attachment devices for construction equipment such as excavators, loaders or other carrier units.
  • Such an application is, for example, in the document DE 40 36 918 A1 shown and described, wherein the impact device is attached to the boom of a hydraulic excavator and connected via a pressure line and return line to the supply unit of the hydraulic excavator.
  • the impact mechanism itself supporting guide unit can be designed as a housing (hammer case) or as a support frame.
  • the movement of the percussion piston in the direction of the working stroke or the opposite return stroke is caused by a control, which is assigned to the striking mechanism or integrated in this.
  • the control can be equipped in particular with a movable spool, which acts on two opposite in the direction of movement, different sized annular surfaces of the percussion piston, that the smaller (effective in return direction) annular surface constantly with the pressure line and the larger (effective in working direction) annular surface over the spool is alternately connected to the pressure line and the return line.
  • the invention has for its object to design a fluid-operated impact device of the type mentioned in such a way that it can be used without additional retrofitting with control units in connection with differently designed supply units for construction machinery.
  • the percussion device itself should be designed such that its percussion mechanism - regardless of the input power provided by the associated supply unit - is protected against inadmissible operating states in the sense of overstressing.
  • control valve consisting of a pressure shut-off valve or of a pressure relief valve is in communication with the pressure line pressurized with the working pressure and the percussion mechanism - if the working pressure that arises due to the input power exceeds a predetermined maximum value - automatically shut down by either the pressure line blocked or the controller is held in one of its end positions, namely the working stroke position or the return stroke position. Accordingly, the pressure shut-off valve or the pressure relief valve with respect to the impact mechanism is switched so that this and its control is not exposed by the supplied pressure medium unduly high stress.
  • the percussion device Since the percussion mechanism is shut down when required under the action of the pressure shut-off valve or the pressure limiting valve, which forms part of the guide unit or percussion mechanism itself, that is part of the percussion device, the percussion device can be used without retrofitting in connection with construction machines of different design with regard to their input power. Accordingly, the impact device is ready for use without the need to avoid any overuse retrofitting on site.
  • the pressure shut-off valve or the pressure relief valve can in particular also form part of the impact mechanism itself, which is integrated in this. If the working pressure acting on the impact mechanism with the interposition of a pressure shut-off valve has an inadmissibly high value, the pressure shut-off valve is automatically transferred to its blocking position, whereby the energy supply to the impact device is interrupted. For their re-commissioning, it is then only necessary that the supplied from the supply unit input power - for example, by reducing the speed of the associated pump unit - is adjusted accordingly.
  • the subject invention may be further formed in such a way that the pressure shut-off valve or the pressure relief valve is connected via an additional line to the controller, that this is blocked when exceeding the set on Druckabschaltventil or pressure relief valve working pressure peak in one of its end positions (claim 2).
  • This blockage can be brought about in particular by the fact that a control surface acting on the control is subjected to corresponding pressure under the action of the relevant control valve.
  • the Druckabschaltventil or the pressure relief valve acts directly on the controller with the result that this is finally held in a certain end position and thus the percussion no longer carries out more strokes.
  • the pressure shut-off valve may in particular be equipped with a double piston, which has, on the one hand, an effective provision in the direction of the open position and, on the other hand, an effective valve in the opposite direction; the latter is connected via a control line on the input side to the pressure line (claim 3).
  • a double piston which has, on the one hand, an effective provision in the direction of the open position and, on the other hand, an effective valve in the opposite direction; the latter is connected via a control line on the input side to the pressure line (claim 3).
  • the pressure limiting valve is connected on the input side to the pressurized line acted upon by the working pressure, from which its switching line emanates (claim 4). Furthermore, the pressure relief valve may be designed and connected such that it blocks the control in the working stroke position in its open position after exceeding the maximum working pressure (claim 5).
  • the pressure relief valve may also be connected via a switching line to the pressure line acted upon by the working pressure and the output side to a non-pressurized return line; the controller is designed such that it is blocked in the return stroke position, if the pressure relief valve when it exceeds the maximum operating pressure assumes its open position (claim 6).
  • the equipped with a pressure shut-off valve embodiment may be further designed so that the pressure shut-off valve is connected via a switching line with the pressure applied to the working pressure line and designed so that it exceeds the working pressure maximum occupies the blocking position with the result that the Pressure shut-off valve connected Um laketechnisch for the transfer of the control is blocked in the working stroke position (claim 7).
  • the hammer mechanism is always protected against an inadmissibly high working pressure, despite the use of the pressure shut-off valve or pressure relief valve, it should be structurally designed for the highest possible pressure provided with the input power.
  • This point of view can be met in that the percussion is structurally (by appropriate design of its wall thickness and its remaining components) designed statically for the highest possible pressure. This can be determined with regard to the relevant characteristic values of the construction machines or associated supply units which are introduced in the market and which could be considered for interaction with the impact device.
  • a supply unit 2 (consisting essentially of a diesel engine, not shown, and driven by this hydraulic pump), which - as known for example from the document DE 40 36 918 A1 - via a Pressure line 3 and a non-pressurized return line 4 (see Fig. 1 a) is connected to a fluid-operated impact device 5.
  • the latter is adjustably held on the boom 6 of the hydraulic excavator with two boom arms 6a, 6b.
  • the impact device 5 has, as a guide unit, a support frame 7 which is articulated relative to the extension arm 6b and in which a percussion-driven impact mechanism 8 (for example shown in FIG. 3) is supported. From the support frame 7 projects out a tool in the form of a chisel 9, which acts on the aforementioned percussion in a conventional manner.
  • Fig. 1a is further shown schematically that the impact device 5, a controller 10 and - to adapt to the provided by the supply unit 2 available hydraulic input power - additionally designed as a pressure monitor control valve 11.
  • control valve 11 may be part of the support frame 7 or the percussion mechanism 8 or integrated into the latter (cf., for example, FIG. 3).
  • control valve is designed as Druckabschaltventil 12 and connected to the connected to the percussion, acted upon by the working pressure pressure line 3.
  • the pressure shut-off valve 12 forms part of the support frame 7.
  • the pressure shut-off valve 12 has within a housing 13 a double piston 14; this is designed and connected such that it only connects the pressure line 3 with its output-side continuation 3a, if the working pressure in the pressure line 3 does not exceed a predetermined maximum value.
  • the housing 13 is provided with a connected to the pressure line 3 control line 15; this opens on the side of the double piston 14 in a valve chamber 16, which is opposite to the acted upon by a return spring 17 page.
  • the double piston has a tendency to occupy the illustrated open position, in which the lines 3 and 3a are interconnected, as long as in the valve chamber 16 acting on the double piston 14 counterforce does not exceed the restoring force.
  • the double piston 14 moves (in the illustration) downwards and finally reaches the blocking position in which the connection between the lines 3 and 3a is interrupted. Accordingly, the striking mechanism 8 downstream of the pressure shut-off valve 12 (cf., for example, FIG. 3) is then shut down by switching off the energy supply.
  • the percussion device 8 which forms part of the percussion device 5 can be designed as desired in the context of the invention, in particular also with regard to its controller 10.
  • the percussion mechanism 8 has a percussion piston 18, which is held reciprocably in the longitudinal direction within a working cylinder 19 and cooperates with the aforementioned chisel 9.
  • the percussion piston 18 has in the cylinder space of the working cylinder 19 lying on two piston collars 18a and 18b, which are separated by a circumferential groove 18c.
  • the outwardly directed piston surface A1 and A2 of the piston collar 18b or 18a defines with the working cylinder 19 a rear and front cylinder space portion 19a and 19b, wherein the piston area A1 is dimensioned smaller than the piston area A2.
  • the smaller piston area A1 is constantly exposed to working pressure (system pressure) via a return line 20 extending from the continuation 3a of the pressure line 3.
  • the opening 20a of the return line 20 is arranged with respect to the working cylinder 19 so that it lies in any case outside of the piston collar 18b and thus within the front cylinder chamber portion 19b.
  • the cylinder chamber of the working cylinder 19 is (in Fig. 3 on the left side) provided with a conduit 21 which merges into the return line 4.
  • the associated junction 21 a in the cylinder chamber is arranged such that it lies in the indicated impact position of the percussion piston 18 between the piston collars 18 a and 18 b.
  • the control (designated by "10" in FIG. 1a) for switching the movement of the percussion piston 18 consists of a 2/2-way valve 22; this has two differently sized control surfaces - namely, a smaller control surface S1 and a counter-directed to larger control surface S2.
  • the smaller control surface S1 is connected via a control line 23 to the continuation 3a of the pressure line 3 and accordingly effective in the sense of a provision.
  • the larger control surface S2 is connected via a reversing line 24 on the one hand to the output of a pressure relief valve 25 and on the other hand with the cylinder chamber in connection; its junction 24a is arranged with respect to the working cylinder 19 so that it is also in the illustrated Aufschlag too the percussion piston 18 between the two piston collars 18a and 18b.
  • junction 21a is further away from the front cylinder space portion 19b than the junction 24a.
  • the pressure relief valve 25 is connected on the input side to the acted upon by the working pressure continuation 3a, via an additional line 26, from which also its switching line 25a starts.
  • the 2/2-way valve 22 is further configured such that it is on the one hand on the input side with the continuation 3a and the return line 4 and the other on the output side via a reversing line 22a with the rear cylinder space portion 19a in connection.
  • the 2/2-way valve 22 is operated under the action of its control surfaces S1 and S2 so that it connects the rear cylinder chamber portion 19a alternately with the continuation 3a or the return line 4. This has the consequence that the percussion piston 18 is driven either in the working stroke direction (i.e., in the representation downward) or in the return stroke direction, counter to the return effect emanating from the smaller piston surface A1.
  • control in the form of the 2/2-way valve 22 is likewise assigned a pressure limiting valve 27; this is the input side via an additional line 28 - from which also its switching line 27a goes - with the continuation 3a of the pressure line 3 and the output side with a third control surface S3 of the 2/2-way valve 22 in conjunction.
  • the third control surface S3 is also sized larger than the control surface S1 and effective for pressurization in the direction of the not shown working stroke position of the 2/2-way valve 22.
  • the pressure relief valve 27 applied working pressure exceeds the predetermined maximum value, the pressure relief valve is transferred to the open position, not shown, with the result that the 2/2-way valve 22 finally occupies the working stroke position and is blocked in this, regardless of the position the percussion piston 18 within the cylinder space. Due to the blocking of the control in the aforementioned end position, the percussion piston can not perform any further blows during this time.
  • FIG. 5 differs from the aforementioned embodiment of FIG. 4 in that the control is optionally blocked in another end position.
  • the control in the form of the 2/2-way valve 22 via an additional line 30 is connected upstream of a pressure relief valve 29 with an on the input side into the additional line 30 opening switching line 29a.
  • the pressure relief valve 29 is connected via the additional line 30 with a control surface S4 in connection. This is - as well as the smaller control surface S1 - effective in the direction of remindhub ein and dimensioned so that they together with the smaller control surface S1 optionally generates a greater restoring force than the effective in the opposite direction control surface S2.
  • the embodiment according to FIG. 6 also has a pressure limiting valve 31 (shown differently), which cooperates with the control in the form of the 2/2-way valve 22.
  • the pressure relief valve 31 is connected via an additional line 32 on the one hand with the non-pressurized return line 4 and on the other hand with the reversing line 24, which acts on the larger control surface S2.
  • the pressure relief valve via a switching line 31 a control technology connected to the continuation of the pressure line 3 3a. If the working pressure in the switching line 31 a exceeds the predetermined maximum value, the pressure limiting valve 31 is transferred from the illustrated blocking position to the open position and thereby relieved of pressure then connected to the return line 4 reversing line 24.
  • control valve in the form of a Druckabschaltventils 33 is switched directly into the reversing line 24 of the 2/2-way valve 22, wherein the associated switching line 33a opens into the continuation 3a of the pressure line 3.
  • the pressure shut-off valve 33 is transferred from the illustrated open position to the blocking position, thereby blocking the Um Kunststoff 24 toward the 2/2-way valve 22 and this held in an end position, thereby further Working movements of the percussion piston 18 can be prevented.
  • the advantage achieved by the invention is, in particular, that the input power supplied from the outside can be adapted with simple technical means to differently designed and designed supply units, wherein a possibly expensive retrofitting of the respective carrier device or the supply unit can be dispensed with.
  • the embodiment of the invention has the consequence that the impact device is automatically stopped if the working pressure acting on it assumes an inadmissibly high value.
  • the striking mechanism as a whole should be designed such that it can withstand the maximum pressure that can be generated by a suitable supply unit introduced on the market.

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  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Pens And Brushes (AREA)
  • Chair Legs, Seat Parts, And Backrests (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (7)

  1. Dispositif à percussion (5) actionné par fluide, en particulier marteau hydraulique, se composant d'un mécanisme à percussion (8) actionné par fluide comprenant un piston percutant (18) actionné d'un mouvement de va-et-vient sous l'action d'une commande (10, 22), et d'une unité de guidage (7) sur laquelle ledit mécanisme à percussion est appuyé, le dispositif à percussion (5) étant équipé en sus - pour l'adaptation à la puissance d'entrée amenée - d'une soupape de contrôle (11) réalisée comme contrôle de pression, caractérisé par le fait que la soupape de contrôle (11) réalisée comme soupape de coupure de pression (12, 33) ou comme soupape de limitation de pression (25, 27, 29, 31) - qui forme une partie composante de l'unité de guidage (7) ou du mécanisme à percussion (8) même - est en communication avec la conduite de pression (3) alimentée en pression de travail et arrête le mécanisme à percussion (8) - si la pression de travail se présentant en raison de la puissance d'entrée dépasse une valeur maximale donnée - automatiquement par le fait que soit la conduite de pression (3) est bloquée soit la commande (10) est retenue dans l'une de ses positions extrêmes, à savoir la position de course de travail ou la position de course de retour.
  2. Dispositif selon la revendication 1, caractérisé par le fait que la soupape de coupure de pression (12, 33) ou la soupape de limitation de pression (25, 27, 29, 31) est reliée via une conduite additionnelle (26, 28, 30, 32) à la commande (22) de manière à ce que celle-ci soit bloquée dans l'une de ses positions extrêmes lorsque la valeur maximale de la pression de travail, réglée sur la soupape de coupure de pression ou sur la soupape de limitation de pression est dépassée.
  3. Dispositif selon la revendication 1 ou 2, caractérisé par le fait que la soupape de coupure de pression (12) est équipée d'un double-piston (14) qui présente d'une part un dispositif de rappel (17) agissant dans la direction de la position d'ouverture et d'autre part une chambre de soupape (16) agissant dans le sens opposé qui, du côté de l'entrée, est reliée via une conduite de commande (15) à la conduite de pression (3).
  4. Dispositif selon la revendication 2, caractérisé par le fait que, du côté de l'entrée, la soupape de limitation de pression (25, 27, 29) est connectée à la conduite de pression (3a) alimentée en pression de travail de laquelle part aussi la ligne de commutation (25a, 27a, 29a) de cette soupape.
  5. Dispositif selon la revendication 4, caractérisé par le fait que, dans sa position d'ouverture, la soupape de limitation de pression (25, 27) bloque la commande (22) dans la position de course de travail après que la valeur maximale de la pression de travail a été dépassée.
  6. Dispositif selon la revendication 2, caractérisé par le fait que la soupape de limitation de pression (31) est connectée d'une part, via une ligne de commutation (31a), à la conduite de pression (3a) alimentée en pression de travail et, d'autre part, du côté de la sortie, à une conduite de retour (4) exempte de pression, la commande (22) étant réalisée de manière à être bloquée dans la position de course de retour si la soupape de limitation de pression (31) prend sa position d'ouverture lorsque la valeur maximale de la pression de travail est dépassée.
  7. Dispositif selon la revendication 2, caractérisé par le fait que la soupape de coupure de pression (33) est reliée, via une ligne de commutation (33a), à la conduite de pression (3a) alimentée en pression de travail et est réalisée de manière à prendre la position d'arrêt lorsque la valeur maximale de la pression de travail est dépassée, avec la conséquence que la conduite de renversement (24) connectée à la soupape de coupure de pression (33) et destinée à faire passer la commande (22) dans la position de course de travail est bloquée.
EP99101199A 1998-01-30 1999-01-22 Dispositif à percussion actionné par fluide Expired - Lifetime EP0934804B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803449A DE19803449A1 (de) 1998-01-30 1998-01-30 Druckmittelbetriebene Schlagvorrichtung
DE19803449 1998-01-30

Publications (3)

Publication Number Publication Date
EP0934804A2 EP0934804A2 (fr) 1999-08-11
EP0934804A3 EP0934804A3 (fr) 2003-03-05
EP0934804B1 true EP0934804B1 (fr) 2006-01-11

Family

ID=7856037

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99101199A Expired - Lifetime EP0934804B1 (fr) 1998-01-30 1999-01-22 Dispositif à percussion actionné par fluide

Country Status (5)

Country Link
US (1) US6959967B1 (fr)
EP (1) EP0934804B1 (fr)
AT (1) ATE315457T1 (fr)
DE (2) DE19803449A1 (fr)
ES (1) ES2257827T3 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10013270A1 (de) * 2000-03-17 2001-09-20 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
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
DE102006026274A1 (de) 2006-06-02 2007-12-06 Willy Vogel Ag Selbsttätige Schmierpumpe mit doppelt wirkendem Antriebskolben
US8939227B2 (en) 2010-12-23 2015-01-27 Caterpillar Inc. Pressure protection valve for hydraulic tool
RU2476644C1 (ru) * 2011-10-06 2013-02-27 Учреждение Российской академии наук Институт горного дела Сибирского отделения РАН Регулируемая ударная машина
GB2522625A (en) * 2014-01-29 2015-08-05 Mincon Internat Ltd Pressure control system
US9701003B2 (en) 2014-05-23 2017-07-11 Caterpillar Inc. Hydraulic hammer having delayed automatic shutoff
RU2567059C1 (ru) * 2014-10-20 2015-10-27 Федеральное государственное бюджетное учреждение науки Институт горного дела им. Н.А. Чинакала Сибирского отделения Российской академии наук Регулируемая ударная машина (варианты)
US9840000B2 (en) * 2014-12-17 2017-12-12 Caterpillar Inc. Hydraulic hammer having variable stroke control
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
US10377028B2 (en) 2016-03-14 2019-08-13 Caterpillar Inc. Hammer protection system and method
ES2733769B2 (es) * 2018-05-31 2020-05-26 Mayor Gines Perez Martillo hidráulico para demolición

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3664435A (en) 1970-11-09 1972-05-23 Worthington Corp Worthington C Hydraulic hammer with automatic stopping action
FI50390C (fi) * 1973-09-14 1976-03-10 Murskauskone Oy Hydraulisesti käytetty iskulaite
US4006783A (en) * 1975-03-17 1977-02-08 Linden-Alimak Ab Hydraulic operated rock drilling apparatus
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
FR2397578A1 (fr) * 1977-07-13 1979-02-09 Baudet Alain Dispositif de securite pour supprimer les risques d'accident sur les machines hydrauliques
DE2737081C3 (de) 1977-08-17 1980-07-24 Frank 3380 Goslar Habsick Hydraulischer Drehschlaghammer
JPS59185234A (ja) * 1983-04-05 1984-10-20 Kubota Ltd フロントロ−ダの制御装置
EP0190703B1 (fr) * 1985-02-04 1988-05-25 Hitachi Construction Machinery Co., Ltd. Système de commande pour un circuit hydraulique
US4900093A (en) * 1986-11-10 1990-02-13 Caterpillar Inc. Impact ripper and control
DE4036918A1 (de) * 1990-11-20 1992-05-21 Krupp Maschinentechnik Verfahren zur anpassung des arbeitsverhaltens eines schlagwerks an die haerte des zerkleinerungsmaterials und einrichtung zur durchfuehrung des verfahrens
DE4128137A1 (de) 1991-08-24 1993-02-25 Krupp Maschinentechnik Sicherheitseinrichtung fuer fluidbetriebene schlagwerke
US5417294A (en) * 1994-03-15 1995-05-23 American Pneumatic Technologies Pneumatic hammer
FI104959B (fi) 1994-06-23 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
FI104960B (fi) * 1995-07-06 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara

Also Published As

Publication number Publication date
US6959967B1 (en) 2005-11-01
EP0934804A2 (fr) 1999-08-11
EP0934804A3 (fr) 2003-03-05
ES2257827T3 (es) 2006-08-01
DE59913032D1 (de) 2006-04-06
DE19803449A1 (de) 1999-08-05
ATE315457T1 (de) 2006-02-15

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