EP0942809A1 - Dispositif d'entrainement pour outil a percussion - Google Patents

Dispositif d'entrainement pour outil a percussion

Info

Publication number
EP0942809A1
EP0942809A1 EP98918823A EP98918823A EP0942809A1 EP 0942809 A1 EP0942809 A1 EP 0942809A1 EP 98918823 A EP98918823 A EP 98918823A EP 98918823 A EP98918823 A EP 98918823A EP 0942809 A1 EP0942809 A1 EP 0942809A1
Authority
EP
European Patent Office
Prior art keywords
impact
drive
hammer
drive shaft
hammer member
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.)
Withdrawn
Application number
EP98918823A
Other languages
German (de)
English (en)
Inventor
Richard L. Marcengill
Gary L. Young
William C. Buck
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.)
Power Tool Holders Inc
Original Assignee
Power Tool Holders Inc
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
Priority claimed from US08/962,255 external-priority patent/US5992538A/en
Application filed by Power Tool Holders Inc filed Critical Power Tool Holders Inc
Publication of EP0942809A1 publication Critical patent/EP0942809A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode

Definitions

  • the present invention relates to an impact drive device configured for attachment to a drive spindle or chuck of a power tool, for example a hand drill, and more particularly to a portable tool drive incorporating an impact drive mechanism.
  • impact drive mechanisms are well understood by those skilled in the art.
  • impact drive mechanisms are conventionally incorporated into impact air wrenches and conventional hammer drills. These mechanisms add the additional benefit of a hammering effect to conventional rotational drives.
  • a drawback of conventional impact drive mechanisms is that such devices are typically only incorporated directly into the drive device of the drill or power tool. In other words, the entire tool constitutes the impact drive mechanism, and there are certain situations wherein an impact drive is not desired.
  • the impact drive tools of the known conventional devices are relatively sophisticated and expensive to manufacture and own, and generally can only be used as an impact tool.
  • 4,840,387 to McCarthy describes a keyless chuck device for attachment to a drive spindle of a drill in which the operating sleeve has impact members biased toward mating impact members associated with the rotatable nut.
  • the impact dogs disclosed in the *387 patent are meant to increase the tightening (or loosening) effect of the chuck device on a tool shank carried therein depending on the direction of rotation of the body of the chuck.
  • the chuck does not impart an impact drive to the tool bit once the chuck is tightened onto the tool bit.
  • An additional object of the present invention is to provide an impact tool drive which can be easily carried by any conventional chuck device and which thus converts any conventional drill into an impact drive tool.
  • Still a further object of the present invention is to provide an impact tool driver which can convert any manner of conventional drive tool to an impact drive tool.
  • Yet another object of the present invention is to provide an impact tool driver having an impact drive mechanism which is relatively simple and inexpensive to manufacture.
  • an impact tool drive which is configured for removable attachment to a drive spindle or chuck of a power tool, for example a conventional hand drill or similar device.
  • the impact tool driver includes a body member which is removably connectable to a rotational drive member of the power tool.
  • a drive shaft is operably configured with the body member so as to be rotationally driven therewith.
  • the drive shaft is formed as an integral part of the body member.
  • a hammer member is rotationally coupled to the drive shaft so as to be rotationally driven thereby.
  • the hammer member is axially movable relative to the drive shaft.
  • the hammer member includes a first impact face configured thereon with at least two impact drivers defined on the impact face.
  • a coupling drive mechanism is disposed between the drive shaft and the hammer member to impart rotational and longitudinal movement to the hammer member.
  • An anvil member includes a second impact face opposite the first impact face of the hammer member with an impact receiver configured thereon for periodic impacting engagement with the impact drivers.
  • the anvil member further comprises means for connecting a tool or working device thereto.
  • the hammer member is rotationally driven by the drive shaft while simultaneously moved axially back and forth relative to the drive shaft so that the impact drivers move into and out of rotational impacting engagement with the impact receiver.
  • a biasing member such as a spring, axially biases the hammer member into engagement with the anvil member.
  • the coupling device between the drive shaft and hammer member comprises a helical groove defined in the drive shaft and a complimenting radially opposite groove defined in the hammer member.
  • a drive ball is disposed in the grooves wherein the helical groove and drive ball impart rotational and axial movement to the hammer member as the drive shaft rotates.
  • the impact drivers preferably comprise circumferentially spaced lugs defined on the first impact face.
  • the impact receiver comprises corresponding protruding members defined on the second impact face which define radially opposite legs with circumferential recesses defined between the legs.
  • the lugs are axially movable into and out of the circumferential recesses for periodic rotational engagement with the protruding members as the drive shaft rotates.
  • the body member defines a shaft that further comprises first and second axially separated shaft sections.
  • An elastomeric coupling device is used to rotationally couple the two shaft sections. This embodiment is particularly desirable in that the elastomeric coupling absorbs a significant amount of the vibrations imparted back to the power tool or user through the body member.
  • the present inventive impact tool driver is useful in any environment wherein an impact drive mechanism is desired, and is not limited to any particular type of tool or drive.
  • the present impact tool driver will have particular usefulness with portable hand drills, the invention is not limited to this environment. Additional uses and environments are within the scope and spirit of the invention.
  • Figure 1 is a perspective view of an embodiment of the present invention in threaded engagement with a drive shaft
  • Figure 2 is a perspective view of an alternative embodiment of the invention mated with a chuck device of a drive tool
  • Figure 3 is a cut-away of a complete assembly of the present invention
  • Figure 4 is a cut-away operational view of the device illustrated in Fig. 3;
  • Figure 5 is a cut-away operational view of the device illustrated in Fig. 3;
  • Figures 6a - 6d are sequential views illustrating the operation of the impact drive mechanism according to the invention;
  • Figure 7 is a partial component view particularly illustrating the drive shaft and hammer member according to the invention.
  • Figures 8a - 8d are sequential diagrammatic views illustrating the coupling drive engagement between the drive shaft and hammer member;
  • Figure 9 is a cut-away view of the hammer member;
  • Figure 10 is an in-line component view of the invention.
  • Figure 11 is a cut-away view of an embodiment of the invention incorporating an elastomeric coupling device in the drive shaft;
  • Figure 12 is a partial assembly drawing of one embodiment of the coupling device of Fig. 11;
  • Figure 13 is an alternative embodiment of the coupling device. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • Impact tool driver 10 can be used in any application or environment wherein it is desired to impart an impacting drive to a tool.
  • impact tool driver 10 is illustrated as having a conventional ball detente mechanism 44 configured in a shaft 68 for attachment to any manner of tool.
  • a socket could be attached by way of the ball detente mechanism 44.
  • impact tool driver 10 can be configured with any conventional driving device, such as a conventional hand drill or other portable tool having a driven spindle or drive shaft.
  • Impact tool driver 10 according to the invention is particularly suited for configuration with a portable hand drill in that it converts such a conventional hand drill into an impact tool, as will be described below.
  • FIG. 1 illustrates device 10 held to a drive spindle or shaft 12 by means of a conventional threaded engagement 16.
  • the drive spindle 12 has a male threaded section that threadedly engages within a female receiving section defined in a shank portion 20 of impact tool driver 10.
  • the threaded sections could be interchanged so that impact tool driver 10 contains the male threads.
  • Fig. 2 illustrates impact tool driver 10 held by means of a conventional chuck device 14. It should be appreciated that any mechanical locking mechanism can be utilized for rotationally locking device 10 to a drive spindle.
  • a set screw type of engagement between the shank 20 and drive spindle 12 could be utilized.
  • any type of conventional chuck device could be utilized, including a keyed or keyless chuck. Any and all such locking mechanisms are within the scope and spirit of the invention and are included in the means for removably attaching impact tool driver 10 to a drive spindle 12.
  • the invention is not limited by any type of means or mechanism for connecting a tool or working device thereto.
  • the ball and detente device 44 illustrated in the figures is merely an example of one well-known suitable device.
  • device 10 could include a square or multi-sided receptacle for receiving square or hex shaped tool bits.
  • the device could include a star-shaped recess for mating configuration with a conventional star-shaped tool shank.
  • a set screw device could also be utilized.
  • These conventional connecting means are well understood by those skilled in the art and need not be explicitly described herein. Any and all such connecting means are within the scope and spirit of the invention.
  • Impact tool driver 10 includes a body member, generally 18, which is configured for attachment to a drive spindle of the tool, as described above.
  • body member 18 includes a shank portion 20 which may include a threaded receiving portion as shown in Fig. 1, or a multi-sided portion as shown particularly in Fig. 7.
  • Body member 18 is rotationally driven by the drive spindle of a power tool once the body member is rotationally locked to the drive spindle.
  • Impact tool driver 10 also includes a drive shaft, generally 22, that is configured with body member 18 so as to be rotationally driven therewith.
  • drive shaft 22 is formed as an integral part of body member 18. However, it should be understood, that drive shaft 22 may comprise a separate component that is rotationally locked to body member 18.
  • a hammer member is rotationally coupled to drive shaft 22 so as to be rotationally driven thereby.
  • Hammer member 24 is axially movable relative to drive shaft 22, as will be explained in more detail below.
  • Hammer member 24 comprises a first impact face 26 defined thereon which includes at least two impact drivers or lugs 28 defined on impact face 26.
  • the impact lugs or drivers 28 extend longitudinally from first impact face 26, as particularly seen in Figs. 3 through 5.
  • the impact lugs 28 preferably have a generally triangular shape defining radial impact faces 29, as seen in Figs. 6a through 6d.
  • Hammer member 24 is co-axial with drive shaft 22 as seen in Figs. 3 through 5, and includes an annular recess 58 defined therein.
  • a coupling drive mechanism is operably disposed between drive shaft 22 and hammer member 24 to impact rotational and longitudinal movement to hammer member 24.
  • the coupling drive mechanism 30 comprises a ball 32 which resides in opposing helical grooves defined in shaft 22 and hammer member 24. Referring particularly to Figs. 3 through 5 and 7 through 9, a first helical groove 34 is defined in drive shaft 22. An opposing helical groove is defined in hammer member 24. Ball 32 resides within grooves 34 and 36 respectively. The operation of the device to impart rotational and longitudinal movement to hammer member 24 will be explained in greater detail below.
  • Impact tool driver 10 also includes an anvil member 38 that is rotationally driven by hammer member 24.
  • Anvil member 38 includes a second impact face 40 that is opposite first impact face 26 of hammer member 24.
  • Anvil member 38 includes an impact receiver configured on impact face 40 for periodic impacting engagement with impact drivers or lugs 28.
  • the impact receiver is defined by a protruding member 54 defining radial legs that essentially divides the second impact face 40 into halves 56.
  • Halves 56 define a recess space relative to protruding member 54.
  • Impact drivers or lugs 28 move within recesses 56 and impact against protruding member 54 to rotationally drive anvil member 38.
  • Anvil member 38 also includes an alignment groove or hole 66 defined therein.
  • An alignment tab 64 extending from body member 18 fits into a groove or hole 66 and provides a bearing and alignment mechanism between anvil member 38 and body member 18.
  • Anvil member 18 also contains a shank portion 68 having any conventional means 42 for connecting a tool thereto, such as the ball and detente device 44 discussed above.
  • Shank 68 extends through a hole defined in a front face of sleeve member 46.
  • a biasing spring 52 is disposed within sleeve 46 and resides within annular groove 58 defined in hammer member 24, as particularly seen in Figs. 3 through 5.
  • a bearing plate 62 and bearing device 60 are also disposed in annular groove 58.
  • a backing plate 50 is fitted onto body member 18 and abuts against a shoulder 19 defined on body member 18. Spring 52 abuts against backing plate 50.
  • a retaining clip or ring 48 holds sleeve member 46 relative to body member 18 and backing plate 50. Spring 52 biases hammer member 24 longitudinally forward against anvil member 38
  • impact tool driver 10 is attached to a drive spindle or shaft 12, as generally shown in Figs. 1 and 2.
  • body member 18 and drive shaft 22 are also rotated.
  • the helical grooves 34, 36 and ball 32 coupling device imparts a rotational and longitudinal movement to hammer member 24.
  • Fig. 3 illustrates the device wherein impact drivers or lugs 28 are fully within recesses 56 of anvil member 38. Alignment of the ball 32 and grooves 34, 36 corresponds to the representation shown in Fig. 8a.
  • hammer member 24 is also rotated and caused to move axially relative to drive shaft 22 in a direction towards the back end of the device, as shown in Figs. 4 and 8b.
  • Fig. 8c illustrates the device wherein hammer member 24 has moved axially rearward to its fullest extent. At this point, impact drivers or lugs 28 move over protruding member 54. Drive shaft 22 continues to rotate and once impact drivers or lugs 28 pass over protruding member 54, spring 52 causes hammer member 24 to move axially forward so that impact lugs 28 again fall into recesses 56 of anvil member 38. At this point, drive shaft 22 continues to rotate and impact drivers or lugs 28 spin and bang or impact against protruding member 54 thereby imparting a periodic impacting engagement between impact drivers 28 and impact receiver or protruding member 54.
  • FIG. 6a illustrates the device wherein impact lugs 28 have initially impacted against protruding member 54 and cause protruding member 54, and thus anvil member 38, to rotate in the clockwise direction to the position shown in Fig. 6b. Simultaneously with the rotating movement, hammer member 24 is also being moved axially rearward so that impact lugs 28 move over protruding member 54, as seen in Fig. 6c. Once impact lugs 28 are completely over protruding member 54, they are forced back into recesses 56 as shown in Fig. 6d and continue to rotate again until they impact against protruding member 54.
  • Figs. 8a through 8d show a side view representation of the relative positions of grooves 34, 36, and ball 32.
  • the sequential view of Figs. 8a through 8d correspond to sequential Figs. 6a through 6d.
  • Fig. 8a illustrates the arrangement wherein the hammer member 24 is moved fully axially forward and is rotating within recesses 56, as seen in Fig. 6a.
  • Fig. 8b depicts hammer member 24 moving axially rearward
  • Fig. 8c illustrates hammer member 24 in its fullest axially rearward position wherein drive or impact lugs 28 are passing over protruding member 54, as seen in Fig. 6c.
  • a rotational and longitudinal movement is imparted to hammer member 24 which, in turn, provides a periodic impacting force to anvil member 38.
  • the driving force of the impact drive mechanism depends on a number of factors.
  • the weight of the hammer member relative to the anvil member will affect the degree of force transmitted to the anvil member for each impact.
  • the angle of the impacting face 29 of the impact lugs 28 is also a consideration. Maximum force is imparted if face 29 is flush against protruding member 54.
  • the rotational speed of the impact drivers or lugs 28 is also a consideration and will obviously be affected by the rotational speed of the drive spindle, as well as the diameter of the first impact face 26 defined on hammer member 24.
  • body member 18 defines a shaft that includes two sections 22a, 22b. The sections are separated by and rotationally coupled with a coupling device 100.
  • Coupling device 100 is preferably formed of an elastomeric material, such as a soft grade of polyurethane, rubber, or the like. This particular embodiment of the invention may be preferred wherein it is desired to decrease vibrations imparted back through the body member to the power tool or user.
  • the elastomeric coupling device 100 absorbs the vibrations and substantially reduces the vibrations imparted to the power tool or user.
  • drive shaft sections 22a and 22b are axially spaced apart and are not physically engaged with each other.
  • shaft section 22a includes a front end or hub portion 106 with radially extending drive dogs 102. Recesses 107 are defined between the drive dogs
  • drive shaft section 22b includes an end or hub 105 with radially extending drive dogs 103 and recesses 108 defined therebetween.
  • Elastomeric coupling 100 also includes drive dogs 109 separated by recesses 110 for rotational coupling engagement with drive dogs
  • first shaft section 22a drives second shaft section 22b through the rotational coupling 100.
  • shaft sections 22a and 22b comprise holes 111 defined therein.
  • the elastomeric material is co-molded with the shaft sections so that the material fills holes 111 and also the space between faces 106, 105, of the shaft portions. In this manner, coupling 100 is molded or integrally formed with the shaft portions.
  • coupling 100 is meant to rotationally couple the drive shaft sections while simultaneously absorbing vibrations imparted to the shafts from the hammer mechanism.
  • coupling 100 can be formed of any manner of conventional material for fulfilling this purpose. Any number of materials and construction of device 100 are within the scope and spirit of the invention.
  • coupling 100 resides in a recess 101 defined between backing plate 50 and an additional plate 51.
  • Plate 51 is fitted onto second shaft section 22b.
  • Spring 52 bears against the opposite side of plate 51.

Landscapes

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

Abstract

L'invention se rapporte à un dispositif d'entraînement (10) portatif pour outil à percussion, ce dispositif étant fixé amovible à un arbre d'entraînement (12) d'un outil à commande mécanique classique. Ce dispositif (10) comporte un corps (18) et un arbre d'entraînement (22) couplé audit corps (18) de manière à être entraîné rotatif par ce dernier. Un marteau (24) est couplé rotatif à l'arbre d'entraînement (22) et est entraîné rotatif par ce dernier. Ce marteau (24) se déplace également dans le sens axial le long dudit arbre d'entraînement (22) et présente une première surface (26) de percussion comportant au moins deux dispositifs d'entraînement (28) par percussion. Un mécanisme d'entraînement (30) de couplage est installé entre l'arbre d'entraînement (22) et le marteau (24) et confère un mouvement rotatif et longitudinal au marteau (24). Une enclume (38) présente une seconde surface (40) de percussion, opposée à la première surface (26) de percussion, un récepteur (54) de percussions étant situé sur cette surface en vue de venir percuter périodiquement les dispositifs d'entraînement (28) par percussion.
EP98918823A 1997-08-08 1998-04-28 Dispositif d'entrainement pour outil a percussion Withdrawn EP0942809A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US962255 1992-10-16
US90877797A 1997-08-08 1997-08-08
US908777 1997-08-08
US08/962,255 US5992538A (en) 1997-08-08 1997-10-31 Impact tool driver
PCT/US1998/008536 WO1999007521A1 (fr) 1997-08-08 1998-04-28 Dispositif d'entrainement pour outil a percussion

Publications (1)

Publication Number Publication Date
EP0942809A1 true EP0942809A1 (fr) 1999-09-22

Family

ID=27129511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98918823A Withdrawn EP0942809A1 (fr) 1997-08-08 1998-04-28 Dispositif d'entrainement pour outil a percussion

Country Status (6)

Country Link
EP (1) EP0942809A1 (fr)
JP (1) JP2001501877A (fr)
CN (1) CN1236338A (fr)
AU (1) AU7167598A (fr)
BR (1) BR9806086A (fr)
WO (1) WO1999007521A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2430907A (en) * 2005-10-10 2007-04-11 Bosch Gmbh Robert Manual machine tool attachment having impact screwdriver function

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2603527C (fr) * 2005-04-13 2013-02-12 Cembre S.P.A. Mecanisme d'impact pour une cle a chocs
EP1961522B1 (fr) * 2007-02-23 2015-04-08 Robert Bosch Gmbh Outil d'alimentation rotatif qui fonctionne en mode d'impact ou en mode de forage
JP5426197B2 (ja) * 2009-03-10 2014-02-26 株式会社マキタ 打撃工具
DE102010029559A1 (de) * 2010-06-01 2011-12-01 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Schlagwerk
EP2806734B1 (fr) * 2011-12-23 2019-02-27 Shoof International Limited Mécanisme amélioré de transmission pour outil motorisé portatif
DE102011089913A1 (de) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Handwerkzeugvorrichtung
DE102011089910A1 (de) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Handwerkzeugvorrichtung
US10259111B2 (en) 2013-04-03 2019-04-16 Robert Bosch Gmbh Tool attachment for a hand-held power tool
US9505107B2 (en) 2013-05-14 2016-11-29 Snap-On Incorporated Ball deflecting chamfer
CN104175160B (zh) * 2013-05-21 2017-04-19 苏州宝时得电动工具有限公司 动力工具
JP6198515B2 (ja) * 2013-08-08 2017-09-20 株式会社マキタ インパクト工具
CN111331559A (zh) * 2018-12-18 2020-06-26 宝时得科技（中国）有限公司 电镐转接组件以及电镐
WO2021156314A1 (fr) * 2020-02-03 2021-08-12 A Hansson Holding Ab Modules de marteau pilon, système de marteau pilon adaptatif et procédé correspondant
CN113386074B (zh) * 2020-03-11 2023-10-24 喜利得股份公司 冲击工具

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US1925714A (en) * 1931-01-08 1933-09-05 George W Crist Combination wrench and anvil
US2227627A (en) * 1938-11-03 1941-01-07 Perfection Auto Parts Mfg Co Rotary tool
US2794621A (en) * 1951-06-11 1957-06-04 William D Sellers Drilling attachments
US3006446A (en) * 1954-01-25 1961-10-31 Ingersoll Rand Co Impact tools
US2940565A (en) * 1956-05-14 1960-06-14 Schodeberg Carl Theodore Power driven impact tool
US2923191A (en) * 1958-10-21 1960-02-02 Fulop Charles Power operated, predetermined torque release, axial-impact type hand tool

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2430907A (en) * 2005-10-10 2007-04-11 Bosch Gmbh Robert Manual machine tool attachment having impact screwdriver function
GB2430907B (en) * 2005-10-10 2009-08-05 Bosch Gmbh Robert Manual machine tool attachment

Also Published As

Publication number Publication date
WO1999007521A1 (fr) 1999-02-18
BR9806086A (pt) 1999-08-24
CN1236338A (zh) 1999-11-24
JP2001501877A (ja) 2001-02-13
AU7167598A (en) 1999-03-01

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