EP2473320A1 - Dispositif à marteau perforateur et/ou à marteau burineur - Google Patents

Dispositif à marteau perforateur et/ou à marteau burineur

Info

Publication number
EP2473320A1
EP2473320A1 EP10732989A EP10732989A EP2473320A1 EP 2473320 A1 EP2473320 A1 EP 2473320A1 EP 10732989 A EP10732989 A EP 10732989A EP 10732989 A EP10732989 A EP 10732989A EP 2473320 A1 EP2473320 A1 EP 2473320A1
Authority
EP
European Patent Office
Prior art keywords
hammer
planetary gear
gear
drilling
drive
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Withdrawn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
EP10732989A
Other languages
German (de)
English (en)
Inventor
Christian Wiedemann
Achim Duesselberg
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2473320A1 publication Critical patent/EP2473320A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • 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
    • B25D2211/003—Crossed drill and motor spindles
    • 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

  • a hammer and chisel hammer device with a hammer mechanism and a gear unit for transmitting a drive torque from an electric motor to the hammer impact mechanism.
  • the gear unit has mutually engaging spur gears.
  • a hammer and / or chisel hammer with a hammer mechanism which has a drive unit, and a transmission unit for transmitting a drive torque from a motor to the hammer mechanism, wherein the transmission unit comprises at least one planetary gear and a drive element of the drive unit to a transmission element of the planetary gear is arranged, proposed.
  • a "hammer blower” in particular a striking mechanism with racket, which can be accelerated over a distance in the direction of impact before it impinges on a component to trigger a shock pulse, such as preferably a pneumatic percussion, in which a racket from a piston over a mechanical impact mechanism, in which a racket can be accelerated by a mechanical arrangement, such as in particular a spring arm, is to be understood in particular as meaning a transmission which has at least one planet connected to a planetary carrier in the radial direction outwards with a ring gear and / or in the radial direction inwardly coupled to a sun gear and thus in particular has a plurality of coaxial shafts.
  • the sun wheel, the planet and / or the ring gear may be formed by round gears or by matched non-circular gears. It can be connected in series one behind the other planetary gear and / or it can be interposed between the planet and ring gear several stages.
  • the drive unit can be formed by various units that appear appropriate to a person skilled in the art, such as a swash bearing unit in which a swash element is mounted in a bearing plane that is tilted to an axis of rotation by an angle greater than zero, such as in particular by a rolling body track Bearing level, one of a curved path unit formed drive unit and / or particularly advantageous of an eccentric unit, which in particular has an eccentrically arranged drive element, such as in particular an eccentrically arranged drive pin.
  • the drive unit is used in particular to convert a rotational movement into an axial impact movement.
  • "arranged on a gear element" in this context is to be understood in particular that the drive element, in particular a bearing element with a tilted bearing track of a swash bearing unit or particularly advantageous an eccentric bolt of an eccentric unit is firmly connected to a transmission element of the planetary gear, in particular with a ring gear, a planet carrier and / or with a planet of the planetary gear.
  • an advantageous gear ratio can be achieved with a particularly space-saving design, in particular if the planetary gear has an input element, in particular a sun gear, whose axis of rotation is at least substantially coaxial to a rotational axis of a drive element of the hammer impact mechanism is.
  • substantially coaxial is to be understood in particular as meaning that the shafts enclose an angle of less than 30 ° and preferably less than 10.
  • an "input element” should be understood to mean, in particular, an element via which a torque is introduced into the gear unit and the latter Rotation axis is arranged in particular coaxially to a rotation axis of the motor.
  • the gear unit can be advantageously designed as a preassemblable assembly and it can reach a low load on a motor shaft and the Motor shaft can be made with a smaller diameter, whereby the motor is smaller executable.
  • an axis of rotation of the planetary gear and a striking axis of the hammer percussion include an angle other than zero, i. have a different orientation from a parallel or coaxial orientation, which in particular larger motors can be integrated advantageously, in particular when the axis of rotation of the planetary gear and the striking axis of the hammer impact mechanism, in which a shock pulse is transmitted in operation, an angle greater than 10 ° and preferably greater than 20 °.
  • an L-shape can be achieved in which the axis of rotation of the planetary gear and the striking axis of the hammer impact mechanism at least substantially, i. with an error of less than 10 ° and preferably less than 5 °, enclose an angle of 90 °.
  • At least one transmission element of the planetary gear unit is formed integrally with a drive element of the hammer impact mechanism, in particular with an eccentric element and / or a swash bearing element, additional components, installation space, weight, assembly costs and costs can be saved.
  • integral piece should be understood to mean, in particular, a cast, but in principle also a multi-part design is conceivable in which parts are connected by means of a riveted, welded and / or brazed joint, etc.
  • the drilling and / or chiseling device has at least one latching coupling, whereby undesirably high torques can advantageously be avoided.
  • the lock-up clutch is arranged in the power flow between a planet carrier and an element of the gear unit and / or between a ring gear and an element of the gear unit, whereby the Kochrastkupplung can be integrated advantageously simple and space-saving.
  • the planetary gear has at least one sealing means which is provided for sealing a planetary gear internal space, an advantageously central lubrication can be achieved.
  • a "sealant" is to be understood in particular as a means which is specifically intended for sealing, such as in particular a sealing ring, a labyrinth seal, a rubber-like sealant, etc.
  • a ring gear and a planet carrier of the planetary gear are connected via a bearing connection, i. the particular at least one ring gear on a
  • Planet carrier is mounted so that bearing forces of the ring gear are supported by the planet carrier, and / or at least one planet carrier is mounted via a ring gear, so that bearing forces of the planet carrier are supported via the ring gear.
  • the transmission element of the planetary gear, on which the drive element is arranged is driven in at least one operating mode with a superimposed rotational movement, so that the drive element performs a linear movement along a striking axis of the hammer impact mechanism.
  • the drive element can advantageously be connected directly to a piston of the hammer impact mechanism.
  • Be planetary gear with a superimposed rotary motion acted on but particularly advantageous simple is a corresponding embodiment achievable when the transmission element is formed by a planet, and the drive element of the drive unit is arranged on a planet of the planetary gear.
  • FIG. 2 shows a detail of the schematically illustrated drill and chisel hammer device from FIG. 1, FIG.
  • FIG. 3 shows a detail of an alternative, schematically illustrated drill and chipping apparatus with two planetary gears connected in series
  • FIG. 4 shows a detail of an alternative, schematically illustrated drill and chipping device with an alternative starting element
  • FIG. 5 shows a detail of a further alternative drilling and chiseling device in a perspective view with partial sections
  • FIG. 6 is a bottom view of the drilling and chipping apparatus of FIG. 5;
  • FIG. 7 shows a section through the drilling and chipping device along the line VII-VII in FIG. 6 and FIG
  • Fig. 8 is a view of the drilling and chipping apparatus of Figure 5 from above with a partial section.
  • FIG. 1 shows a drill and chisel hammer with a drill and chisel device arranged in a housing 54a.
  • a main handle 58a formed by a strap handle is fastened, and an auxiliary handle 60a formed by a handle handle is fastened on a side facing the tool holder 56a.
  • the hammer and chisel device has a hammer percussion device 10a, which comprises a hammer tube 62a, a piston 34a guided in the hammer tube 62a, and a piston which can be driven by the piston via a gas cushion 36a
  • Racket 38a which in operation via an anvil 66a on an insert tool 64a acts includes.
  • the hammer mechanism 10a comprises a drive unit with a drive element 28a formed by an eccentric element, which is intended to translate a rotational movement into an axial stroke movement and thus to drive the piston 34a in the axial direction of the hammer tube 62a (FIGS. 1 and 2).
  • the drilling and chiseling hammer device comprises a gear unit 12a for transmitting a drive torque from an electric motor 14a arranged in the housing 54a to the hammer impact mechanism 10a or to the drive element 28a.
  • the gear unit 12a has a planetary gear 16a.
  • the planetary gear 16a has an input member 20a formed by a sun gear whose rotation axis 24a is disposed coaxially with a rotation axis 26a of the drive member 28a of the hammer impact mechanism 10a.
  • the sun gear is formed integrally with a motor shaft of the electric motor 14a.
  • the rotation axis 24a of the planetary gear or the sun gear is coaxial with one
  • Rotary axis of the electric motor 14a arranged.
  • the rotation axis 24a and a striking axis 30a of the hammer impactor 10a include an angle 32a of 90 °. In principle, however, other angles are conceivable.
  • a ring gear 42a of the planetary gear 16a forms an output element of the gear unit 12a.
  • the drive element 28a is arranged on the ring gear 42a, specifically the ring gear 42a is formed integrally with the drive element 28a (FIG. 2).
  • Formed on an outer circumference of the ring gear 42a is a gear 68a provided to transmit rotational motion from the ring gear 42a to the hammer tube 62a in a drilling operation.
  • the ring gear 42a is rotatable on one by means of a bearing connection 69a formed by a roller bearing 70a
  • Planet carrier 46a of the planetary gear 16a mounted wherein the rolling surfaces of the rolling bearing 70a are integrally formed on the planet carrier 46a and the ring gear 42a and the planet carrier 46a and the ring gear 42a form rolling surfaces for balls 72a of the rolling bearing 70a.
  • balls instead of balls, in principle, other rolling elements appearing appropriate to the person skilled in the art are also conceivable.
  • Planet carrier 46a carries a plurality of planets 74a, which mesh radially inwardly with the sun gear and the input member 20a of the planetary gear 16a and radially outwardly mesh with an internal toothing 76a of the ring gear 42a.
  • the planetary carrier 46a is supported in a housing element 48a of the gear unit 12a via a latching coupling 44a of the drill and chisel device.
  • the lockup clutch 44a has Studentsrastkugeln 78a, which are slidably mounted in radial recesses 80a of the planet carrier 46a against an annular spring 82a and engage in the radial direction outwardly into a detent contour 84a, which is integrally formed on an inner periphery of the ring gear 42a. If, in operation, a torque to be transmitted by the ring gear 42a is below a certain lockup torque, the planet carrier 46a is held in the housing element 48a in a rotationally fixed manner by means of the lockup clutch 44a and torque can be transmitted from the ring gear 42a to the hammer driver 10a and / or to the hammer tube 62a become.
  • the latching balls 78a are deflected inward in the radial direction against a spring force of the annular spring 82a, and the planet carrier 46a rotates in the housing element 48a.
  • the planet carrier 46a could also be made in one piece with the housing element 48a.
  • To achieve an advantageous lubrication is a planetary gear interior
  • FIG. 52a in which in particular the planet 74a are arranged, filled with lubricant.
  • the planetary gear internal space 52a is sealed by means of a sealed needle bearing 86a between the input element 20a and the planetary carrier 46a and by means of a sealant 50a formed by a sliding seal.
  • the annular sealing means 50a is fastened with its radially inner region to the planet carrier 46a and lies with its radially outer region, loaded by an internal clamping force, on an end face of the ring gear 42a.
  • Figures 3 and 4 show sections of alternative embodiments.
  • FIG. 2 shows a section of an alternative, schematically illustrated drill and chisel device, which has a gear unit 12b with two planetary gears 16b, 18b connected in series.
  • the planetary gear 16b has a non-rotatably coupled to an electric motor not shown, formed by a sun gear input member 20b and a ring gear 88b.
  • the ring gear 88b of the planetary gear 16b is rotatably coupled to an input member 22b of the second planetary gear 18b.
  • the input elements 20b, 22b have a common axis of rotation 24b.
  • the second planetary gear 18b has a ring gear 42b, which forms an output element of the gear unit 12b and is integrally formed with a drive element 28b of a hammer impact mechanism 10b.
  • FIG. 4 shows a drilling and chiseling device of a drill and chisel hammer with a gear unit 12c, which has a planetary gear 16c.
  • the planetary gear 16c has an input member 20c formed by a sun gear, the rotation axis 24c of which is disposed coaxially with a rotation axis 26c of a drive unit 28c of the drive unit of a hammer impact mechanism 10c.
  • Sun gear integral motor shaft are mounted by means of a needle bearing 86c in a ring gear 42c of the planetary gear 16c.
  • the sun gear and / or the motor shaft could be mounted in a planet carrier 40c of the planetary gear 16c.
  • the planetary carrier 40c of the planetary gear 16c constitutes an output element of the transmission unit 12c.
  • the drive element 28 c is on the
  • Planet carrier 40 c arranged, that is, the planet carrier 40 c is integrally formed with the drive member 28 c.
  • the planetary carrier 40c could be connected to a toothed wheel or a toothed wheel could be formed on the planet carrier 40c.
  • the planet carrier 40c is rotatably supported in the ring gear 42c of the planetary gear 16c by means of a bearing 70c.
  • the planetary carrier 40c carries a plurality of planets 74c which mesh radially inwardly with the sun gear and the input member 20c of the planetary gear 16c, respectively, and mesh radially outward with an internal gear 76c of the ring gear 42c.
  • the planets 74c are each mounted rotatably on axles which are rotatably mounted in the planet carrier 40c via a bearing 90c.
  • the planets 74c could also be rotatably mounted on the axles and the axles could be rotationally fixed in the planet carrier 40c.
  • the planetary gear 16c is filled with lubricant and the bearings 70c, 86c, 90c are sealed.
  • the ring gear 42c is rotatably disposed in a housing, not shown, a drill and chisel hammer.
  • the ring gear 42c could be mounted via a Studentsrastkupplung in the housing of the drill and chisel hammer and / or it could be a Studentsrastkupplung between the planet carrier 40c and the hammer tube.
  • FIG. 5 shows a drill and chisel hammer device of a drill and chisel hammer with a gear unit 12d, which has a planetary gear 16d.
  • the planetary gear 16d has an input element 20d formed by a sun gear whose rotation axis 24d is arranged coaxially with a rotation axis 26d of a drive unit or drive element 28d of the drive unit of a hammer impact mechanism 10d.
  • the planetary gear 16d has a rotatably mounted planetary carrier 40d on which three planets 74d are rotatably mounted on a side facing the sun gear.
  • the planetary gear 74d mesh radially inward with the sun gear and radially outward with a ring gear 42d of the planetary gear 16d fixed non-rotatably in a housing, not shown.
  • the planet carrier 40d of the planetary gear 16d has an output element 92d on a side facing away from the sun gear.
  • the output element 92d is arranged eccentrically to the rotation axis 24d.
  • the driven element 92d is formed by a bolt formed integrally with the planet carrier 40d.
  • a planet 75d of the planetary gear 16d is rotatably mounted, which meshes in the radial direction outwardly with the ring gear 42d.
  • the drive element 28d is arranged on the planet 75d on a side facing away from the planet carrier 40d.
  • the drive element 28d is arranged eccentrically to a rotation axis 94d of the planet 75d, about which the planet 75d is rotatably mounted on the output element 92d.
  • the planet 75d, on which the drive element 28d is arranged, is driven in operation with a superimposed rotational movement, so that the drive element 28d performs a linear movement along a striking axis 30d.
  • the drive member 28d has a longitudinal axis 96d which extends through a pitch circle 98d of the planet 74d and parallel to the rotational axis 94d of the planet 75d.
  • the pitch circle 98d has a diameter that is half the diameter of a pitch circle diameter of a pitch circle 100d of the ring gear 42d in which the planetary gear 75d can roll.
  • the planetary carrier 40d could be connected to a toothed wheel or a toothed wheel could be molded onto the planet carrier 40d.
  • the ring gear 42d could be mounted in the housing of the drill and chisel hammer via a latching coupling and / or there could be a latching coupling between the planet carrier 40d and the planetary carrier 40d

Landscapes

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

Abstract

L'invention concerne un dispositif à marteau perforateur et/ou à marteau burineur muni d'un mécanisme de percussion (10a; 10b; 10c; 10d), présentant une unité d'entraînement, et d'une unité de transmission (12a; 12b; 12c; 12d) destinée à transmettre un couple d'entraînement d'un moteur (14a) au mécanisme de percussion (10a; 10b; 10c; 10d). L'unité de transmission (12a; 12b; 12c; 12d) comprend au moins un train planétaire (16a; 16b, 18b; 16c; 16d), un élément d'entraînement (28a; 28b; 28c; 28d) de l'unité d'entraînement étant agencé sur un élément de transmission du train planétaire (16a; 16b, 18b; 16c; 16d).
EP10732989A 2009-09-01 2010-07-16 Dispositif à marteau perforateur et/ou à marteau burineur Withdrawn EP2473320A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009029055A DE102009029055A1 (de) 2009-09-01 2009-09-01 Bohr- und/oder Meißelhammervorrichtung
PCT/EP2010/060318 WO2011026683A1 (fr) 2009-09-01 2010-07-16 Dispositif à marteau perforateur et/ou à marteau burineur

Publications (1)

Publication Number Publication Date
EP2473320A1 true EP2473320A1 (fr) 2012-07-11

Family

ID=43012698

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10732989A Withdrawn EP2473320A1 (fr) 2009-09-01 2010-07-16 Dispositif à marteau perforateur et/ou à marteau burineur

Country Status (6)

Country Link
US (1) US10183390B2 (fr)
EP (1) EP2473320A1 (fr)
CN (1) CN102481687B (fr)
DE (1) DE102009029055A1 (fr)
RU (1) RU2550469C2 (fr)
WO (1) WO2011026683A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5395620B2 (ja) 2009-11-02 2014-01-22 株式会社マキタ 打撃工具
DE102012212417B4 (de) * 2012-07-16 2017-06-08 Robert Bosch Gmbh Schalteinheit
US9630307B2 (en) * 2012-08-22 2017-04-25 Milwaukee Electric Tool Corporation Rotary hammer
JP6086704B2 (ja) * 2012-11-13 2017-03-01 オリンパス株式会社 レーザアブレーション装置
GB2531995A (en) * 2014-10-20 2016-05-11 Black & Decker Inc Pneumatic hammer
DE102016112051B4 (de) * 2016-06-30 2024-01-04 Interroll Holding Ag Modulsystem für motorbetriebene Förderrollen
WO2019079560A1 (fr) 2017-10-20 2019-04-25 Milwaukee Electric Tool Corporation Outil à percussion
US11059155B2 (en) 2018-01-26 2021-07-13 Milwaukee Electric Tool Corporation Percussion tool
CN110153960B (zh) * 2018-02-14 2024-10-11 苏州宝时得电动工具有限公司 冲击工具
CN109176411B (zh) * 2018-11-13 2024-03-29 久维科技(苏州)有限公司 一种快速紧固装置
US11453109B2 (en) * 2019-01-09 2022-09-27 Makita Corporation Power tool
USD1034128S1 (en) * 2022-02-07 2024-07-09 Robert Bosch Gmbh Hammer drill
EP4302926B1 (fr) 2022-06-16 2025-08-06 Milwaukee Electric Tool Corporation Outil compact à percussion

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004051911A1 (de) * 2004-10-26 2006-04-27 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohrschrauber
EP1955823A1 (fr) * 2007-02-08 2008-08-13 HILTI Aktiengesellschaft Machine-outil manuelle dotée d'une sonnette pneumatique

Family Cites Families (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2342540A (en) * 1939-10-12 1944-02-22 Jesse W Hale Coupling device
US3022683A (en) * 1959-03-30 1962-02-27 Int Harvester Co Transmission for vehicles
US4034833A (en) * 1974-07-22 1977-07-12 Texas Dynamatics, Inc. Roller clutch
DE2511148C3 (de) * 1975-03-14 1981-08-13 Otto Bilz, Werkzeugfabrik, 7302 Ostfildern Überlastkupplungseinrichtung für Gewindeschneidfutter oder Schnellwechseleinsätze für diese
US4579019A (en) * 1980-04-04 1986-04-01 Darcy Gabriele Method and apparatus for power transmission from an engine
US4460078A (en) * 1981-12-10 1984-07-17 Heide Charles H Torque release clutch
DE3516494A1 (de) * 1985-05-08 1986-11-13 Hilti Ag, Schaan Bohrhammer
US5295925A (en) * 1991-11-22 1994-03-22 Harmonic Drive Systems, Inc. Planetary gear transmission
US5480362A (en) * 1992-09-03 1996-01-02 Honda Giken Kogyo Kabushiki Kaisha Double planetary carrier
RU2099174C1 (ru) * 1995-06-07 1997-12-20 Виталий Тихонович Бойко Переносной ударный инструмент
US6223833B1 (en) * 1999-06-03 2001-05-01 One World Technologies, Inc. Spindle lock and chipping mechanism for hammer drill
DE10033362A1 (de) * 2000-07-08 2002-01-17 Hilti Ag Elektrohandwerkzeug mit Leerschlagabschaltung
DE10034359A1 (de) * 2000-07-14 2002-01-24 Hilti Ag Schlagendes Elektrohandwerkzeuggerät
DE10037418A1 (de) * 2000-07-19 2002-02-07 Hilti Ag Elektrohandwerkzeuggerät mit elektropneumatischem Schlagwerk
US6733414B2 (en) * 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
DE10103141A1 (de) * 2001-01-24 2002-07-25 Hilti Ag Elektrohandwerkzeuggerät mit Leerschlagabschaltung
DE10259931A1 (de) * 2002-12-20 2004-07-01 Ina-Schaeffler Kg Kupplungsanordnung
JP4270887B2 (ja) * 2003-01-10 2009-06-03 株式会社マキタ 電動往復動式工具
JP3963323B2 (ja) * 2003-02-07 2007-08-22 株式会社マキタ 電動工具
SE525188C2 (sv) * 2003-03-03 2004-12-21 Atlas Copco Tools Ab Kraftverktyg med reverseringsväxel omställbar med manöverring
GB2399615B (en) * 2003-03-21 2006-03-15 Black & Decker Inc Vibration reduction apparatus for power tool and power tool incorporating such apparatus
US7004357B2 (en) * 2003-05-15 2006-02-28 Alemite, Llc Grease gun
DE10330180A1 (de) * 2003-07-04 2005-01-27 Robert Bosch Gmbh Handwerkzeugmaschine
JP4527468B2 (ja) * 2004-08-17 2010-08-18 株式会社マキタ 電動工具
DE202004014986U1 (de) * 2004-09-25 2006-02-02 A & M Electric Tools Gmbh Umlaufrädergetriebe
US20060237205A1 (en) * 2005-04-21 2006-10-26 Eastway Fair Company Limited Mode selector mechanism for an impact driver
DE102005019710A1 (de) * 2005-04-28 2006-11-09 Robert Bosch Gmbh Handwerkzeugmaschinenschlagwerkeinheit
US20060289182A1 (en) * 2005-06-28 2006-12-28 Feng-Chun Tsai Gear box of an electrical drill
DE502005004301D1 (de) * 2005-11-18 2008-07-10 Metabowerke Gmbh Elektromotorisch angetriebenes Schraub-oder Bohrwerkzeuggerät mit Planetengetriebe
DE102006020172A1 (de) * 2006-05-02 2007-11-08 Robert Bosch Gmbh Handwerkzeugmaschine
EP1857228B1 (fr) * 2006-05-19 2008-07-09 Black & Decker, Inc. Mécanisme de changement de mode pour un outil motorisé
DE102006045842A1 (de) * 2006-09-27 2008-04-03 Robert Bosch Gmbh Handwerkzeugmaschine
EP1932608B1 (fr) * 2006-12-15 2011-07-06 Black & Decker, Inc. Foreuse/visseuse
JP5030601B2 (ja) * 2007-01-22 2012-09-19 株式会社マキタ 電動工具
US7794355B2 (en) * 2007-05-15 2010-09-14 Snap-On Incorporated Planetary gear set centering ring
CN201053482Y (zh) * 2007-06-14 2008-04-30 北京航空航天大学 连续可变曲柄长度的曲柄摇杆机构
CN102803774B (zh) * 2010-03-15 2016-03-09 Ntn株式会社 离合器单元

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004051911A1 (de) * 2004-10-26 2006-04-27 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohrschrauber
EP1955823A1 (fr) * 2007-02-08 2008-08-13 HILTI Aktiengesellschaft Machine-outil manuelle dotée d'une sonnette pneumatique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2011026683A1 *

Also Published As

Publication number Publication date
WO2011026683A1 (fr) 2011-03-10
US10183390B2 (en) 2019-01-22
RU2550469C2 (ru) 2015-05-10
DE102009029055A1 (de) 2011-03-10
US20120186842A1 (en) 2012-07-26
CN102481687A (zh) 2012-05-30
CN102481687B (zh) 2016-03-09
RU2012112629A (ru) 2013-10-20

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