EP1694471B1 - Marteau perforateur et/ou marteau percuteur muni d'un raccord d'outil - Google Patents

Marteau perforateur et/ou marteau percuteur muni d'un raccord d'outil Download PDF

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Publication number
EP1694471B1
EP1694471B1 EP04820805A EP04820805A EP1694471B1 EP 1694471 B1 EP1694471 B1 EP 1694471B1 EP 04820805 A EP04820805 A EP 04820805A EP 04820805 A EP04820805 A EP 04820805A EP 1694471 B1 EP1694471 B1 EP 1694471B1
Authority
EP
European Patent Office
Prior art keywords
tool
striking
tool holder
piston
insert
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.)
Not-in-force
Application number
EP04820805A
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German (de)
English (en)
Other versions
EP1694471A1 (fr
Inventor
Rudolf Berger
Wolfgang Schmid
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.)
Wacker Construction Equipment AG
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Wacker Construction Equipment AG
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Publication date
Application filed by Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP1694471A1 publication Critical patent/EP1694471A1/fr
Application granted granted Critical
Publication of EP1694471B1 publication Critical patent/EP1694471B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0038—Locking members of special shape
    • B25D2217/0042—Ball-shaped locking members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T279/00—Chucks or sockets
    • Y10T279/17—Socket type
    • Y10T279/17042—Lost motion
    • Y10T279/17051—Swinging external yoke or detent
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T279/00—Chucks or sockets
    • Y10T279/17—Socket type
    • Y10T279/17042—Lost motion
    • Y10T279/17068—Rotary socket

Definitions

  • the invention relates according to the preamble of claim 1 or 3, a device for a drill and / or percussion hammer with a tool holder for holding a tool and transmitting a torque to the tool.
  • Such a device is z. B. offered under the brand name "SDS-max" and has proven itself in practice.
  • an impact-drilling tool has at least two open at the end of the tool shank rotational drive grooves, can engage in the web-shaped rotational driver of a tool holder of the hammer drill. Furthermore, two mutually closed, diametrically opposite recesses are provided in the tool shank, can engage in the provided on the tool holder locking body.
  • Fig. 1 shows a sectional view of the front, tool receiving side end of a known drilling and / or percussion hammer.
  • Fig. 1 In the upper half of Fig. 1, a known Heilfeder Farbwerk is shown in impact position, while the lower half of Fig. 1 shows the air spring impact mechanism in neutral position.
  • Part of the air spring impact is a hollow trained percussion piston 1, which can be brought by a drive piston, not shown, in reciprocating motion in a known manner.
  • the percussion piston 1 strikes a likewise axially movable anvil 2, which in turn transmits the impact action at its opposite end to the end face of a not shown insertion end of a tool (eg a drill or a chisel).
  • a tool eg a drill or a chisel
  • the insertion end of the tool is inserted via an insertion opening 3 in a tool holder 4 forming a substantially hollow cylindrical recess.
  • a fictitious defined impact opening 5 is provided, through which the impact effect of the striker 2 can be applied to the insertion end.
  • the tool holder 4 is part of a tool holder 6, the three formed on the inside of the tool holder 4, web-shaped rotary driver 7 has.
  • the rotary driver 7 are inserted into non-illustrated rotary driving grooves in the insertion of the tool, as z. B. in DE 37 16 915 A1 is described. Opposite the two rotary drivers 7 shown in FIG. 1, a further rotary driver is arranged.
  • To the tool holder 6 further includes two locking body 8, which are in openings 9 of the tool holder 4 axially and - under certain circumstances explained below - are radially movable.
  • the locking body 8 With the aid of a spring-loaded plate 10, the locking body 8 are axially fixed against a guide 11, so that they can not dodge radially outward. In this position, they are held in associated, not shown, locking recesses which are present in the insertion end of the tool.
  • the locking recesses in the tool are closed on both sides in the tool shaft in the axial direction, so that a tool insertion end can be prevented by the locking body 8 from being pulled out of the tool holder 4.
  • the operator can move a locking sleeve 12 together with the plate 10 against the action of a spring 13 (in Fig. 1 to the right), whereby the locking body 8 are moved in the openings 9 to the right.
  • a spring 13 in Fig. 1 to the right
  • the locking body 8 from the associated locking recesses so that the spigot is free to move in the axial direction and can be pulled out of the tool holder 4.
  • a hammer with a tool holder for holding a tool and transmitting a torque to the tool is known.
  • the tool holder has on its inside a locking body with which a tool end is held in the tool holder and the drive torque is transmitted to the tool end.
  • the invention has for its object to provide a device for a drill and / or percussion hammer with a tool holder for holding a tool and transmitting a torque to the tool, which - with unchanged design of the tool and its insertion - allows higher impact energies and Apply torques to the tool without the plug-in end is more stressed or even damaged.
  • the tool holder in a known manner on a tool holder, on the inside at least one rotary driver and at least one between a locking state and an unlocking state movable locking body are provided.
  • the tool holder is formed by a substantially hollow-cylindrical recess which has an insertion opening for a plug-in end of the preferably frameless tool on one end face and has an impact opening on an opposite end face, by means of which a striking effect can be applied to the insertion end.
  • an abutment surface acting in the axial direction of the tool holder is provided on an inner wall of the tool holder in the region of the impact opening.
  • the one rotary driver or preferably the two or more rotary drivers are designed web-shaped.
  • the rotary driver (s) on the inside of the tool holder extend axially as far as the stop surface.
  • the rotational drivers formed on the inside of the tool holder are assigned corresponding rotational engagement surfaces on the insertion end. If, as in the case of the SDS-max system, the rotary drivers are web-shaped, the rotational engagement surfaces can be designed in the form of rotary driving grooves in the insertion end.
  • the stop surface serves as a stop for the insertion of the tool.
  • the stop surface it is possible that the insertion opposite the tool holder in its axial end position, which generally also corresponds to the impact position, can be fixed on one side, without any repercussions on the impact system, in particular the air spring impact mechanism can be done.
  • Previously known solutions always required an intermediate header (see, for example, reference number 2 in FIG. 1), which not only had to transfer the impact energy to the insertion end but also served for the axial positioning of the insertion end.
  • the stop surface according to the invention is completely separated from the function of the impact transmission and serves to support the applied by the operator pressure forces and the relatively weak so-called B-blows (setbacks of the bit, especially on hard ground).
  • the stop surface is provided fixed relative to the tool holder on the inner wall of the hollow cylindrical recess.
  • the stop surface is formed on the end face of the recess, which also has the impact opening.
  • the stop surface is indeed also provided on the inner wall of the tool holder.
  • she can z. B. of an elastic material (eg., Plastic or rubber) and thus have a certain elasticity.
  • the stop surface z. B. be formed on a sleeve which is axially displaceable against the action of a spring device on the inner wall of the tool holder.
  • the stop surface is indeed provided on the inner wall of the tool holder, but strictly speaking not stationary. If the description of a "fixed" stop surface is mentioned below, the variants described here are also to be understood to include stop surfaces which are movable against an elastic action. The movable stop surfaces are at least at rest, without being affected by the insertion, to be considered stationary. Thus, all subsequent statements regarding fixed stop surfaces apply equally to movable stop surfaces.
  • the abutment surface is conical, so that a frustoconical insertion be formed at the front end of the tool-Einsteckendes can come to rest on her.
  • This conical surface is now assigned according to the invention, the conical stop surface in the tool holder, which ensures a large-scale and thus secure stop.
  • the rotary drivers have only a limited axial extent, the z. B. the length shown in Fig. 1 of the apertures 9 correspond to the locking body 8. This not only has the disadvantage that due to an increased surface pressure between the rotary drivers and the rotary driving surfaces (rotary driving grooves) z. B. increased wear on the side surfaces of the rotary driving grooves has been found in the spigot ends.
  • the inventive design of the tool holder also allows an optimization of the shape of the percussion piston.
  • the percussion piston has a shaft which can be guided in a percussion piston guide.
  • the percussion piston itself can z. B. solid, with a hollow design (hollow bat) is possible.
  • the impact piston guide connects directly to the tool holder, so that the stop surface is arranged according to the invention according to claim 3 at a transition from the impact piston guide to the tool holder.
  • the impact energy of the percussion piston can be transmitted via the shaft directly to the insertion, without an intermediate header must be provided, as is the case in the prior art.
  • the impact piston guide is formed as a hollow cylinder and has at least one, but preferably a plurality of tangentially encircling grooves on the inside.
  • the grooves can be filled in the operation of the percussion with lubricant, especially grease, on the one hand to ensure adequate lubrication of the impact piston guide and on the other hand a seal of the air spring impact against influences that can get from the outside via the tool holder in the drill and hammer ,
  • the tolerance of the outer diameter of the shaft of the percussion piston and the inner diameter of the impact piston guide is selected such that a gap is formed, can pass through the lubricant from the Beerfedertschwerk in the tool holder.
  • Beater solutions causes this type of impact piston guide by the very abrupt delay of the percussion piston during the impact of a wandering of the impact piston shaft adhering fat or dirt parts forward, in the direction of the tool holder. In this way, not only dirt from the area of the air spring impact mechanism is transported out.
  • the tool holder and the insertion of the tool are automatically lubricated, so that the previously customary separate lubrication is no longer required.
  • the gap i. H. the tolerance between the percussion piston shaft and the impact piston guide, be sized so that only relatively small amounts of grease can escape.
  • the diameter of the shaft of the percussion piston is smaller than the outer diameter of the insertion end, preferably even smaller than the inner diameter, so smallest Druchmesser, the frusto-conical insertion slope of the Amsterdamkekendes. This avoids that the spigot itself with its cone-shaped insertion in the event of setbacks on the fixed stop surface in the tool holder can strike a kind of "mushroom”, would be clamped by the worst case of the club shaft.
  • the diameter of the impact piston shaft is smaller than the diameter of a fictitious, usable in the interior of the tool holder between the rotary driver cylinder.
  • the impact piston shaft can also penetrate into the area of the rotary drivers without touching the rotary drivers or even against the rotary drivers.
  • the described embodiments can also be varied by maintaining an intermediate piston or striker as the impactor which transfers the impact energy of the percussion piston to the insertion end.
  • an intermediate piston or striker as the impactor which transfers the impact energy of the percussion piston to the insertion end.
  • the diameter restrictions last described for the stem of the percussion piston apply correspondingly to the impactor (Intermediate piston) or its shaft dimensions.
  • An intermediate piston can z. B. be advantageous in short-building percussion piston, so that the seal is better possible for percussion.
  • the device described is suitable not only for the mentioned SDS-max system, but also for other types of tool holders or tool insertion ends.
  • the tools themselves are often made without a ferrule terminating the insertion end, which brings cost advantages.
  • FIGS. 2 to 4 relate to the same embodiment of the device according to the invention and are described below in parallel, at least in part.
  • the device is part of a rotary hammer and / or percussion hammer, hereinafter referred to as a hammer, of which but here only a Lucasfedertschtechnik 20, a tool holder 21 and a part of a tool 22 are shown.
  • a hammer of which but here only a Lucasfedertschtechnik 20, a tool holder 21 and a part of a tool 22 are shown.
  • the other areas of the hammer are not shown because they do not affect the invention.
  • drive piston 23 is through a drive (motor with crank mechanism) axially reciprocated in a known manner.
  • a drive motor with crank mechanism
  • air spring of the percussion piston 24 is also axially reciprocated.
  • the percussion piston 24 has a piston plate 25 and a shaft 26 which is axially movably guided in an impact piston guide 27 held in the hammer.
  • the shaft 26 strikes an end face 28 of a tool 29 belonging to a male end 30, as z. B. in the upper part of Fig. 3 can be seen.
  • the percussion piston 24 and the percussion piston guide 27 are rotatable together with the tool holder 21, so that they can be driven in rotation by the drive of the hammer. The rotational movement is then transmitted to the tool 22 to achieve a drilling action.
  • the insertion end 30 is configured according to the well-known standard "SDS-max" and the z. B. also have in DE 37 16 915 A1 features described. These include at least two rotary driving grooves, not shown in the figures, which open at the end of belonging to the tool 29 Einsteckendes 30 open, and two diametrically opposed locking recesses 31. At the end face 28 of the insertion 30 a frustoconical insertion bevel 32 is provided.
  • the tool holder 21 has a substantially hollow cylindrical recess which forms a tool holder 33.
  • an insertion opening 34 is provided through which the insertion end 30 in the manner shown in Figs. 2 and 3 can be inserted.
  • a striking opening 35 is provided through which a percussion effect of the percussion piston 24 and the shaft 26 can be applied to the end face 28 of the insertion.
  • the impact opening 35 thus forms the transition between the impact piston guide 27 and the tool holder 33.
  • the impact opening 35 must not necessarily a physically precisely defined feature. Rather, it may also be a transition region in which the impact energy of the percussion piston 24 is transmitted to the insertion end 30.
  • the tool holder 21 furthermore has one or preferably a plurality of web-shaped rotary drivers 36 which extend axially on the inside of the tool holder 33. Of the rotational drivers 36 are shown in Fig. 2, two recognizable. The number of rotary drivers 36 is matched to the number of rotary driving grooves, not shown, so that the rotary driving grooves 36 are pushed onto the rotary driver.
  • two locking body 37 which engage respectively in their associated locking recess 31 in the insertion end 30, as shown in Figs. 2 and 3 can be seen.
  • a stationary stop surface 38 is provided, based on the tool holder 33.
  • the abutment surface acts at least partially in the axial direction of the tool holder 33 such that the insertion bevel 32 of the insertion end 30 can come to a stop against them, such. B. shown in the upper part of Fig. 3.
  • the shaft 26 of the percussion piston 24 can meet the end face 28 of the insertion end 30 optimally.
  • the end face 28 can be acted upon in other positions by the shaft 26.
  • a relative to the tool holder 33 axially against the action of a spring means movable abutment surface. So it is z.
  • the stop surface itself by an elastic material (eg rubber or plastic).
  • the stop surface may also be provided on a sleeve which is axially movable against the action of a spring device supported on the tool holder.
  • the web-shaped rotational drivers 36 are brought up to the impact opening 35 or abutment surface 38. In this way, torque is always transmitted to the insertion end 30 by the rotational drivers 36 and the rotary driving grooves over a maximum possible length.
  • the depth of the rotary driving grooves is preferably dimensioned such that the rotational engagement grooves in the region of the insertion bevel 32 run out without piercing the end face 28. As a result, it can be ensured that even with an at least slight mushrooming of the front side 28 by the impact action of the percussion piston 24, the rotary driving grooves are not deformed, so that the tool 22 can be removed from the tool holder 21 at any time.
  • FIG 3 shows the percussion piston 24 and the insertion end 30 in different positions, the normal impact position being shown in the upper part of the image, in which the percussion piston 24 acts on the end face 28 of the insertion end 30 for impact transmission, while the idle position is shown in the lower part of the image, in which the insertion end 30 slips out of the housing of the hammer and is prevented only by the locking body 37 at the complete sliding out of the housing.
  • the percussion piston 24 has followed the insertion end 30 in the neutral position and is in its foremost position.
  • FIG. 4 shows an enlarged detail of the area around the stop surface 38 of FIG. 3.
  • the insertion end 30 abuts with its insertion bevel 32 against the abutment surface 38.
  • the diameter of the impact piston guide 27 is again slightly smaller than the inner diameter of the stop surface 38. This creates a free area 39, in the material of the insertion end 30th can escape if the end face 28 and the inner diameter of the insertion bevel 32 extending edge due to the impact of the shaft 26 should mush something up.
  • a striking face 40 of the percussion piston 24 has a weak curvature which can be seen in FIG. 4, so that the first contact between the striking face 40 and the end face 28 takes place approximately in the region of the central axis. In this way, a significant portion of the impact energy is applied centrally to the male end 30. At the same time unwanted deformations in the edge region, ie at the insertion bevel 32 are avoided.
  • the diameter of the shaft 26 of the percussion piston 24 may be slightly smaller than the inner diameter of the insertion bevel 32 of the insertion end 30th
  • the special design of the tool holder 33 makes it possible that the insertion end 30 is guided radially over its entire, inserted into the tool holder 33 insertion length. As a result, the wear of the insertion end 30 can be significantly reduced. Because the web-shaped rotational driver 36 only expire in the area of the stop surface 38, it is not necessary to provide diameter enlargements of the tool holder 33 in front of and behind the rotational drivers, in which, for example, B. start a broach and could leak. Such a requirement exists in the shorter rotary drivers of the prior art, where the guidance of the insertion end is possible only in the area of the rotary driver. Due to the fact that according to the invention the rotary drivers have a substantially greater axial extent, the radial guidance of the male end 30 can also be effected over a relatively long range.
  • the invention enables the use of already known tools with insertion ends according to the "SDS-max" standard even for devices with significantly higher performance. If the previously used "SDS-max” standard were retained on such a tool-receiving side, the insertion ends of the tools would be destroyed after a very short time. Of course, the invention can also be used advantageously in other insertion systems than the "SDS-max" standard.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

L'invention concerne un dispositif prévu pour un marteau perforateur et/ou un marteau percuteur, qui présente un raccord d'outil (21) pour maintenir un outil (22) et transmettre un couple à l'outil (22). Un des éléments constitutifs du raccord d'outil (21) est un porte-outil (33) cylindrique creux, présentant une ouverture d'insertion (34) pour insérer l'extrémité emboîtable (30) de l'outil, ainsi qu'une ouverture de martelage (35) par le biais de laquelle un effet de martelage peut être appliqué à l'extrémité emboîtable (30). Dans la zone de l'ouverture de martelage (35) du porte-outil (33), il est prévu une surface de butée (38), fixe par rapport au porte-outil (33) et agissant dans le sens axial dudit porte-outil (33). Le raccord d'outil (33) convient particulièrement aux extrémités emboîtables (30) selon la norme « SDS-max ».

Claims (15)

  1. Dispositif pour un marteau perforateur et/ou d'un marteau percuteur muni d'un raccord d'outil (21) pour le maintien d'un outil (22) et la transmission d'un couple de rotation à l'outil (22), ledit raccord d'outil (21) comprenant :
    - un évidement sensiblement cylindrique formant un attachement d'outil (33) comportant une ouverture d'introduction (34) sur un côté frontal, par laquelle une extrémité d'engagement (30) de l'outil (22) est insérable, et une ouverture de percussion (35) sur un côté frontal opposé, par laquelle un effet de percussion est applicable sur l'extrémité d'engagement (30),
    - au moins un entraîneur en rotation (36) en forme de baguette formé sur une face intérieure de l'attachement d'outil (33),
    - en outre au moins un corps de verrouillage (37) maintenu en état de blocage dans une position radiale définie, et déplaçable en état de déblocage au moins radialement à partir de la position radiale définie,
    caractérisé en ce qu'
    - une surface de butée (38) agissant dans le sens axial de l'attachement d'outil (33) est prévue sur une paroi intérieure de l'attachement d'outil (33) au niveau de l'ouverture de percussion (35), et en ce que
    - l'entraîneur en rotation (36) s'étend axialement sur la face intérieure de l'attachement d'outil (33) jusqu'à la surface de butée (38).
  2. Dispositif selon la revendication 1, caractérisé en ce qu'
    - un mécanisme de percussion à ressort pneumatique (20) est prévu dans le marteau perforateur et/ou le marteau percuteur, avec un piston d'entraînement déplaçable en va-et-vient par un entraînement et un piston de percussion (24) entraînable par le piston d'entraînement,
    - le piston de percussion (24) comprend une tige (26) guidable dans une glissière à piston de percussion (27), et en ce que
    - la surface de butée (38) est disposée à la transition de la glissière à piston de percussion (27) à l'attachement d'outil (33).
  3. Dispositif pour un marteau perforateur et/ou d'un marteau percuteur muni d'un raccord d'outil (21) pour le maintien d'un outil (22) et la transmission d'un couple de rotation à l'outil (22), où
    - un mécanisme de percussion à ressort pneumatique (20) est prévu dans le marteau perforateur et/ ou le marteau percuteur, avec un piston d'entraînement déplaçable en va-et-vient par un entraînement et un piston de percussion (24) entraînable par le piston d'entraînement,
    - le piston de percussion (24) comprend une tige (26) guidable dans une glissière à piston de percussion (27),
    et où le raccord d'outil (21) comprend :
    - un évidement sensiblement cylindrique formant un attachement d'outil (33) comportant une ouverture d'introduction (34) sur un côté frontal, par laquelle une extrémité d'engagement (30) de l'outil (22) est insérable, et une ouverture de percussion (35) sur un côté frontal opposé, par laquelle un effet de percussion est applicable sur l'extrémité d'engagement (30),
    - au moins un entraîneur en rotation (36) en forme de baguette formé sur une face intérieure de l'attachement d'outil (33),
    - en outre au moins un corps de verrouillage (37) maintenu en état de blocage dans une position radiale définie, et déplaçable vers un état de déblocage au moins radialement à partir de la position radiale définie,
    caractérisé en ce qu'
    - une surface de butée (38) agissant dans le sens axial de l'attachement d'outil (33) est prévue sur une paroi intérieure de l'attachement d'outil (33) au niveau de l'ouverture de percussion (35), et en ce que
    - la surface de butée (38) est disposée à la transition de la glissière à piston de percussion (27) à l'attachement d'outil (33).
  4. Dispositif selon la revendication 3, caractérisé en ce que l'entraîneur en rotation (36) s'étend axialement sur la face intérieure de l'attachement d'outil (33) jusqu'à la surface de butée (38).
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que la surface de butée (38) est de forme conique.
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que
    - l'outil (22) comprend :
    + l'extrémité d'engagement (30), sensiblement cylindrique et réalisée par une queue d'outil,
    + au moins une surface d'entraînement en rotation prévue sur l'extrémité d'engagement (30), aboutissant ouverte à l'extrémité de la queue d'outil, et
    + au moins un évidement de verrouillage (31) prévu dans l'extrémité d'engagement (30), clos des deux côtés dans le sens axial de la queue d'outil ;
    - en ce que l'entraîneur en rotation (36) est associé à la surface d'entraînement en rotation correspondante et réalisé de telle manière que la surface d'entraînement en rotation est coulissante à l'insertion de l'outil (22) sur l'entraîneur en rotation (36),
    - en ce que le ou les évidements de verrouillage (31) sont associés à au moins un corps de verrouillage (37) maintenu dans l'évidement de verrouillage (31) en état de blocage, et déplaçable en état de déblocage au moins radialement à partir de l'évidement de verrouillage (31), et
    - en ce que la surface de butée (38) sert de surface de butée pour l'extrémité d'engagement (30).
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce qu'un biseau d'introduction (32) tronconique est prévu sur l'extrémité frontale (28) de l'extrémité d'engagement (30).
  8. Dispositif selon l'une des revendications 1 à 7, caractérisé en ce que l'extrémité d'engagement (30) est radialement glissée sur toute sa longueur d'engagement introduite dans l'attachement d'outil (33).
  9. Dispositif selon l'une des revendications 2 à 8, caractérisé en ce que l'énergie de percussion du piston de percussion (24) est directement transmissible à l'extrémité d'engagement (30) par la tige (26) du piston.
  10. Dispositif selon l'une des revendications 2 à 9, caractérisé en ce que la glissière à piston de percussion (27) est réalisée comme cylindre creux et comprend au moins une rainure périphérique tangentielle sur sa face intérieure.
  11. Dispositif selon l'une des revendications 2 à 10, caractérisé en ce que la tolérance du diamètre extérieur de la tige (26) du piston de percussion (24) et du diamètre intérieur de la glissière à piston de percussion (27) est choisie de manière à former une fente par laquelle un lubrifiant peut parvenir dans l'attachement d'outil (33) depuis une zone du mécanisme de percussion à ressort pneumatique (20).
  12. Dispositif selon l'une des revendications 2 à 11, caractérisé en ce que le diamètre de la tige (26) du piston de percussion (24) ou d'un corps de percussion transmettant l'énergie de percussion du piston de percussion (24) à l'extrémité d'engagement (30), est inférieur au diamètre extérieur de l'extrémité d'engagement (30).
  13. Dispositif selon l'une des revendications 2 à 12, caractérisé en ce que le diamètre de la tige (26) du piston de percussion (24) ou d'un corps de percussion transmettant l'énergie de percussion du piston de percussion (24) à l'extrémité d'engagement (30), est inférieur au diamètre intérieur du biseau d'introduction (32) tronconique de l'extrémité d'engagement (30).
  14. Dispositif selon l'une des revendications 2 à 13, caractérisé en ce que le diamètre de la tige (26) du piston de percussion (24) ou d'un corps de percussion transmettant l'énergie de percussion du piston de percussion (24) à l'extrémité d'engagement (30), est inférieur au diamètre d'un cylindre fictif, insérable dans l'espace intérieur de l'attachement d'outil (33) entre le ou les entraîneurs en rotation (36).
  15. Dispositif selon l'une des revendications 2 à 14, caractérisé en ce que la surface de butée (38) est fixe relativement à l'attachement d'outil (33).
EP04820805A 2003-12-19 2004-11-24 Marteau perforateur et/ou marteau percuteur muni d'un raccord d'outil Not-in-force EP1694471B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10360008A DE10360008B4 (de) 2003-12-19 2003-12-19 Vorrichtung für einen Bohr- oder Schlaghammer mit Werkzeugaufnahme
PCT/EP2004/013349 WO2005063450A1 (fr) 2003-12-19 2004-11-24 Marteau perforateur et/ou marteau percuteur muni d'un raccord d'outil

Publications (2)

Publication Number Publication Date
EP1694471A1 EP1694471A1 (fr) 2006-08-30
EP1694471B1 true EP1694471B1 (fr) 2007-03-28

Family

ID=34672961

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04820805A Not-in-force EP1694471B1 (fr) 2003-12-19 2004-11-24 Marteau perforateur et/ou marteau percuteur muni d'un raccord d'outil

Country Status (7)

Country Link
US (1) US7661484B2 (fr)
EP (1) EP1694471B1 (fr)
JP (1) JP2007514554A (fr)
CN (1) CN100445044C (fr)
DE (2) DE10360008B4 (fr)
ES (1) ES2281028T3 (fr)
WO (1) WO2005063450A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9102045B2 (en) 2011-09-29 2015-08-11 Caterpillar Inc. System and method for easy removal of hydraulic hammer bushing
US9662778B2 (en) 2012-02-10 2017-05-30 Milwaukee Electric Tool Corporation Bit retention assembly for rotary hammer
DE102012210097A1 (de) * 2012-06-15 2013-12-19 Hilti Aktiengesellschaft Steuerungsverfahren

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2432105A1 (de) 1974-07-04 1976-01-22 Duss Maschf Schlag- oder drehschlaghammer
DE3331866A1 (de) * 1983-09-03 1985-03-21 Metabowerke GmbH & Co, 7440 Nürtingen Bohrhammer
DE3448189C2 (en) * 1984-08-08 1988-05-26 Black & Decker Inc., Newark, Del., Us Hammer drill
DE3714679A1 (de) 1985-11-11 1988-11-10 Hilti Ag Werkzeughalter
DE3745046C2 (de) * 1987-05-20 1996-07-25 Bosch Gmbh Robert Werkzeugaufnahme einer Handwerkzeugmaschine mit verdrehsicher einsetzbarem Werkzeug
DE4100186A1 (de) * 1991-01-05 1992-07-09 Bosch Gmbh Robert Handwerkzeugmaschine mit abnehmbaren werkzeughalter
DE4132023A1 (de) * 1991-09-26 1993-04-01 Bosch Gmbh Robert Einrichtung an handwerkzeugmaschinen
DE4136584B4 (de) 1991-11-07 2004-10-28 Hilti Ag Bohr- und Meisselgerät mit Werkzeugaufnahme
CN1060713C (zh) * 1995-10-12 2001-01-17 罗伯特-博希股份公司 用于具有钻和/或冲击驱动装置的电动机器的插装式工具和工具夹
DE19603528B4 (de) * 1996-02-01 2005-01-13 Robert Bosch Gmbh Handwerkzeugmaschine
DE19604282A1 (de) * 1996-02-07 1997-08-14 Bosch Gmbh Robert Werkzeughalter mit Aufnahme für verschiedene Werkzeugsysteme
JP3606021B2 (ja) * 1996-12-13 2005-01-05 日立工機株式会社 衝撃工具
JPH11104974A (ja) * 1997-10-06 1999-04-20 Makita Corp 打撃工具
DE69938838D1 (de) * 1998-11-12 2008-07-10 Black & Decker Inc Futter, bohrer, zusammenbau dafür und montagemethode
GB9910599D0 (en) * 1999-05-08 1999-07-07 Black & Decker Inc Rotary hammer
US6984571B1 (en) * 1999-10-01 2006-01-10 Ziptronix, Inc. Three dimensional device integration method and integrated device
US20030089509A1 (en) 2000-01-22 2003-05-15 Helmut Wanek Hand machine tool
FR2808720B1 (fr) * 2000-05-12 2002-07-26 Montabert Ets Appareil a percussion du type brise-roche
US6510904B1 (en) * 2000-05-26 2003-01-28 Nippon Pneumatic Mfg. Co., Ltd. Protected tool bushing for an impact hammer
DE10337470A1 (de) * 2003-08-14 2005-03-17 Atlas Copco Electric Tools Gmbh Spanneinrichtung für Sechskantbits

Also Published As

Publication number Publication date
DE10360008B4 (de) 2006-04-06
EP1694471A1 (fr) 2006-08-30
CN1856388A (zh) 2006-11-01
WO2005063450A1 (fr) 2005-07-14
CN100445044C (zh) 2008-12-24
US20070163794A1 (en) 2007-07-19
US7661484B2 (en) 2010-02-16
ES2281028T3 (es) 2007-09-16
JP2007514554A (ja) 2007-06-07
DE502004003363D1 (de) 2007-05-10
DE10360008A1 (de) 2005-07-14

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