EP0933169A2 - Dispositif de percussion actionné par un fluide - Google Patents

Dispositif de percussion actionné par un fluide Download PDF

Info

Publication number: EP0933169A2
Authority: EP; European Patent Office
Prior art keywords: liner; piston; pressure; working; outer housing
Prior art date: 1998-02-03
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

EP99101293A

Other languages

German (de)

English (en)

Other versions

EP0933169A3 (fr

EP0933169B1 (fr

Inventor

Heinz-Jürgen Dr.-Ing. Prokop

Martin Schareina

Marcus Geimer

Thomas Deimel

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

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.)

1998-02-03

Filing date

1999-01-25

Publication date

1999-08-04

1999-01-25 Application filed by Krupp Berco Bautechnik GmbH filed Critical Krupp Berco Bautechnik GmbH

1999-08-04 Publication of EP0933169A2 publication Critical patent/EP0933169A2/fr

2000-11-15 Publication of EP0933169A3 publication Critical patent/EP0933169A3/fr

2002-06-12 Application granted granted Critical

2002-06-12 Publication of EP0933169B1 publication Critical patent/EP0933169B1/fr

2019-01-25 Anticipated expiration legal-status Critical

Status 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
- B25D9/16—Valve arrangements therefor
- B25D9/20—Valve arrangements therefor involving a tubular-type slide valve
- 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
- B25D2209/005—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 coaxial with the piston
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/371—Use of springs
- B25D2250/375—Fluid springs

Definitions

the invention relates to a fluid-powered hammer mechanism with one in one Working cylinder movable and hitting a tool Percussion piston as well as a control unit with a housing Movable spool, the percussion piston being two different has large piston surfaces, between which a circumferential groove arranged and of which the smaller, effective towards the return stroke Piston surface constantly with a pressure line under working pressure and the larger piston area effective in the direction of the working stroke the control alternately with the pressure line and a drain line connected is.
the control slide points in opposite to each other Direction effective slide surfaces, which are designed and are pressurized that the spool with the approach of the Percussion piston during the return stroke to top dead center through its then connected to the pressure line, in the direction of the working stroke position effective control surface switches to the working stroke position, in which also the working pressure is applied to the larger piston surface, and with the Approach of the percussion piston during the working stroke to the Impact point through its then with an unpressurized return line connected control surface is transferred to the return stroke position, in which the application of the larger piston area with the working pressure interrupted and a connection to the drain line is established.
composition of the working cylinder which appears to be possible from the point of view of saving costs, of a plurality of longitudinal sections connected to one another in the longitudinal direction of the percussion piston leads at least to problems in the sealing of the working cylinder from the environment and in the guidance of the percussion piston, and thus also to an increased susceptibility to faults.
the invention has for its object a generic percussion to develop in such a way that the disadvantages mentioned above at least partially avoided.
the percussion improved in terms of the costs associated with its manufacture become.
any existing ones in particular longer channels for the supply of the pressurized fluid or for its return from the area of the percussion piston be designed so that they can be manufactured in a simple manner.
the object is achieved by a fluid-operated hammer mechanism with the features of claim 1.
the basic idea of the invention is to design the working cylinder - in which the percussion piston is movable in the longitudinal direction - as a separate component in the form of a liner, which in turn is arranged in an outer housing and together with this at least one in the longitudinal direction of the two mentioned Parts extending pressure medium channel forms.
the liner should be formed in one piece at least over such a longitudinal extent that the front guide section facing the tool for the percussion piston and at least approximately further guide sections adjoining this in the return stroke direction are part of the liner including the guide section for the larger piston area.
the liner can also be made longer, ie it can extend beyond the front guide section and / or the guide section for the larger piston area.
the liner with the outer housing merely forms at least one pressure medium channel for the return piston stroke, the length of each pressure medium channel concerned with the working stroke is dimensioned such that it is connected to a return stroke chamber - which takes up the smaller piston area - via a front connecting channel extending from it. extends over a rear connecting channel extending therefrom, which is temporarily connected to a working stroke chamber accommodating the larger piston area.
any pressure medium channel for the percussion piston return stroke can be produced in a simple manner, in particular by machining only the outer surface of the liner facing the outer housing, before it is introduced into the outer housing.
the outer surface of the liner can be provided in the region of the pressure medium channel to be formed with a longitudinal groove or a flat in the longitudinal direction; instead or in addition, the inner wall of the outer housing in the region of the pressure medium channel to be formed can have a longitudinal groove or other depression which forms the same.
the former is resiliently biased in the axial direction against a stop element arranged on the outer housing (claim 2).
a stop element arranged on the outer housing (claim 2).
the pretension can be generated mechanically (claim 3).
this can be done by means of at least one spring element - for example in the form of a plate spring.
a hydraulic preload can also be provided within the scope of the invention (claim 4). This is preferably designed such that the liner is hydraulically supported against the working stroke direction of the percussion piston (claim 5).
the support field is expediently subjected to the working pressure with the interposition of a throttle point (claim 6).
the subject matter of the invention can be further developed in that the hydraulic support field - as seen in the working direction of the percussion piston - is arranged behind the return stroke chamber (claim 7).
a plurality of pressure medium channels can optionally also be provided (claim 8).
the manufacture, assembly and maintenance of the striking mechanism can be further simplified by the fact that the bushing is also hydraulically supported within the outer housing transversely to the longitudinal axis of the striking piston.
This can be done in particular in that the liner is held in contact with a circumferential part of the inner surface of the outer housing by means of a radially asymmetrical pressure field on the opposite side of the resultant force (claim 9).
the asymmetrical pressure field can be generated in the context of the invention in that between the liner and the outer housing, on the one hand, there is at least one pressure area subjected to the working pressure and, on the other hand, at least one relief point separate therefrom. Due to the interaction between the existing pressure areas and relief points, the resultant force results, with the result that the liner rests there on the inner surface of the outer housing (claim 10).
the relief point can each consist of a bore which opens into the interior of the outer housing and is at least temporarily relieved of pressure.
the liner in the region of the supporting peripheral part advantageously has at least one in the direction of this open channel, which forms a pressure-free return line (claim 11).
the embodiment in question (according to at least one of claims 9 to 11) has the consequence that the channel required for generating the asymmetrical pressure field can be open and consequently can be produced as a flattening of the depression in the outer surface of the liner without any particular effort lets, since the channel in question is sealed under the influence of the asymmetrical pressure field at the same time.
the spool can with respect to the percussion piston within the Invention can be arranged in any way, so - as at the beginning described - lie laterally offset to the percussion piston.
Control spool as a sleeve arranged parallel to the percussion piston trained and at least on part of its longitudinal extent is arranged within the liner (claim 12).
the striking mechanism also assigns to the descriptive channels as well as drive and control elements Working cylinder in the form of a liner 2 on which one Percussion piston 3 over successive in the longitudinal direction Guide sections 2a and 2b reciprocable in the transverse direction supports and - if necessary with little play in the radial direction - is arranged within an outer housing 4.
the outer housing 4 is closed by means of a hollow cover 5, into the cavity 5a of which the rear end section 3a of the percussion piston projects.
the movement of the percussion piston 3 in the direction of the working stroke is indicated by an arrow 6.
the striking mechanism 1 has, in a manner known per se, a tool holder, for example for a chisel, which is not shown.
the longitudinal axis of the liner 2 - which coincides with that of the percussion piston 3 - is designated by 7.
the liner 2 is held in the axial direction on the outer housing mechanically in that it is supported on the one hand by a plurality of prestressed disc springs 8 on the inner end face 5b of the hollow cover and on the other hand on an inner shoulder 4a of the outer housing opposite the end face 5b.
the hollow cover thus simultaneously forms a stop element which interacts with and is arranged on the outer housing.
this can also be designed differently, for example as a shoulder or support ring arranged on the outer housing.
the former is equipped with a sealing element 9.
the liner 2 has - seen in the working stroke direction (arrow 6) - behind the shoulder 4a a projection 2c, in which a sealing element 10 is also held for sealing next to the percussion piston.
the percussion piston 3 has two lying in the cylinder space of the liner 2 Piston collars 3b and 3c, which by a circumferential groove 3d in the axial Direction are separated from each other.
the outward facing Piston area A1 and A2 of the piston collar 3b and 3c together limit with the end face 5b, one held on this and the liner Intermediate ring 11 and with the liner itself a rear Cylinder chamber section 2d or with the liner alone a front Cylinder space section 2e; the piston area A2 is smaller than the piston area A1.
the smaller piston area A2 is constantly subjected to the working pressure (system pressure) via a pressure medium channel 12; this is generated by an energy source in the form of a hydraulic pump (not shown) and is fed (among other things) into the pressure medium channel 12 via a transverse bore 13 connected to it in the outer housing 4; this in turn is connected to the front cylinder space section 2e via a transverse bore 14 in the liner.
the percussion piston tends to perform a return stroke against the working stroke direction (arrow 6).
the opening 14a of the transverse bore 14 is arranged with respect to the percussion piston and the liner in such a way that it lies in any case outside the piston collar 3c and thus within the front cylinder space section 2e.
the control for switching over the movement of the percussion piston 3 into the bushing 2 including the bushing-like intermediate ring 11 is integrated, ie it is located in the region of the rear cylinder section 2d .
the control has a control slide 15 which is movable with respect to parts 2 and 11. This is sleeve-like and is arranged such that - lying coaxially to the percussion piston 3 - it surrounds it at a distance in the region of the rear cylinder space section 2d. Accordingly, the internal cavity of the control slide 15 simultaneously forms part of the rear cylinder section.
the control slide 15 has two differently sized end faces - namely a smaller, front end face S1 and a rear, larger one End face S2. Limit the two end faces S1 and S2 the axial range of motion of the spool in the direction of Working strokes (arrow 6) or in the direction of the return stroke. Accordingly the control spool can assume two end positions - namely that in the Drawing indicated return stroke position, in which the Control spool over the smaller end face S1 on a stop surface 2f the liner supports, and a working stroke position in which the larger end face S2 axially abuts the intermediate ring 11.
the junction 16a is located near the stop surface 2f arranged in the bushing transverse bore 16, which in turn with the Pressure medium channel 12 is connected and via this with the Working pressure is applied.
the pressure medium channel itself is on the one hand from the correspondingly designed outer surface 2g and on the other hand, from the opposite inner surface 4b of the Outer housing 4 formed.
control slide 15 has one Cross bore 15a through which, if necessary - i.e. dependent on from the position of the spool - a connection between the rear cylinder space section 2d and a drain line in the form of a Cross bore 17 can be made in the outer housing.
the liner 2 near the intermediate ring 11 also with a transverse bore 18 opening into the transverse bore 17, which in turn is also connected to a longitudinal bore 19; latter extends in the opposite direction of the working stroke (arrow 6) to the area in which the liner 2 is supported on the plate springs 8.
the transverse bore 13 merges into an annular groove 20 machined into the outer housing, which surrounds the liner 2 and opens into the pressure medium channel 12 in question.
its length is greater than the distance between the transverse bores 14 and 16 or between their openings 14a and 16a.
the one-piece bush 2 has such a longitudinal extent that it also includes the guide sections 2a and 2b and extends beyond them on both sides.
the control slide 15 is - seen in the axial direction - in the area between the two end faces S1 and S2 continue with one in the direction its working stroke effective control surface SF equipped - in Cross section seen - as a radially projecting shoulder is formed and which is opposite a smaller counter surface GF.
the latter is via the transverse bore 18 arranged in the liner 2 relieved of pressure.
the longitudinal bore 19 connected to the transverse bore 18 passes - seen in the working stroke direction (arrow 6) - outside the area of the control slide 15 and the annular groove 20 into a return line 21, which is formed in the area of the liner as a groove-shaped depression worked into the outer surface thereof .
This return line extends in the working stroke direction into the region of a relief bore 22 connected to it, the latter opening into the interior of the liner 2 and its opening 22a being spaced between the front cylinder space section 2e (namely the return stroke chamber) and the projection 2c.
the liner 2 is equipped with a sealing element 23 in the region between the relief bore 22 and the support surface 4a and with a sealing element 24 in the region of the projection 2c.
the relief bore 22 protects the sealing element 10 from stress caused by the working pressure prevailing in the front cylinder space section 2e.
a sealing element 25 held in the outer housing 4 is arranged between the transverse bore 17 merging into an annular groove 17a and the annular groove 20.
the return line 21 is also connected to a through hole 26, which in the drawn position of the percussion piston 3 opens into the interior of the liner 2 in the region of the circumferential groove 3d.
the control surface SF of the control slide can be acted upon or relieved of the working pressure via a control line 27 - which is connected to the interior of the liner 2 via a through hole 28 in the area between the holes 26 and 22a.
a control line 27 - which is connected to the interior of the liner 2 via a through hole 28 in the area between the holes 26 and 22a.
the internal opening 28a of the through bore 28 is closed by the piston collar 3c.
the control line 27 merges into an annular groove-shaped extension 27a, which is delimited laterally by the control surface SF.
control slide 15 assumes the return stroke position in which the end face S1 bears against the stop face 2f; Accordingly, the rear cylinder space section 2d (namely the working lifting chamber) is partially relieved of pressure via the bores 15a and 18, the transverse bore 15a serving as an outflow resistance. Under the influence of the remaining pressure, the control slide 15 is held in the return stroke position shown via its larger end surface S2. At this point in time, the control line 27 is relieved of pressure after the pressure has been relieved by the interaction of the through bores 28 and 26, which had temporarily been connected to one another via the circumferential groove 3d.
the intermediate ring 11 - which defines the range of motion of the control slide 15 in the direction of the working stroke position - also serves to guide the control slide.
the percussion mechanism has an inner liner which, with the associated channels, bores and the like.
Manufactured separately and therefore - with due regard to different requirements that have to be placed on an outer housing or an internal component - can consist of a different material than the outer housing.
the material for the liner can be selected taking into account the sliding properties, which are irrelevant for the outer housing.
the costs for the manufacture of the striking mechanism can be reduced in that, in particular, longer ducts - such as ducts 12 and 21 - can be produced by simply machining the outer surface of the liner, ie by providing corresponding depressions, grooves, flats or the like, in which Installed state, the inner surface of the outer housing represents part of the wall of the relevant channels.
the separate manufacture of the liner also facilitates the production of certain transverse bores (such as, for example, the transverse bore 14), provided that these are only part of the liner and do not need to be closed to the outside.
the resilience of the striking mechanism can also be reduced by the resilient support of the liner within the outer housing.
the liner 2 is hydraulically prestressed in the axial direction against the outer housing 4, specifically against the working stroke direction (arrow 6) of the percussion piston 3.
the liner 2 is supported against the working stroke direction directly on the end face 5b of the hollow cover 5.
the outer housing 4 delimits a support chamber 29 via its shoulder 4a with the liner above the projection 2c. This is connected to the pressure medium channel 12 via a longitudinal bore 30 and a throttle bore 31 acting as a throttle point. Under the influence of the working pressure, a hydraulic support field is formed in the support chamber 29, which fixes the liner 2 with respect to the outer housing 4 in the manner already described.
the throttle bore 31 serves to stabilize the hydraulic support field in the support chamber 29 in the event of impact loads, namely in that the fluid contained in the support chamber 29 can only escape from it against the outflow resistance of the throttle bore 31.
the bores 30 and 31 are also easily accessible on the liner 2 and can therefore be produced in a simple manner.
the liner 2 can also be held in contact with a peripheral part 4c of the inner surface 4b of the outer housing 4 by means of a radially asymmetrical pressure field on the side opposite the resultant force (indicated by an arrow 32 pointing upwards). Under the action of the asymmetrical pressure field, a gap s is present between the liner 2 and the outer housing 4 on the side opposite the peripheral part 4c.
the liner 2 is provided with three flats 2h which are offset with respect to one another on their circumference and which together with the inner surface 4b form three pressure medium channels 12; a transverse bore 14 extends from these, which - as already explained with reference to FIG. 1 - opens into the front cylinder space section 2e.
the return line 21 mentioned above is also arranged in the region of the supporting peripheral part 4c. It is formed by this in cooperation with a longitudinal groove machined into the liner 2.
the illustration in question additionally shows the position of the through bore 26, the control line 27 and the through bore 28 connected to it for ease of understanding.
the latter is arranged in such a way that its outward opening 28b also lies in the region of the supporting peripheral part 4c. Accordingly, it can be disregarded to close the through bore 28, which is also temporarily subjected to the working pressure, in the direction of the outer housing 4, which simplifies the manufacture of the said through bore.

Landscapes

Physics & Mathematics (AREA)
Fluid Mechanics (AREA)
Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
Percussive Tools And Related Accessories (AREA)
Earth Drilling (AREA)
Portable Nailing Machines And Staplers (AREA)
Drilling And Exploitation, And Mining Machines And Methods (AREA)

EP99101293A 1998-02-03 1999-01-25 Dispositif de percussion actionné par un fluide Expired - Lifetime EP0933169B1 (fr)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
DE19804078A DE19804078A1 (de)	1998-02-03	1998-02-03	Fluidbetriebenes Schlagwerk
DE19804078		1998-02-03

Publications (3)

Publication Number	Publication Date
EP0933169A2 true EP0933169A2 (fr)	1999-08-04
EP0933169A3 EP0933169A3 (fr)	2000-11-15
EP0933169B1 EP0933169B1 (fr)	2002-06-12

Family

ID=7856429

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP99101293A Expired - Lifetime EP0933169B1 (fr)	1998-02-03	1999-01-25	Dispositif de percussion actionné par un fluide

Country Status (4)

Country	Link
EP (1)	EP0933169B1 (fr)
AT (1)	ATE218946T1 (fr)
DE (2)	DE19804078A1 (fr)
ES (1)	ES2177145T3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP1256419A1 (fr) *	2001-05-12	2002-11-13	Krupp Berco Bautechnik GmbH	Méthode et pour la protection d'un outil de percussion hydraulique contre les effects des frappes à vide
CN102275152A (zh) *	2010-06-10	2011-12-14	喜利得股份公司	工具机
EP2873489A1 (fr) *	2013-11-13	2015-05-20	Sandvik Mining and Construction Oy	Dispositif d'impact et son procédé de démontage
US9151386B2 (en)	2013-03-15	2015-10-06	Caterpillar Inc.	Accumulator membrane for a hydraulic hammer
US9555531B2 (en)	2013-03-15	2017-01-31	Caterpillar Inc.	Hydraulic hammer having co-axial accumulator and piston
US9592598B2 (en)	2013-03-15	2017-03-14	Caterpillar Inc.	Hydraulic hammer having impact system subassembly

Citations (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE2645213A1 (de) *	1975-12-05	1977-06-08	Gardner Denver Co	Schlagwerkzeug
US4181183A (en) *	1978-01-05	1980-01-01	Nippon Pneumatic Manufacturing Co., Ltd.	Impact tool
DE3412187A1 (de) *	1984-04-02	1985-10-10	Ri&zcaron;skij politechni&ccaron;eskij institut imeni A. Ja. Pel&scaron;e, Riga	Drucklufthammer
EP0183093A1 (fr) *	1984-11-29	1986-06-04	Fried. Krupp Gesellschaft mit beschränkter Haftung	Dispositif hydraulique de percussion
EP0658681A2 (fr) *	1993-12-15	1995-06-21	Walter, Hans-Philipp	Marteau à forage

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
FI60151C (fi) *	1979-06-26	1981-12-10	Tampella Oy Ab	Hydraulisk slaganordning
DE3400302A1 (de) *	1984-01-03	1985-08-29	Mannesmann AG, 4000 Düsseldorf	Hydraulisch betaetigte schlagvorrichtung

1998
- 1998-02-03 DE DE19804078A patent/DE19804078A1/de not_active Withdrawn
1999
- 1999-01-25 EP EP99101293A patent/EP0933169B1/fr not_active Expired - Lifetime
- 1999-01-25 AT AT99101293T patent/ATE218946T1/de not_active IP Right Cessation
- 1999-01-25 ES ES99101293T patent/ES2177145T3/es not_active Expired - Lifetime
- 1999-01-25 DE DE59901686T patent/DE59901686D1/de not_active Expired - Lifetime

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE2645213A1 (de) *	1975-12-05	1977-06-08	Gardner Denver Co	Schlagwerkzeug
US4181183A (en) *	1978-01-05	1980-01-01	Nippon Pneumatic Manufacturing Co., Ltd.	Impact tool
DE3412187A1 (de) *	1984-04-02	1985-10-10	Ri&zcaron;skij politechni&ccaron;eskij institut imeni A. Ja. Pel&scaron;e, Riga	Drucklufthammer
EP0183093A1 (fr) *	1984-11-29	1986-06-04	Fried. Krupp Gesellschaft mit beschränkter Haftung	Dispositif hydraulique de percussion
EP0658681A2 (fr) *	1993-12-15	1995-06-21	Walter, Hans-Philipp	Marteau à forage

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP1256419A1 (fr) *	2001-05-12	2002-11-13	Krupp Berco Bautechnik GmbH	Méthode et pour la protection d'un outil de percussion hydraulique contre les effects des frappes à vide
CN102275152A (zh) *	2010-06-10	2011-12-14	喜利得股份公司	工具机
EP2394795A1 (fr) *	2010-06-10	2011-12-14	HILTI Aktiengesellschaft	Machine-outil
US8939229B2 (en)	2010-06-10	2015-01-27	Hilti Aktiengesellschaft	Power tool
CN102275152B (zh) *	2010-06-10	2016-08-03	喜利得股份公司	工具机
US9151386B2 (en)	2013-03-15	2015-10-06	Caterpillar Inc.	Accumulator membrane for a hydraulic hammer
US9555531B2 (en)	2013-03-15	2017-01-31	Caterpillar Inc.	Hydraulic hammer having co-axial accumulator and piston
US9592598B2 (en)	2013-03-15	2017-03-14	Caterpillar Inc.	Hydraulic hammer having impact system subassembly
US9822802B2 (en)	2013-03-15	2017-11-21	Caterpillar Inc.	Accumulator membrane for a hydraulic hammer
US10562166B2 (en)	2013-03-15	2020-02-18	Caterpillar Inc.	Hydraulic hammer having co-axial accumulator and piston
EP2873489A1 (fr) *	2013-11-13	2015-05-20	Sandvik Mining and Construction Oy	Dispositif d'impact et son procédé de démontage

Also Published As

Publication number	Publication date
ATE218946T1 (de)	2002-06-15
EP0933169A3 (fr)	2000-11-15
DE59901686D1 (de)	2002-07-18
EP0933169B1 (fr)	2002-06-12
ES2177145T3 (es)	2002-12-01
DE19804078A1 (de)	1999-08-05

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