EP2236249B1 - Bohrhammer - Google Patents

Bohrhammer Download PDF

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Publication number
EP2236249B1
EP2236249B1 EP10002955.2A EP10002955A EP2236249B1 EP 2236249 B1 EP2236249 B1 EP 2236249B1 EP 10002955 A EP10002955 A EP 10002955A EP 2236249 B1 EP2236249 B1 EP 2236249B1
Authority
EP
European Patent Office
Prior art keywords
gear
torque
hammer drill
cam ring
cam
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.)
Active
Application number
EP10002955.2A
Other languages
German (de)
English (en)
Other versions
EP2236249A2 (fr
EP2236249A3 (fr
Inventor
Yoshitaka Machida
Kiyonobu Yoshikane
Toshiro Hirayama
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.)
Makita Corp
Original Assignee
Makita Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Makita Corp filed Critical Makita Corp
Publication of EP2236249A2 publication Critical patent/EP2236249A2/fr
Publication of EP2236249A3 publication Critical patent/EP2236249A3/fr
Application granted granted Critical
Publication of EP2236249B1 publication Critical patent/EP2236249B1/fr
Active 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
    • 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
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • 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
    • B25D2216/0015—Tools having a percussion-only mode
    • 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
    • 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
    • B25D2216/0038—Tools having a rotation-only mode
    • 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
    • B25D2250/165—Overload clutches, torque limiters

Definitions

  • This invention relates to a hammer drill as per the preamble of claim 1, which can impart a rotation and/or an impact to a bit at a front end of the hammer drill.
  • a tool holder having a bit-installable front end and functioning as a final output shaft is rotatably supported at a front side of a housing, and at a rear side of the tool holder in the housing there is provided an impact mechanism configured to indirectly impact a bit through an interjacent element by a reciprocating movement of an impactor.
  • An intermediate shaft to which a rotation is transmitted from an output shaft of a motor is disposed in the housing below the impact mechanism and parallel to the tool holder.
  • the intermediate shaft is rotatably supported, and a gear on the intermediate shaft is in mesh with a gear on the tool holder so that a rotation of the intermediate shaft can be transmitted to the tool holder.
  • a torque limiter is provided on the tool holder.
  • the torque limiter uncouples a torque transmission from the intermediate shaft when a mechanical overload or a torque exceeding a setting torque is applied to the tool holder.
  • the torque limiter comprises a rotatable and axially movable gear fitted on the tool holder, a coil spring for urging the gear toward a cam ring fixed to the tool holder, and rollers positioned between the gear and cam ring and engageable with opposite surfaces thereof.
  • the torque limiter operates such that when a torque applied to the tool holder does not exceed the setting torque, a rotation of the gear is constrained so that the torque is transmitted to the cam ring and the tool holder, whereas when the torque applied to the tool holder exceeds the setting torque because of a rotation load to the bit, the gear advances forward against the urging force of the coil spring and slips to thereby uncouple the torque transmission to the cam ring.
  • Patent Document 1 U.S. Patent No. 5,373,905
  • a torque limiter comprises: a cam ring adjacent to a gear, and configured to be provided onto a final output shaft so as to be unitarily rotatable with the final output shaft and to have cam projections on a surface facing to the gear; rolling elements received in corresponding through-holes formed in the gear at positions concentrically with the cam projections, and engageable with the cam projections in their rotational directions; and urging means configured to urge the rolling elements toward the cam ring so that when a torque applied to the final output shaft does not exceed a setting torque, the rolling elements are engaged with the cam projections, and when the torque exceeds the setting torque, the rolling elements pass the cam projections within the through-holes against the urging means and roll on the cam ring, so that the gear slips on the cam ring to thereby uncouple the torque transmission to the cam ring.
  • the rolling elements are rollers and an axis of each roller lies in conformity with a radial direction of the gear.
  • the contacting area between the rolling element and the cam ring can be increased by the use of the rollers, when compared with the use of balls. This can enhance the reliability of the engagement between the cam projections and the rolling elements, as well as restrict a load applied to the cam projections to thereby improve the durability of the cam ring.
  • a hammer drill 1 includes a gear housing 2 in which a rotation mechanism and an impact mechanism are accommodated, a motor housing 3 at the rear of the gear housing 2 (at a right-hand side of FIG. 1 ) and configured to accommodate a motor 4, and a tool holder 6 as a final output shaft which is rotatably supported in the gear housing 2 at a front side of the gear housing 2 and to which a bit can be installed at the front end thereof.
  • the tool holder 6 is a tubular member having an intermediate portion 8 which is rotatably supported at a front end of the gear housing 2 through a ball bearing 10, and a rear portion 9 which is rotatably supported in an inner housing 11 assembled with the gear housing 2 at a rear side of the gear housing 2.
  • a manipulation sleeve 12 for attachment or detachment of a bit (not shown) to be inserted into the front end of the tool holder 6 is provided at a front end portion 7 of the tool holder 6 protruding from the gear housing 2.
  • a gear 13 is rotatably provided onto the tool holder 6 at a periphery of the rear portion 9, and at a front side of the gear 13, a cam ring 14 is unitarily provided onto the tool holder 6 through stopper balls 15.
  • a washer 16 and a coil spring 17 are provided onto the tool holder 6 at a rear side of the gear 13.
  • cam projections 18 protrude from a rear surface (i.e., surface facing to the gear 13) of the cam ring 14 at positions proximate to the peripheral edge of the cam ring 14.
  • the six cam projections 18 are equidistantly arranged around a peripheral direction of the cam ring 14.
  • Each cam projection 18 has slant surfaces extending in a front-back direction along the peripheral direction of the cam ring 14 as seen in the rotating direction of the cam ring 14.
  • the gear 13 has an annular projection 19 at a front surface (i.e., surface facing to the cam ring 14) thereof.
  • the annular projection 19 contacts with the rear surface of the cam ring 14 at an inner side of the cam projections 18, and the annular projection 19 has a height that is slightly greater than that of the cam projection 18.
  • six through-holes 20 are formed in the gear 13 at positions concentrically with the cam projections 18, and the arrangement of the six through-holes 20 conforms to that of the six cam projections 18 (i.e., the cam projections 18 and the through-holes 20 are in phase with each other).
  • a roller 21 is received in each through-hole 20, and an axis of rotation of the roller 21 lies in conformity with a radial direction of the gear 13.
  • the washer 16 has a diameter sufficient to cover the through-holes 20 of the gear 13 from the rear side of the gear 13.
  • the washer 16 is urged forward by the coil spring 17 and pushes the gear 13.
  • the washer 16 and the coil spring 17 correspond to the urging means according to the present invention.
  • Reference numeral 22 indicates a bearing which is retained in the inner housing 11 and supports the rear portion 9 while allowing a rotation of the rear portion 9.
  • Reference numeral 23 indicates a spring retainer which is provided onto the rear portion 9 between the bearing 22 and the coil spring 17 for receiving the rear end of the coil spring 17.
  • An impact bolt (interjacent element) 30 is received in and reciprocates within the intermediate portion 8 of the tool holder 6.
  • the retreating position (rear end position) of the impact bolt 30 is defined by an elastic ring 32 and a retaining ring 33, which are positioned by a tubular cap 31 assembled in the intermediate portion 8 at a rear side of the impact bolt 30.
  • An O-ring 34 is received at the rear end of the cap 31.
  • the rear end of the impact bolt 30 is engageable with the O-ring 34 to restrict the reciprocating movement of a striker 37 to be described later.
  • the O-ring 34 holds the front end of the striker 37 and restricts the reciprocating movement of the striker 37.
  • a tubular piston cylinder 35 which opens toward the front is loosely fitted into the rear portion 9 of the tool holder 6, and the striker (impactor) 37 is accommodated in the piston cylinder 35 through an air chamber 36 so as to reciprocate in the front-back direction.
  • An intermediate shaft 38 is rotatably supported in the gear housing 2 below the output shaft 5 of the motor 4.
  • the intermediate shaft 38 is disposed parallel to the tool holder 6 and the output shaft 5, and a first gear 39 provided at the rear end of the intermediate shaft 38 is in mesh with the output shaft 5.
  • a spline gear 40 is formed on the intermediate portion of the intermediate shaft 38.
  • a second gear 41 is separately and rotatably provided onto the intermediate shaft 38 at the front of the spline gear 40, and the second gear 41 is in mesh with the gear 13 of the tool holder 6.
  • a boss sleeve 42 is separately and rotatably provided onto the intermediate shaft 38 at the rear of the spline gear 40, and a swash bearing 43 is rotatably provided onto the outer periphery of the boss sleeve 42.
  • a connecting arm 44 is connected to the boss sleeve 42 via the swash bearing 43 with its axis inclined. The upper end of the connecting arm 44 protruding upward from the swash bearing 43 is rotatably connected to the rear end of the piston cylinder 35.
  • a sleeve-shaped clutch 45 in which a V-shaped fitting groove 46 is formed around a peripheral surface thereof, is provided on the spline gear 40 of the intermediate shaft 38.
  • the clutch 45 is splined to the intermediate shaft 38 so as to be unitarily rotatable with the intermediate shaft 38 and slidable along the intermediate shaft 38 in the front-back direction.
  • a mode-selecting knob 47 is rotatably mounted below the clutch 45 and at the lower surface of the gear housing 2, and an engagement pin 48 having a tapered upper end to be fitted into the fitting groove 46 of the clutch 45 is eccentrically provided on the upper surface of the mode-selecting knob 47.
  • the engagement pin 48 is retained on the mode-selecting knob 47 in such a manner that it is movable in the vertical direction while being urged upward by a coil spring 49.
  • the engagement pin 48 undergoes an eccentric motion while being fitted into the fitting groove 46, so that the clutch 45 moves in the front-back direction in accordance with the travel distance of the engagement pin 48 in the front-back direction. According to the sliding position of the clutch 45, the clutch 45 is brought into engagement with either one of or both of the second gear 41 and the boss sleeve 42.
  • the clutch 45 in an advanced position of the clutch 45, the clutch 45 merely engages with the second gear 41 to allow a unitary rotation of the second gear 41 and the intermediate shaft 38 in their rotational direction (i.e., drill mode). In a retreating position of the clutch 45, the clutch 45 merely engages with the boss sleeve 42 to allow a unitary rotation of the boss sleeve 42 and the intermediate shaft 38 (i.e., hammer mode). In an intermediate position of the clutch 45, the clutch 45 engages with both the second gear 41 and the boss sleeve 42 to allow a unitary rotation of the second gear 41 and the boss sleeve 42 with the intermediate shaft 38 in their rotational direction (i.e., hammer drill mode). Therefore, various modes of operation can be selected in accordance with the sliding positions of the clutch 45.
  • the torque limiter operates so that the rollers 21 ride on the cam projections 18 of the cam ring 14 and pass the cam projections 18. Because the rollers 21 roll on the cam ring 14 and the gear 13 slips on the cam ring 14, the mechanical coupling between the cam ring 14 and the gear 13 is uncoupled. Therefore, the torque transmission from the gear 13 to the cam ring 14 and the tool holder 6 is disconnected.
  • the gear 13 does not move in the axial direction during operation/non-operation of the torque limiter and only the rotation of the gear 13 is permitted, so that the teeth at regions where the gear 13 and the second gear 41 mesh with each other are less likely to subject to wear.
  • the torque limiter includes: the cam ring 14 adjacent to the gear 13, and configured to be provided onto the tool holder 6 so as to be unitarily rotatable with the tool holder 6 and to have cam projections 18 on the surface facing to the gear 13; rollers 21 received in the corresponding through-holes 20 formed in the gear 13 at positions concentrically with the cam projections 18, and engageable with the cam projections 18 in their rotational directions; and the urging means (the washer 16 and the coil spring 17) configured to urge the rollers 21 toward the cam ring 14 so that when the torque applied to the tool holder 6 does not exceed the setting torque, the rollers 21 are brought into engagement with the cam projections 18; and when the torque applied to the tool holder 6 exceeds the setting torque, the rollers 21 pass the cam projections 18 within the through-holes 20 against the urging means and roll on the cam ring 14, so that the gear 13 slips on the cam ring 14 to thereby uncouple the torque transmission to the
  • the rolling elements are rollers 21 and an axis of each roller 21 lies in conformity with the radial direction of the gear 13. Therefore, the contacting area between the rolling element and the cam ring 14 can be increased by the use of the rollers 21, when compared with the use of balls. This can enhance the reliability of the engagement between the cam projections 18 and the rolling elements, as well as restrict a load applied to the cam projections 18 to thereby improve the durability of the cam ring 14.
  • the number of cam projections 18 of the cam ring 14 and the number of through-holes 20 of the gear 13 may vary where necessary, and the number of rollers 21 may vary in accordance with the number of the through-holes 20.
  • the rolling elements are not limited to the rollers 21, and balls may be employed instead.
  • a resilient member such as a coned disc spring may be employed as the urging means in place of the coil spring.
  • the direction of the torque limiter is not limited to that disclosed in the above embodiment, and it is possible to change the arrangement such that the cam ring 14 is disposed rearward of the gear 13 and the washer 16 and the resilient member are disposed forward of the gear 13.
  • the design of the hammer drill may also vary where necessary.
  • the impact mechanism may be configured such that a piston reciprocates in a stationary cylinder so as to cause an impactor to reciprocate in synchronization with the piston.
  • the impactor may directly strike the bit without employing an interjacent element.
  • a crank mechanism may be employed for the reciprocating motion of the piston.
  • other modifications may be made where necessary.

Landscapes

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

Claims (11)

  1. Marteau perforateur (1) comprenant :
    un logement (2) ;
    un arbre de sortie finale supporté, de manière à pouvoir tourner, dans le logement (2) et apte à avoir un foret qui lui est attaché ;
    un mécanisme de rotation disposé dans le logement (2) et configuré pour transmettre un couple à un engrenage (13) qui est fourni, de manière à pouvoir tourner, sur l'arbre de sortie finale ;
    un mécanisme de percussion disposé dans le logement (2) et configuré pour frapper le foret ; et
    un limiteur de couple fourni sur l'arbre de sortie finale et configuré de sorte que, lorsqu'un couple appliqué à l'arbre de sortie finale ne dépasse pas un couple de consigne, une rotation de l'engrenage (13) est limitée afin de permettre la transmission du couple à l'arbre de sortie finale, tandis que, lorsque le couple appliqué à l'arbre de sortie finale dépasse le couple de consigne, l'engrenage (13) glisse pour de ce fait découpler la transmission de couple à l'arbre de sortie finale,
    dans lequel le limiteur de couple comprend :
    un anneau à cames (14) adjacent à l'engrenage (13), et
    configuré pour être fourni sur l'arbre de sortie finale de manière à pouvoir tourner de manière unitaire avec l'arbre de sortie finale et pour avoir des saillies de cames (18) sur une surface faisant face à l'engrenage (13) ;
    des éléments de roulement reçus dans des trous traversants (20) correspondants formés dans l'engrenage (13) à des positions concentriques aux saillies de cames (18), et pouvant se mettre en prise avec les saillies de cames (18) dans leur sens de rotation, et
    des moyens de poussée configurés pour pousser les éléments de roulement vers l'anneau à cames (14) de sorte que, lorsque le couple ne dépasse pas le couple de consigne, les éléments de roulement sont mis en prise avec les saillies de cames (18),
    dans lequel, lorsque le couple dépasse le couple de consigne, les éléments de roulement passent les saillies de cames (18) à l'intérieur des trous traversants (20) contre les moyens de poussée et
    roulent sur l'anneau à cames (14), de sorte que l'engrenage (13) glisse sur l'anneau à cames (14) pour découpler de ce fait la transmission de couple de l'anneau à cames (14), caractérisé en ce que les éléments de roulement sont des rouleaux (21) et un axe de chaque rouleau (21) repose en conformité avec un sens radial de l'engrenage (13).
  2. Marteau perforateur (1) selon la revendication 1, dans lequel les moyens de poussée comprennent une rondelle (16) adjacente à l'engrenage (13) et ayant un diamètre pour couvrir les trous traversants (20) et un ressort hélicoïdal (17) poussant la rondelle (16) vers l'engrenage (13).
  3. Marteau perforateur (1) selon la revendication 1 ou 2, dans lequel l'engrenage (13) a une saillie annulaire à une surface faisant face à l'anneau à cames (14), la saillie annulaire étant configurée pour être en contact avec l'anneau à cames (14) à un côté intérieur des saillies de cames (18) et pour avoir une hauteur supérieure à celle de la saillie de cames (18).
  4. Marteau perforateur (1) selon l'une des revendications 1 à 3, dans lequel chacune des saillies de cames (18) a des surfaces inclinées s'étendant dans un sens de l'avant à l'arrière le long d'un sens périphérique de l'anneau à cames (14).
  5. Marteau perforateur (1) selon l'une des revendications 1 à 4, dans lequel le nombre de trous traversants (20) fournis est égal au nombre de saillies de cames (18), et les saillies de cames (18) et les trous traversants (20) sont en phase l'un avec l'autre.
  6. Marteau perforateur (1) selon l'une des revendications 1 à 5, dans lequel l'arbre de sortie finale est un porte-outil tubulaire (6) comportant une extrémité avant à laquelle un foret peut être installé.
  7. Marteau perforateur (1) selon la revendication 6, dans lequel l'anneau à cames (14) est fourni sur le porte-outil (6) à travers des billes de butée (15) fournies entre l'anneau à cames (14) et le porte-outil (6).
  8. Marteau perforateur (1) selon la revendication 6 ou 7, dans lequel le mécanisme de rotation est supporté, de manière à pouvoir tourner, dans le logement (2), parallèlement au porte-outil (6), et le mécanisme de rotation comprend un arbre intermédiaire (38) comportant un premier engrenage (39) à un côté arrière de celui-ci qui s'engrène avec un arbre de sortie d'un moteur et un deuxième engrenage (41) à un côté avant de celui-ci qui s'engrène avec l'engrenage.
  9. Marteau perforateur (1) selon la revendication 8, dans lequel le mécanisme de percussion comprend : un boulon de percussion (30) reçu dans le porte-outil (6) à l'arrière du foret, un cylindre de piston tubulaire (35) inséré dans le porte-outil (6) à partir d'un côté arrière du boulon de percussion (30) et dans lequel un percuteur (37) est agencé à travers une chambre à air ; un bras de liaison (44) relié à une extrémité arrière du cylindre de piston (35) ; et un manchon de bossage (42) fourni sur l'arbre intermédiaire (38) et sur lequel l'arbre de liaison (44) est positionné par l'intermédiaire d'un palier en biais (43) dans un état dans lequel un axe du bras de liaison (44) est incliné.
  10. Marteau perforateur (1) selon la revendication 9, dans lequel un embrayage (45) est cannelé sur l'arbre intermédiaire (38) entre le deuxième engrenage (41) et le manchon de bossage (42), et dans lequel trois modes de fonctionnement peuvent être sélectionnés par un mouvement coulissant de l'embrayage (45), comprenant un mode de perforation dans lequel l'embrayage (45) se met simplement en prise avec le deuxième engrenage (41) pour permettre une rotation unitaire du deuxième engrenage (41) et de l'arbre intermédiaire (38), un mode de marteau dans lequel l'embrayage (45) se met simplement en prise avec le manchon de bossage (42) pour permettre une rotation unitaire du manchon de bossage (42) et de l'arbre intermédiaire (38), et un mode de marteau perforateur dans lequel l'embrayage (45) se met en prise à la fois avec le deuxième engrenage (41) et le manchon de bossage (42) pour permettre une rotation unitaire du deuxième engrenage (41) et du manchon de bossage (42) avec l'arbre intermédiaire (38).
  11. Marteau perforateur (1) selon la revendication 10, dans lequel une gorge de montage en forme de V est formée autour d'une surface périphérique de l'embrayage (45), et une tige de mise en prise (48) fournie de manière excentrique sur un bouton de sélection de mode (47) est montée dans la gorge de montage, de sorte que l'embrayage (45) soit glissé le long de l'arbre intermédiaire (38) par un mouvement excentrique de la tige de mise en prise (48) sous l'effet d'une rotation du bouton de sélection de mode (47).
EP10002955.2A 2009-04-01 2010-03-19 Bohrhammer Active EP2236249B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009089461A JP5431000B2 (ja) 2009-04-01 2009-04-01 ハンマードリル

Publications (3)

Publication Number Publication Date
EP2236249A2 EP2236249A2 (fr) 2010-10-06
EP2236249A3 EP2236249A3 (fr) 2011-12-28
EP2236249B1 true EP2236249B1 (fr) 2015-09-09

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Family Applications (1)

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EP10002955.2A Active EP2236249B1 (fr) 2009-04-01 2010-03-19 Bohrhammer

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EP (1) EP2236249B1 (fr)
JP (1) JP5431000B2 (fr)
CN (1) CN101856733B (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012223844A (ja) * 2011-04-18 2012-11-15 Makita Corp ハンマドリル
JP6378989B2 (ja) * 2014-09-22 2018-08-22 株式会社マキタ ハンマドリル
CN108031895B (zh) * 2017-12-18 2018-11-20 绍兴伊司特家具有限公司 一种新型的弧形钻孔设备
JP7331864B2 (ja) * 2018-11-29 2023-08-23 工機ホールディングス株式会社 打撃作業機
CN112112878B (zh) * 2019-06-19 2024-12-13 博世电动工具（中国）有限公司 垫片装置、活塞组件和电动工具

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5997850A (ja) * 1982-11-26 1984-06-05 有限会社　新城製作所 電動回転工具のアタツチメント
DE4215288A1 (de) * 1991-07-08 1993-01-14 Bosch Gmbh Robert Bohrhammer
JP3450558B2 (ja) * 1995-12-25 2003-09-29 株式会社マキタ 電動工具
DE19707588B4 (de) * 1997-02-26 2005-08-18 Robert Bosch Gmbh Werkzeugmaschine, insbesondere Bohr- bzw. Schlagbohrmaschine oder Bohrhammer
GB2392966B (en) * 2002-09-13 2006-05-31 Black & Decker Inc Rotary tool with overload clutch
JP3976187B2 (ja) * 2002-11-20 2007-09-12 株式会社マキタ ハンマードリル
JP4515181B2 (ja) * 2004-07-20 2010-07-28 株式会社マキタ 電動ハンマドリル
JP5015653B2 (ja) * 2007-05-01 2012-08-29 株式会社マキタ ハンマードリル
JP5128391B2 (ja) * 2008-07-03 2013-01-23 株式会社マキタ ハンマードリル

Also Published As

Publication number Publication date
CN101856733B (zh) 2012-08-22
EP2236249A2 (fr) 2010-10-06
JP2010240759A (ja) 2010-10-28
JP5431000B2 (ja) 2014-03-05
CN101856733A (zh) 2010-10-13
EP2236249A3 (fr) 2011-12-28

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