EP1307313A1 - Machine portable - Google Patents

Machine portable

Info

Publication number
EP1307313A1
EP1307313A1 EP01943165A EP01943165A EP1307313A1 EP 1307313 A1 EP1307313 A1 EP 1307313A1 EP 01943165 A EP01943165 A EP 01943165A EP 01943165 A EP01943165 A EP 01943165A EP 1307313 A1 EP1307313 A1 EP 1307313A1
Authority
EP
European Patent Office
Prior art keywords
intermediate shaft
tool according
disc
hand
hand tool
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
EP01943165A
Other languages
German (de)
English (en)
Other versions
EP1307313B1 (fr
EP1307313B2 (fr
Inventor
Peter Holzer
Robert Simm
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7651168&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1307313(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1307313A1 publication Critical patent/EP1307313A1/fr
Publication of EP1307313B1 publication Critical patent/EP1307313B1/fr
Application granted granted Critical
Publication of EP1307313B2 publication Critical patent/EP1307313B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—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
    • B25D16/003—Clutches specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle
    • 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
    • B25D2250/195—Regulation means
    • B25D2250/201—Regulation means for speed, e.g. drilling or percussion speed

Definitions

  • the invention is based on a hand tool according to the preamble of claim 1.
  • a hand tool of this type is known (DE 198 03 454 A1).
  • a drill spindle which can be driven by the drive motor can be locked in a rotationally fixed manner relative to the housing of the handheld power tool, so that a tool holder screwed to the drill spindle, e.g. B. a chuck, from the drill spindle! solved and / or a tool can be clamped in the tool holder.
  • the locking device is arranged on an intermediate shaft which can be coupled to the drilling spindle via two gear stages. The locking device opens automatically when torque is transmitted from the drive motor in the direction of Tool holder and locks automatically when transmitting torque from the tool holder to the drive motor.
  • the handheld power tool according to the invention with the features of claim 1 has the advantage that in the form of the torque-dependent safety coupling, overload protection for the user when the drill spindle is suddenly blocked, e.g. due to hooking of the drill.
  • an overload protection is achieved that protects the existing gear or the locking device against overload. Due to the inclusion of the safety clutch in the locking device, practically no additional effort for the safety clutch is necessary. There is also no need for additional installation space in the machine housing or a special adaptation of the machine housing to any installation space required for this. Through the integration, the number of components required for the locking device or safety clutch is also as small as possible. Overall, despite the additional safety coupling provided, practically no additional effort in terms of assembly and costs is required.
  • 1 is a longitudinal section with a partial side view of an impact drill
  • FIG. 3 shows a section along the line III-III in FIG. 2.
  • FIG. 1 schematically shows a handheld power tool in the form of an impact drill 10 with a drive motor (not shown in more detail) arranged in a machine housing 26 for at least rotatingly driving a tool holder 12.
  • the drive motor has a motor shaft 14, which is provided at the end with a drive pinion 15 or a similar toothing and in a flange 27 by means of a bearing 29, e.g. Ball bearing, is rotatably mounted.
  • the flange 27 is a separate component and is firmly connected to the machine housing 26.
  • the drive motor is connected via the motor shaft 14 in a gear connection to a drilling spindle 13 with which the tool holder 12 is detachably connected, for. B. is screwed via a thread 35.
  • the drive pinion 15 meshes with a gearwheel 16, which is shown in FIG. 2 and is coaxial with the intermediate shaft 17 and which is rotatable relative to the intermediate shaft 17.
  • the intermediate shaft 17 is rotatably supported in the flange 27 by means of a needle bearing 48 with an end-side shaft journal 46.
  • the other shaft journal 47 is rotatably supported in the machine housing 26 by means of a needle bearing 49
  • Intermediate shaft 17 has a toothing 18 and next to it a rotationally fixed, z. B. hot pressed, gear 19, which are in engagement with gears 20 and 21 which are rotatably mounted on the drilling spindle 13 and alternatively z. B.
  • the pulling wedge 23 forms, together with the gear wheels 20, 21 and an actuating device (not shown further here), a manual transmission 24 with two gears.
  • a first gear (slow speed) is formed by the tooth pairing 18, 20 and a second gear (fast speed) by the tooth pairing 19, 21.
  • the gear ratio of these gear stages 18, 20 and 19, 21 is negative, ie there is a translation from the meantime 17 to the drilling spindle 13 in slow.
  • a catch mechanism 28 received in the flange 27, via which axial impacts can be applied to the drilling spindle 13 in a known manner.
  • the catch mechanism 28 can be switched off in the usual way, so that the impact drill 10 can also be used as a drill with two gears.
  • the tool holder 12 is e.g. B. designed as a jaw chuck, which has adjustable jaws 32 by means of a sleeve 31 and a non-rotatably connected conical nut, between which the shank of a tool can be clamped.
  • a base body 33 of the tool holder 12 is screwed on the thread 35 on a threaded pin 34 of the drilling spindle 13 with high prestress, so that the tool holder 12 and the drilling spindle 13 are connected to one another in a rotationally fixed manner in the case of the impact drill 10.
  • a dust collar 30 of the sleeve 31 projects into an opening in the machine housing 26.
  • the drilling spindle 13 absorbs a loosening or tightening torque when changing the tool and can be coupled in a rotationally fixed manner relative to the flange 27 of the machine housing 26 by means of a locking device 38.
  • the locking device 38 is arranged between the drilling spindle 13 and part of the machine housing 26 on the intermediate shaft 17.
  • Part of the locking device 38 is an approximately ring-shaped housing 43, which is held non-rotatably and positively in a part of the flange 27 by means of radial projections 43a.
  • the housing 43 contains a cylindrical bore 53 which is coaxial with the intermediate shaft 17.
  • a radially projecting driver element 41 having a disk 40 which is arranged on the intermediate shaft 17 such that it can rotate and at least slightly axially displaceably.
  • the locking device 38 also includes the gear 16, which can be driven by the drive motor via the drive pinion 15 and rotates relative to the intermediate shaft 17 and which has approximately claw-like projections 39a, 39b on one end face facing the disk 40 and extends approximately parallel to one another and towards the disk 40 ,
  • These projections 39a, 39b can be held in the form of cylindrical pins which fit into and can circulate in the annular space which is formed between the bore 53 on the one hand and an outer peripheral surface 54 of the disk 40 on the other hand, which are diametrically opposed between the two Driver elements 41 extends.
  • the driver elements 41 are shaped such that the disk 40 can be rotated to a limited extent between adjacent claws 39a, 39b.
  • the outer circumferential surface 54 of the disk 40 has a cylindrical basic shape, this cylindrical basic shape then merging approximately centrally between two adjacent driver elements 41 into a flattened area 42.
  • this cylindrical basic shape then merging approximately centrally between two adjacent driver elements 41 into a flattened area 42.
  • In the area of the outer surface of the driver elements 41 there is only a slight amount of movement between them and the bore 53 of the housing 43.
  • In the adjoining area of the cylindrical circumferential surface 54 of the disk 40 there is a radial distance between the disk 40 and the bore 53 which is just sufficient to accommodate the projections 39a, 39b with little movement play.
  • In the area of the respective flat 42 there is a larger radial one Distance between the bore 53 and the flat 42 of the disc.
  • a cylindrical rolling element 45 is accommodated with little movement play, the diameter of which exceeds the radial thickness of the approximately claw-shaped projections 39a, 39b.
  • the rolling elements 45 form pinch rollers.
  • the claw-like projections 39a, 39b can be of different lengths in the circumferential direction, for example, pairs 39a on the one hand and 39b on the other diagonally opposite each other can each have the same length. Instead, the projections 39a, 39b can also be the same size.
  • the projections 39a When torque is transmitted from the drive motor via the motor shaft 14 with drive pinion 15 to the gearwheel 16, the projections 39a have a torque-transmitting effect on the driver elements 41, the rolling elements 45 then coming to rest in front of the adjacent claws 39b due to their persistence. The adjacent claws 39b then hold the rolling elements 45 in the area of the respective flats 42, so that unimpeded torque transmission is ensured, in this example and in the representation according to FIG. 3 in a clockwise direction.
  • the driver elements 41 each have a torque-transmitting effect on the projections 39a, b. Due to their persistence, the rolling elements 45 are then pushed in the direction of the torque-transmitting projections 39a, b, in which case they then move clamp between the flats 42 of the disc 40 and the bore 53 of the housing 43. As a result, the disc 40 is automatically locked in place with the housing.
  • a safety clutch 58 is included, which is also arranged on the intermediate shaft 17.
  • the safety clutch 58 is, for. B. formed as a slip clutch or front teeth tooth clutch. It is arranged axially on the driven side of the locking device 38. It offers overload protection for the user as well as for the locking device 38 and the transmission described, is extremely simple and requires only a small installation space. Since the safety clutch 58 is integrated in the locking device 38, the number of components is further reduced. Furthermore, a reduction in assembly effort is achieved.
  • the safety clutch 58 is formed between the disk 40, which has the radial driver elements 41, on the one hand, and an abutment surface 59 fixed on the intermediate shaft, which here is formed by the axial end face of the gearwheel 19 of the one gear stage, which is connected in a rotationally fixed manner to the intermediate shaft 17.
  • the disk 40 can be pressed axially against this stop surface 59 with a facing end face 44 by means of resilient axial force supported on the intermediate shaft 17.
  • the end of the sleeve 60 facing the disk 40 axially abuts the disk 40 and is pressed there.
  • the resilient axial force acts on the other end of the sleeve 60 facing away from the disk 40.
  • at least one spring 61 in particular plate spring, which generates the axial force is arranged on the intermediate shaft 17.
  • a plurality of disc springs 61 are provided. These sit directly on the intermediate shaft 17.
  • the plate springs 61 are axially supported on the right side in FIG. 2 by means of a retaining washer 62 and a locking washer 63 with respect to the intermediate shaft 17.
  • the locking washer 63 is positively received in a groove 64 of the intermediate shaft 17.
  • Shims 65 are arranged between the plate springs 61 and the facing end face of the sleeve 60. Because of the arrangement described, the at least one spring, here in the form of the plate springs 61, is axially supported on the one hand on the intermediate shaft 17, on the other hand it acts resiliently on the facing end of the sleeve 60. The sleeve 60 is thus axially resiliently loaded towards the left in FIG. 2. With the end facing away from the disk 40 and thus facing the at least one spring 61, the sleeve 60 projects axially beyond the right-hand end face of the gearwheel 16 in FIG. 2. The gear 6 is rotatably mounted on the sleeve 60. With the left end in FIG.
  • the sleeve 60 also projects beyond the end face of the gearwheel 16 there, the sleeve 60 being pressed axially with this end face onto the facing end face 66 of the disk 40.
  • the face 40 of the disk 40 which is rotatable and at least slightly axially displaceable on the intermediate shaft 17 is pressed against the associated stop face 59 of the gearwheel 19, so that the disk 40 transmits torque with the gearwheel 19 and via this with the intermediate shaft 17 in Connection is established.
  • the disk 40 has a hub 67, which extends in FIG. 2 on the right to the facing end face of the sleeve 60 and has the end face 66 acted upon by the sleeve 60.
  • the stop surface 59 which is fixed to the intermediate shaft, of the gearwheel 19, which is connected to the intermediate shaft 17 in a rotationally fixed manner, on the one hand, and the end face 44 of the disk 40 assigned to this, on the other hand, can face the mutually facing ones and by means of the at least one spring 61 resiliently pressed together end faces forming a frictional engagement, z. B. friction surfaces.
  • these surfaces 59 and 44 can also have surface elevations and surface depressions, in particular end teeth integral therewith, which bring about a positive engagement.
  • the safety coupling 58 is designed as a form-fitting coupling of this type, in which the surfaces 44 and 59 that are in contact with one another thus have one-piece front teeth, not shown.
  • the gear wheel 19 is completely manufactured as a sintered part, in which the front teeth as parts of the safety clutch 58 are formed at the same time as they are produced, thereby achieving considerable cost savings.
  • the complete disk 40, together with its driver elements 41 and the hub 67, which is integral therewith, and the front teeth on the end face 44, is also designed as a sintered part, so that the costs for this are also minimized.
  • the sleeve 60 as a further part of the safety coupling 58 represents a simple, inexpensive component that does not require any additional installation space.
  • the safety clutch 58 provides overload protection for the user as well as for the locking device 38 and the transmission. It is integrated in a cost-saving manner in the locking device 38, which is also designed to be cost-effective without requiring a larger installation space due to the arrangement of the safety coupling 58. Due to the reduced proportion of the components, the assembly effort is also reduced.
  • the safety clutch 58 is arranged axially next to the locking device 38 and on the driven side thereof, which is predetermined by the disk 40, and thus at an axial distance from the locking device 38.
  • the disk 40 When the drive force is transmitted from the motor shaft 14 via the gearwheel 16 and its claw-like projections 39a, b to the driver elements 41, the disk 40 is driven, with an effective safety clutch 58 the drive torque is transmitted from the disk 40 to the gear 19 and thus to the intermediate shaft 17.
  • the safety clutch 58 responds in such a way that the disk 40 is pressed axially against the force of the at least one spring 61 to the right in FIG. 2 and thus the drive between the Washer 40 and the gear 19 is separated. This protects the user from excessive reverse torques of the machine and prevents damage or destruction of the locking device 38.
  • the safety clutch 58 is adjusted with regard to its transmissible torque in such a way that in this state of jamming by the rolling elements 45, the safety clutch 58 does not yet respond in the sense of a decoupling, since this occurs in the drilling spindle 13 initiated moment z. B. for changing the tool or loosening the tool holder 12 is less than the permissible transmissible torque of the safety clutch 58. Only when an inadmissible higher torque is introduced via the drilling spindle 13 can the safety clutch 58 also respond in the uncoupling sense, to also then avoid damage or destruction of the locking device 38 and the transmission.

Abstract

L'invention concerne une machine portable comprenant un porte-outil pouvant être entraîné au moins en rotation, au moyen d'un moteur d'entraînement et d'une broche de perçage (13), et présentant un mandrin pour la fixation des outils, pouvant être actionné dans le sens de rotation de la broche (13), ainsi qu'un dispositif de blocage (38) au moyen duquel la broche (13) peut être accouplée non tournante par rapport à une partie (27) du bâti de la machine (26), pour la fermeture et l'ouverture du mandrin du porte-outil (12), s'ouvrant automatiquement lors du transfert du couple de rotation du moteur d'entraînement au porte-outil (12), et se bloquant automatiquement lors du transfert du couple de rotation du porte-outil (12) au moteur d'entraînement. Le dispositif de blocage (38) est disposé sur un arbre intermédiaire (17), en combinaison avec un accouplement de sécurité (58) qui est monté également sur l'arbre intermédiaire (17).
EP01943165A 2000-08-03 2001-05-29 Machine portable Expired - Lifetime EP1307313B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10037808A DE10037808A1 (de) 2000-08-03 2000-08-03 Handwerkzeugmaschine
DE10037808 2000-08-03
PCT/DE2001/002035 WO2002011933A1 (fr) 2000-08-03 2001-05-29 Machine portable

Publications (3)

Publication Number Publication Date
EP1307313A1 true EP1307313A1 (fr) 2003-05-07
EP1307313B1 EP1307313B1 (fr) 2007-08-01
EP1307313B2 EP1307313B2 (fr) 2009-08-19

Family

ID=7651168

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01943165A Expired - Lifetime EP1307313B2 (fr) 2000-08-03 2001-05-29 Machine portable

Country Status (6)

Country Link
US (1) US6793023B2 (fr)
EP (1) EP1307313B2 (fr)
JP (1) JP2004524168A (fr)
CN (1) CN1211176C (fr)
DE (2) DE10037808A1 (fr)
WO (1) WO2002011933A1 (fr)

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0210029D0 (en) * 2002-05-02 2002-06-12 Black & Decker Inc Detent mechanism
DE10316889B4 (de) * 2003-04-12 2007-06-06 Metabowerke Gmbh Elektrohandwerkzeuggerät mit einem Klemmgesperre
DE10338608B3 (de) * 2003-08-22 2004-10-07 Metabowerke Gmbh Elektrohandwerkzeuggerät
US6886643B2 (en) * 2003-09-05 2005-05-03 Credo Technology Corporation Shaft lock mechanism for a rotary power hand tool
DE102004052124B3 (de) * 2004-10-27 2006-04-27 Metabowerke Gmbh Motorisch antreibbares Werkzeuggerät mit einer Spindelarretiereinrichtung
DE102004059331B4 (de) * 2004-12-09 2021-02-18 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Kupplung
US20060213675A1 (en) * 2005-03-24 2006-09-28 Whitmire Jason P Combination drill
DE102005040547A1 (de) * 2005-08-26 2007-03-01 BSH Bosch und Siemens Hausgeräte GmbH Elektromotorisches Küchengerät mit einem Bajonettverschluss für einen Elektromotor und eine Getriebestufe und Verfahren zum Montieren eines elektromotorischen Küchengeräts
DE102005040544A1 (de) * 2005-08-26 2007-03-01 BSH Bosch und Siemens Hausgeräte GmbH Küchengerät mit einer verstärkten Elektromotor-Getriebestufen-Anordnung und Verfahren zum Herstellen eines elektromotorischen Küchengeräts
US7410007B2 (en) * 2005-09-13 2008-08-12 Eastway Fair Company Limited Impact rotary tool with drill mode
DE102005056205A1 (de) * 2005-11-25 2007-06-06 Robert Bosch Gmbh Bohrhammer mit drei Betriebsarten
CN101204804B (zh) * 2006-12-21 2011-09-07 苏州宝时得电动工具有限公司 动力工具
DE102007000313A1 (de) * 2007-06-06 2008-12-11 Hilti Aktiengesellschaft Elektrisches Handwerkzeuggerät mit Spindellockvorrichtung
US7793560B2 (en) * 2007-09-11 2010-09-14 Black & Decker Inc. Transmission and variable radially expanding spring clutch assembly
US7717191B2 (en) 2007-11-21 2010-05-18 Black & Decker Inc. Multi-mode hammer drill with shift lock
US7735575B2 (en) 2007-11-21 2010-06-15 Black & Decker Inc. Hammer drill with hard hammer support structure
US7854274B2 (en) 2007-11-21 2010-12-21 Black & Decker Inc. Multi-mode drill and transmission sub-assembly including a gear case cover supporting biasing
US7798245B2 (en) 2007-11-21 2010-09-21 Black & Decker Inc. Multi-mode drill with an electronic switching arrangement
US7762349B2 (en) 2007-11-21 2010-07-27 Black & Decker Inc. Multi-speed drill and transmission with low gear only clutch
US7770660B2 (en) 2007-11-21 2010-08-10 Black & Decker Inc. Mid-handle drill construction and assembly process
US7717192B2 (en) 2007-11-21 2010-05-18 Black & Decker Inc. Multi-mode drill with mode collar
DE102008040031A1 (de) * 2008-06-30 2009-12-31 Robert Bosch Gmbh Mehrgang-Getriebevorrichtung und Werkzeugmaschine
EP2216114B1 (fr) * 2009-02-05 2013-08-28 Techtronic Power Tools Technology Limited Ensemble de mandrin d'outil électrique doté d'un mécanisme marteau
US8540580B2 (en) 2009-08-12 2013-09-24 Black & Decker Inc. Tool bit or tool holder for power tool
DE102011089913A1 (de) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Handwerkzeugvorrichtung
DE102012211907A1 (de) 2012-07-09 2014-01-09 Robert Bosch Gmbh Drehschlagschrauber mit einem Schlagwerk
US9630307B2 (en) 2012-08-22 2017-04-25 Milwaukee Electric Tool Corporation Rotary hammer
US10512971B2 (en) * 2013-08-28 2019-12-24 Positec Power Tools (Suzhou) Co., Ltd. Power tool and operation method for quick locking and releasing working attachment thereof
DE102014224931A1 (de) 2014-12-04 2016-06-09 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Drehmomentkupplung
US10328560B2 (en) * 2015-02-23 2019-06-25 Brian Romagnoli Multi-mode drive mechanisms and tools incorporating the same
CN105987143B (zh) * 2015-02-25 2019-04-19 南京德朔实业有限公司 花园类工具及其传动系统
CN110937531B (zh) * 2019-09-11 2021-04-09 国网浙江省电力有限公司金华供电公司 一种手自一体化吊装驱动机构
DE102020212427A1 (de) 2020-10-01 2022-04-07 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Erfassung eines Getriebespiels in einer Werkzeugmaschine, insbesondere Handwerkzeugmaschine, sowie Werkzeugmaschine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2522446C3 (de) 1975-05-21 1982-10-28 Kress-elektrik GmbH & Co, Elektromotorenfabrik, 7457 Bisingen Sicherheitsrutschkupplung für Handbohrmaschine
US4400995A (en) * 1981-09-23 1983-08-30 Milwaukee Electric Tool Corporation Spindle lock with impacting capability
DE3821594A1 (de) * 1988-06-27 1989-12-28 Hilti Ag Motorisch betriebenes handwerkzeug
DE4135240A1 (de) * 1991-10-25 1993-04-29 Bosch Gmbh Robert Bohrhammer
DE4213291C2 (de) * 1992-04-23 1997-12-04 Atlas Copco Elektrowerkzeuge Getriebeeinrichtung einer handgeführten Bohrhammermaschine
US5372206A (en) * 1992-10-01 1994-12-13 Makita Corporation Tightening tool
US5588496A (en) * 1994-07-14 1996-12-31 Milwaukee Electric Tool Corporation Slip clutch arrangement for power tool
JP3582760B2 (ja) * 1997-04-18 2004-10-27 日立工機株式会社 ハンマドリル
DE19803454B4 (de) * 1998-01-30 2018-11-29 Scintilla Ag Handgeführte Schlagbohrmaschine mit einer Arretiervorrichtung
US6223833B1 (en) * 1999-06-03 2001-05-01 One World Technologies, Inc. Spindle lock and chipping mechanism for hammer drill
DE19942271C2 (de) † 1999-09-04 2002-01-31 Metabowerke Kg Elektrowerkzeug mit einem Klemmgesperre und einer Sicherheitskupplung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0211933A1 *

Also Published As

Publication number Publication date
EP1307313B1 (fr) 2007-08-01
EP1307313B2 (fr) 2009-08-19
CN1446139A (zh) 2003-10-01
DE50112797D1 (de) 2007-09-13
WO2002011933A1 (fr) 2002-02-14
US6793023B2 (en) 2004-09-21
JP2004524168A (ja) 2004-08-12
CN1211176C (zh) 2005-07-20
DE10037808A1 (de) 2002-02-14
US20030173097A1 (en) 2003-09-18

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