EP0394765A1 - Mécanisme à coup hydraulique - Google Patents

Mécanisme à coup hydraulique Download PDF

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Publication number
EP0394765A1
EP0394765A1 EP90107000A EP90107000A EP0394765A1 EP 0394765 A1 EP0394765 A1 EP 0394765A1 EP 90107000 A EP90107000 A EP 90107000A EP 90107000 A EP90107000 A EP 90107000A EP 0394765 A1 EP0394765 A1 EP 0394765A1
Authority
EP
European Patent Office
Prior art keywords
piston
return
chamber
percussion
channel
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
EP90107000A
Other languages
German (de)
English (en)
Other versions
EP0394765B1 (fr
Inventor
Friedrich-Karl Dr.-Ing. Arndt
Robert Dr.-Ing. Bartels
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
Priority to AT90107000T priority Critical patent/ATE84739T1/de
Publication of EP0394765A1 publication Critical patent/EP0394765A1/fr
Application granted granted Critical
Publication of EP0394765B1 publication Critical patent/EP0394765B1/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
    • B25D9/145—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D2209/007—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously having a tubular-slide valve, which is not coaxial with the piston

Definitions

  • the invention relates to a hydraulic percussion mechanism with a cylinder, a percussion piston guided therein and a piston return device, the percussion piston being pressurized on one side with a compressible drive means (pressurized gas) and the piston return device, via which the percussion piston can be retrieved against the direction of its working stroke and which, on its side facing the percussion piston tip, can alternately be connected to a pressure source for an incompressible drive means (hydraulic oil) and to an unpressurized return line, is slidably supported on the percussion piston independently of the latter.
  • a compressible drive means pressurized gas
  • the known percussion mechanisms have in common that the incompressible drive means is directly coupled to the opposing piston surfaces of the percussion piston.
  • the incompressible drive means ie the hydraulic oil
  • the incompressible drive means is in front of the one piston surface ousted and tracked behind the other.
  • the liquid columns in front of and behind the two piston surfaces have the same speed as the percussion piston itself.
  • the percussion piston hits the chisel or, if it strikes directly, the material to be processed, the percussion piston is suddenly decelerated.
  • the liquid column in front of the piston surface continues to move in the direction of impact; this creates the risk of cavitation.
  • Considerable pressure peaks occur on the opposite piston surface due to the sudden deceleration of the impact piston and the liquid column.
  • the direct coupling of the incompressible drive means to the movement of the percussion piston is also disadvantageous insofar as the flow cross sections in the associated channels and in the control have to be adapted to the highest piston speed that occurs.
  • a percussion mechanism of the type mentioned at the outset with a piston return device which - enclosing the percussion piston on the side facing away from the percussion piston tip by a distance - is connected to piston rods on its side facing the percussion piston tip.
  • the piston return device During the working stroke of the percussion piston in the striking direction, the piston return device is released from the percussion piston after unlocking the pawl and races in the striking direction.
  • the disadvantage of the known percussion mechanism is that the coupling and uncoupling of the piston return device, which takes place mechanically, is complex in terms of production technology and prone to failure. Due to the comparatively large mass of the components interacting overall, the piston return device only allows impact rates in the order of magnitude of not more than 60 / min. to.
  • the invention has for its object to provide a percussion mechanism, the piston return device decoupled during the working stroke of the percussion piston is as simple as possible, in particular has hardly any mechanically effective additional components, and which also allows high numbers of blows with the lowest possible mass.
  • the piston return device should also be designed in such a way that it can be braked independently of the impact of the impact piston.
  • a suitable configuration of the subject matter of the invention is also intended to open up the possibility of realizing a continuous adjustment of the piston stroke, and thus the impact energy and the impact rate.
  • the task is solved by a striking mechanism with the features of claim 1.
  • the basic idea of the invention is to design the piston return device as an annular piston which rests freely against the cylinder and against the cylinder in the longitudinal direction of the percussion piston and which has an annular surface of the cylinder on the side facing the percussion piston tip which is separate from the compressible drive means (compressed gas) Piston space limited in the axial direction; the freedom of movement of the annular piston with respect to the percussion piston against the direction of impact is determined by a stop surface attached to it.
  • the percussion mechanism has an oil chamber which is arranged at a distance from it and which the percussion piston delimits with the cylinder.
  • the end position of the percussion piston on the return stroke is limited by a cylindrical percussion piston shoulder located in the oil chamber.
  • a control is assigned to the piston chamber and the oil chamber, by means of which, on the one hand, with the approach of the percussion piston shoulder to the rear of the oil chamber facing the piston chamber, the latter can be connected to the return line and, on the other hand, with the approach of the leading in the direction of impact (with respect to the percussion piston) Ring piston to the ring surface of the cylinder the piston chamber can be connected to the pressure source.
  • the ring piston is effective as a piston return device in that the piston chamber is acted upon by the pressure of the pressure source under the influence of the control and that the ring piston resting on the stop surface of the percussion piston counteracts the force exerted by the compressed gas on the percussion piston in the direction of impact and against the direction of impact - carries along.
  • the annular piston used as the control and return element has the shape of a simply designed hollow cylinder.
  • gas space and "oil space” are only intended to express that the spaces in question are or can be acted upon by a suitable compressible or incompressible drive means; the drive means used in the piston chamber is also incompressible.
  • the gas space serves to drive the percussion piston in the direction of impact after the return stroke has ended, wherein the freely displaceable ring piston - due to its lower mass - is initially accelerated faster in the direction of impact and consequently leads the working stroke movement of the impact piston.
  • the control system expediently consists of a hollow slide movable in a control chamber, which can be moved into a return stroke position with the approach of the annular piston to the cylinder ring surface and into a working stroke position with the opposite approach of the working piston shoulder to the rear side of the oil chamber.
  • a plurality of pressure and return channels which are connected to the pressure source or the return, and on the other hand four channels open into the control chamber, two of which each merge into the piston chamber or oil chamber (claim 2).
  • the respective operating position of the control is therefore dependent on the position of the ring piston with respect to the cylinder ring area delimiting the piston chamber or on the position of the working piston shoulder with respect to the rear side of the oil chamber:
  • the control enables the pressurization of the ring piston required for the working cycle of the percussion piston or the discharge of the incompressible drive means from the piston chamber and the oil chamber into the unpressurized return.
  • the channels assigned to the piston chamber and the oil chamber are arranged in the following manner and switched: - The mouth of the first piston chamber channel - which is constantly connected to the pressure source - is further away from the cylinder ring surface than the mouth of the second piston chamber channel; - The mouth of the second oil space channel - which is constantly connected to the return - is further away from the rear of the oil space than the mouth of the first oil space channel, which is permanently connected to the pressure source, in the vicinity thereof.
  • the second piston chamber channel is on the control during the return stroke at least up to the approach of the working piston shoulder to the mouth of the first oil chamber channel with the pressure source or during the working stroke at least until the annular piston approaches the mouth of the first piston chamber - Channel with the return in connection (claim 3).
  • the hollow slide valve the interior of which is connected to the pressure source, has five differently sized annular work surfaces on its outside, namely two work surfaces for generating pressure forces effective in the direction of the working stroke and three work surfaces for generating the opposite pressure forces , towards the return stroke position of effective pressure forces.
  • the first and the second work surfaces which are designated in accordance with their sequence in the direction of the working stroke position, are common as large as the total area formed from the third to fifth working area; the first and the fifth working surface consist of the end face of the hollow slide which is effective in the direction of the return stroke or working stroke position (claim 4).
  • the hollow slide valve with the resulting pressure conditions in the piston chamber and in the oil chamber can be moved into one of its two end positions, namely the working stroke position or the return stroke position, which it maintains until further notice.
  • the working surfaces of the hollow slide are coordinated in size according to the following conditions:
  • the first work surface ie the one end surface
  • the fifth work surface thus the second end surface
  • the first working area is smaller than the sum of the third and fifth working area
  • the sum of the first and second work surfaces is greater than the sum of the third and fifth work surfaces (claim 5).
  • the subject of the invention can advantageously be further developed in that the second and the third working surface are each connected via an annular groove of the control chamber on the one hand to the pressure source and on the other hand to the first oil chamber channel or to the first piston chamber channel; that the fourth working surface is simultaneously connected to the second oil chamber channel and to a return channel via an annular groove in the control chamber; that the second piston chamber channel is connected to the control chamber via a first and a second annular groove which - seen in the direction of the working stroke position of the hollow slide valve - lies in front of the fourth working surface or behind the fourth working surface near the fifth working surface; that the control chamber is connected to a return channel via an annular groove, the annular groove - viewed in the direction of the working stroke position of the hollow slide valve - lying in the area behind the annular groove of the first piston chamber channel and in front of the first annular groove of the second piston chamber channel ( Claim 6).
  • the control effect of the hollow slide required for the working cycle of the percussion piston can also be realized in that it has an external annular groove which is arranged and designed such that the second piston chamber channel is only connected to the return via this annular groove when the Hollow pusher occupies a position at least in the vicinity of its working stroke position (claim 7).
  • the piston chamber is connected to the return via the annular groove of the hollow slide valve, with the result that the annular piston moving forward in the direction of impact is the one in the piston chamber Can displace liquid column.
  • the return channels are connected in a corresponding manner with the interposition of a throttle with the return (claim 9).
  • the first oil chamber channel is equipped with a prestressed passage valve with an adjustable adjusting force, the working position of which can be influenced via a control line (claim 10); According to the chosen designation, the flow control valve assumes the flow control or opening position as long as the control pressure in the control line does not exceed a predetermined limit value.
  • the working stroke of the percussion piston can be shortened and thus the impact energy and number of impacts can be changed: as long as the passage valve is in the passage position, it has no influence on the working cycle of the percussion piston; with the switching of the passage valve into the blocking position, the connection between the first oil chamber channel and the pressure source - regardless of the position of the working piston paragraph with respect to the oil chamber rear side - is interrupted with the result that the pressure acting on the second working surface increases and the hollow slide moves in the direction of its working stroke position.
  • the passage valve can be pressurized in particular by a control line connected to the gas space (claim 11). So if the pressure in the gas space is due to the movement of the percussion piston and the annular piston during the return stroke, exceeds a predetermined limit value, the passage valve switches into the blocking position, whereby the return stroke movement is interrupted.
  • the passage valve can advantageously also be remotely operable via a control line (claim 12). Such a design makes it possible to influence the working cycle of the percussion piston in the desired manner from the outside, either by hand or via a control unit.
  • the percussion mechanism has a percussion piston 1 with a percussion piston tip 1a, which faces the material 2 to be processed.
  • the percussion piston itself is guided to and fro in a cylinder 3 closed by a cover 3a in the direction of its longitudinal axis 4 (FIG. 1).
  • the drive-side end section 1b of the percussion piston facing away from the percussion piston tip 1a projects with a disk-shaped stop surface 5 attached to it into a gas space 6 filled with compressed gas, which can be connected via a line (not shown) to a compressed gas reservoir or a compressed gas source and can thus be refilled.
  • annular piston 8 which is freely displaceable both on the impact piston 1 and on the inner surface 3c starting from the ring surface 3b supports the cylinder 3; the ring piston 8 is sealed against the parts 1 and 3 by means of sealing elements 8a, 8b. Its length in the axial direction is dimensioned such that it has the lowest possible mass, without its sealing and guiding function being called into question.
  • the range of motion of the annular piston 8 with respect to the percussion piston 1 against the direction of impact is defined by the stop surface 5, the diameter of which - and maintaining a sufficient distance from the inner surface 3c - is greater than that Diameter of the end portion 1b of the percussion piston.
  • the range of motion of the annular piston 8 in the direction of impact is limited by the already mentioned annular surface 3b of the cylinder 3.
  • the gas space 6 is formed by the cylinder 3 together with the cover 3a, the ring piston 8 and the percussion piston 1.
  • the annular piston 8 and the annular surface 3b delimit a piston chamber 9 with variable capacity in the axial direction, which is laterally delimited by the inner surface 3c and the percussion piston itself; the movable wall of the piston chamber is formed by the end face 8d of the annular piston facing the annular surface 3b.
  • a first piston chamber channel 10 opens into the piston chamber and, with the interposition of an annular groove 11a, a second piston chamber channel 11. The mouth 10a of the first piston chamber channel is further away from the annular surface 3b than the mouth of the second piston chamber channel designed as an annular groove 11a.
  • the percussion piston 1 delimits an oil chamber 12 with the working cylinder 3, which - viewed in the direction of impact (arrow 7) - adjoins the piston chamber 9 at a distance.
  • the oil chamber has a first oil chamber channel 13 in the vicinity of its rear side facing the annular surface 3b and a second oil chamber channel 14 at a distance from it.
  • the mouth 13a of the first oil space channel merges into a cylindrical recess 12a of the oil space; the mouth 14a of the second oil space channel lies further from the rear of the oil space removed as the nearby mouth 13a of the first oil space channel.
  • the percussion piston itself is equipped with a cylindrical shoulder 1c lying in the oil chamber 12, by means of which its end position on the return stroke (against the direction of stroke according to arrow 7) is determined and by means of which the mouth 13a of the first oil chamber channel can be closed by approaching this end position .
  • the recess 12a and the shoulder 1c are adapted to one another in such a way that the percussion piston shoulder can be moved into the said recess with little play.
  • the percussion piston thus forms a type of shut-off valve with the recess 12a, which - depending on the position of the percussion piston shoulder 1c within the oil chamber 12 - releases or interrupts its connection to the first oil chamber channel 13.
  • the percussion piston shoulder has a frustoconical collar 1d on the side facing the percussion piston tip 1a, which collar can be inserted with tight play into a cylindrical recess 12b on the front side of the oil chamber facing the percussion piston tip.
  • a sealing element 15 which - seen in the direction of impact (arrow 7) - with Distance behind the recess 12b of the oil chamber 12 is mounted in the cylinder 3.
  • a control 16 is connected downstream of the piston chamber 9 and the oil chamber 12 via the two piston chamber channels 10, 11 and the two oil chamber channels 13, 14, via which, on the one hand, with the approach of the percussion piston shoulder 1c to the rear of the piston chamber 9
  • Oil chamber 12 which can be connected to an unpressurized return 17 and via which, on the other hand, with the approach of the annular piston 8 moving in the direction of impact (arrow 7) to the annular surface 3b, the piston chamber can be connected to a pressure source 18 and the oil chamber can also be connected to the pressure source.
  • the control 16 consists of a hollow slide 20 which is movable in a control chamber 19 and is cylindrical in basic form and which can be displaced into two end positions, namely into the return stroke position (FIG. 2a) or working stroke position (FIG. 2a). 2c).
  • the hollow slide 20, the interior 20a of which is constantly connected to the pressure source 18 via a pressure channel 21, has five ring-shaped work surfaces, namely - designated in accordance with their sequence in the direction of the working stroke position - a first and a second work surface A1 and A2, respectively serve to generate effective compressive forces in the direction of the working stroke, and a third to fifth working surface A3, A4 and A5 for producing opposing, in the direction effective return forces on the return stroke position.
  • the first and fifth working surfaces A1 and A5 are formed by the end surface of the hollow slide 20 which is effective in the direction of the return stroke or working stroke position; the work surfaces A2 to A4 protrude outwards over these end surfaces.
  • the work surfaces are coordinated in size so that they meet the following conditions: - The first work surface A1 is larger than the fifth work surface A5; - The first working area A1 is smaller than the sum of the third and fifth working area (A3 + A5); - The sum of the first and second work surfaces (A1 + A2) is greater than the sum of the third and fifth work surfaces (A3 + A5) and - The sum of the first and second work surfaces (A1 + A2) is as large as the total surface formed from the third to fifth work surfaces (A3 + A4 + A5).
  • control chamber 19 is equipped with six annular grooves 22 to 27. Via the annular grooves 22 and 23, the first oil chamber channel 13 or the first piston chamber channel 10 is connected to a pressure channel 28 or 29 equipped with a throttle 28a or 29a, which in turn is connected to the pressure source 18 via the pressure channel 21 is.
  • the control chamber 19 is connected to the second oil chamber channel 14, which is additionally connected to the return 17 via a branch 14b and the return channel 30.
  • the hollow slide 20 has an external annular groove 20b in the area between the work surfaces A3 and A4. This is arranged and designed such that the second piston chamber channel 11 is only connected to the return 17 via the latter when the hollow slide 20 assumes a position at least in the vicinity of its working stroke position.
  • the piston chamber channel 11 is connected to the return 17 via the annular groove 25, the hollow slide ring groove 20b, the annular groove 24 and the return channel 30 with the throttle 30a interposed.
  • the working surface A2 is connected to the return 17 via the annular groove 22, the first oil space channel 13, the cutout 12a, the oil space 12, the second oil space channel 14, the branch 14b and the return channel 30.
  • the annular groove 23 acted upon by the pressure source 18 via the pressure channels 21 and 29 is likewise connected to the piston chamber 9 via the first piston chamber channel 10; this is also connected to the pressure source 18 via the branch 11b of the second piston chamber channel 11, the annular groove 27, the control chamber 19 and the pressure channel 21. Since the pressure emanating from the pressure source 18 thus acts on the end face 8d of the annular piston 8, the percussion piston 1 is carried over the latter (whose end face 8c is supported on the stop face 5) in the direction of arrow 31 against the pressure force emanating from the gas space 6.
  • the Working surface A4 is continuously connected to the return 17 via the annular groove 26, the branch 14b of the second oil chamber channel and the return channel 30.
  • the pressure p supplied by the pressure source 18 is significantly greater than the pressure in the return line 17, the following applies to the control force in this operating state:
  • F St px (A1 - A2 - A3) ⁇ 0, ie the control force F St is, by definition, oriented in such a way that the hollow slide 20 bears against the end face 19b of the control chamber 19.
  • the annular piston 8 which is not coupled to the percussion piston 1 in terms of movement during the working stroke, initially closes the mouth 10a of the first piston chamber channel 10 and then also the annular groove 11a forming the mouth of the second piston chamber channel 11 when it approaches the annular surface 3b , causing the movement of the Ring piston is continuously braked in the direction of impact.
  • Fig. 3 shows an embodiment of the subject matter of the invention, in which the working stroke of the percussion piston 1 can be changed and thus the impact energy and number of impacts can be influenced.
  • the first oil chamber channel 13 is equipped with a passage valve 33, the operating position of which is predetermined by a spring 33a with an adjustable pretensioning force.
  • Pass valve 33 is also connected to gas space 6 in cylinder 3 via a connection bore 34 and a control line 35.
  • the passage valve 33 assumes the passage or opening position shown; in this the working cycle of the percussion piston 1 is not affected.
  • the passage valve 33 can also be operated remotely via a control line, either by hand or via a suitable control unit, via which the working position of the passage valve can be changed after an adjustable time period.
  • the object of the invention can be designed in such a way that either the percussion piston tip strikes the material to be processed either directly or with the interposition of a tool, ie indirectly.

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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)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Lubricants (AREA)
EP90107000A 1989-04-27 1990-04-11 Mécanisme à coup hydraulique Expired - Lifetime EP0394765B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90107000T ATE84739T1 (de) 1989-04-27 1990-04-11 Hydraulisches schlagwerk.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3913866 1989-04-27
DE3913866A DE3913866A1 (de) 1989-04-27 1989-04-27 Hydraulisches schlagwerk

Publications (2)

Publication Number Publication Date
EP0394765A1 true EP0394765A1 (fr) 1990-10-31
EP0394765B1 EP0394765B1 (fr) 1993-01-20

Family

ID=6379558

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90107000A Expired - Lifetime EP0394765B1 (fr) 1989-04-27 1990-04-11 Mécanisme à coup hydraulique

Country Status (5)

Country Link
US (1) US5038668A (fr)
EP (1) EP0394765B1 (fr)
JP (1) JPH02303775A (fr)
AT (1) ATE84739T1 (fr)
DE (2) DE3913866A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0473968A2 (fr) * 1990-09-06 1992-03-11 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Appareil de forage tournant et frappant, actionné hydrauliquement, spécialement pour le forage d'ancrage
DE102015016149A1 (de) * 2015-12-12 2017-06-14 Ulrich Keller Hochfrequenzzylinder

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IT1270226B (it) * 1994-06-15 1997-04-29 Giordano S R L Off Dispositivo di distribuzione di olio in pressione e martello idraulico dotato di tale dispositivo
JPH08281571A (ja) * 1995-04-14 1996-10-29 Komatsu Ltd 振動発生装置
US6058632A (en) * 1997-11-07 2000-05-09 Hawkins; Peter Arthur Taylor Tool holder with percussion member
FI115759B (fi) * 2002-05-17 2005-07-15 Yrjoe Raunisto Iskuja synnyttävä laite
DE10237407B4 (de) * 2002-08-16 2009-12-10 Eurodrill Gmbh Hydraulischer Schlaghammer mit Leerschlagabschaltung
SE528033C2 (sv) * 2004-03-12 2006-08-15 Atlas Copco Constr Tools Ab Hydraulslagverk
DE102004042369A1 (de) * 2004-09-01 2006-07-13 Eurodrill Gmbh Bodenbearbeitungsgerät und Verfahren zum Einbringen eines Arbeitselementes in den Boden
SE528743C2 (sv) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Slagverk för bergborrmaskin, förfarande för åstadkommande av en fram- och återgående slagkolvrörelse och bergborrmaskin
FI124781B (fi) * 2009-03-26 2015-01-30 Sandvik Mining & Constr Oy Iskulaite
EP3508308B1 (fr) * 2016-08-31 2022-08-17 Furukawa Rock Drill Co., Ltd. Dispositif de percussion hydraulique

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FR2175781A1 (fr) * 1972-03-10 1973-10-26 Atlas Copco Ab
FR2291374A1 (fr) * 1974-11-14 1976-06-11 Af Hydraulics Perfectionnements apportes a des dispositifs a commande hydraulique
DE2941443A1 (de) * 1979-10-12 1981-04-23 Institut Gidrodinamiki Sibirskogo Otdelenia Akademii Nauk Sssr Schlagvorrichtung

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DE3443542A1 (de) * 1984-11-29 1986-06-05 Fried. Krupp Gmbh, 4300 Essen Hydraulische schlagvorrichtung
EP0236721A3 (fr) * 1986-03-11 1989-10-25 NITTETSU JITSUGYO CO., Ltd. Concasseur hydraulique
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Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2175781A1 (fr) * 1972-03-10 1973-10-26 Atlas Copco Ab
FR2291374A1 (fr) * 1974-11-14 1976-06-11 Af Hydraulics Perfectionnements apportes a des dispositifs a commande hydraulique
DE2941443A1 (de) * 1979-10-12 1981-04-23 Institut Gidrodinamiki Sibirskogo Otdelenia Akademii Nauk Sssr Schlagvorrichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0473968A2 (fr) * 1990-09-06 1992-03-11 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Appareil de forage tournant et frappant, actionné hydrauliquement, spécialement pour le forage d'ancrage
EP0473968A3 (en) * 1990-09-06 1992-05-27 Krupp Maschinentechnik Gesellschaft Mit Beschraenkter Haftung Hydraulic operated impact drilling device, especially for bolt drilling
DE102015016149A1 (de) * 2015-12-12 2017-06-14 Ulrich Keller Hochfrequenzzylinder

Also Published As

Publication number Publication date
DE3913866A1 (de) 1990-10-31
US5038668A (en) 1991-08-13
DE59000777D1 (de) 1993-03-04
EP0394765B1 (fr) 1993-01-20
JPH02303775A (ja) 1990-12-17
ATE84739T1 (de) 1993-02-15

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