EP2095909A1 - Train épicycloïdal pour une machine-outil électrique et machine-outil portative électrique - Google Patents

Train épicycloïdal pour une machine-outil électrique et machine-outil portative électrique Download PDF

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Publication number
EP2095909A1
EP2095909A1 EP08003434A EP08003434A EP2095909A1 EP 2095909 A1 EP2095909 A1 EP 2095909A1 EP 08003434 A EP08003434 A EP 08003434A EP 08003434 A EP08003434 A EP 08003434A EP 2095909 A1 EP2095909 A1 EP 2095909A1
Authority
EP
European Patent Office
Prior art keywords
gear
stage
switching
gear stage
stages
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Withdrawn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
EP08003434A
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German (de)
English (en)
Inventor
Benjamin Wieler
Stefan Dipl.-Ing. Schwarz (Fh)
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.)
Metabowerke GmbH and Co
Original Assignee
Metabowerke GmbH and Co
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 Metabowerke GmbH and Co filed Critical Metabowerke GmbH and Co
Priority to DE200820017689 priority Critical patent/DE202008017689U1/de
Priority to EP08003434A priority patent/EP2095909A1/fr
Publication of EP2095909A1 publication Critical patent/EP2095909A1/fr
Withdrawn legal-status Critical Current

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    • 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

Definitions

  • the invention relates to a planetary gear for an electric hand tool for connecting an output shaft for driving a power tool with a drive motor comprising three switching stages, wherein the planetary gear comprises a first, a second, a third and a fourth gear stage, each having a sun gear, a planet carrier with rotatable thereto mounted planet and a ring gear and wherein switching means are provided for switching between the three switching stages.
  • planetary gear in electric hand tools is basically known.
  • FIG. 1 shows the DE 199 02 197 A1 a gangumschaltbares planetary gear for electric hand tool machines, such.
  • B. screwdriver in which for gear change an axially displaceable ring gear is provided, which belongs to the second planetary stage, in particular three planetary stages are provided, which is disadvantageous here that due to the ring gear to be shifted increased wear is to be feared.
  • Another design with three gear stages is for example from the EP 1 707 847 A2 previously known.
  • a planetary gear with the generic features of claim 1, wherein two of the gear stages switchable and two gear stages are not switchable, wherein each ring gear of a switchable gear stage is associated with a switching means which is connected between a position in which the ring gear of the switchable gear stages rotatably connected to a housing of the planetary gear, that is active, and a position in which the ring gear of switchable gear stages is connected to an adjacent planetary carrier, that is not actively connected, is movable and only one or none of the switchable gear stages is rotatably connected to the housing.
  • the switching means in particular the third stage in the first gear with its inner profile in engagement with the outer profile of the ring gear of the third gear stage. Furthermore, the outer profile of the switching means in the housing, which has a corresponding inner contour for this purpose, fixed and thus locks the ring gear of the third gear stage.
  • the third gear stage is thus actively switched and enters into the translation.
  • the switching means for example, the second stage, which forms the two switchable gear stages with the third stage in the present example, connects in this gear, the planet carrier, for example, the first stage with the ring gear of the second gear stage. In this way, the second gear stage is bridged.
  • the switching means of the second gear stage locked via an engagement in the ring gear and at the same time an engagement in the housing, the second gear stage with respect to the housing and thus switches them active.
  • the switching means of the third gear stage in the present example connects the ring gear of the third gear stage with the planet carrier of the third gear stage, which in the output direction, in particular the adjacent planet carrier to the ring gear of the third gear stage, resulting in a bridging of the third gear stage.
  • the two switchable stages are bridged by the switching means here connect the ring gears of the switchable stages with the adjacent planet carriers, here the planet carrier of the first and third gear stage, and only the first and the fourth gear together form the entire translation.
  • the translations of the first and fourth gear stage thus always go into the overall translation.
  • the switching means have an inner profile and an outer profile, where they can interact with their inner profiles with outer profiles of the ring gears of the switchable stages for switching between the individual switching stages and beyond the housing has such a contour that a guide and locking the switching means in the housing can be achieved.
  • the housing for this purpose has a switching contour which is designed so that at most one of the two switching means can cooperate with the switching contour at the same time to actively switch one of the switchable gear stages. In this way, a particularly simple design can be achieved because the switching means z. T. with the ring gears and planet carriers and z. T. rotationally fixed to the housing, since the angular position of the switching means and the ring gears and planet carrier plays no role.
  • the first gear stage is arranged on the drive side and the fourth gear stage on the output side.
  • the two middle intermediate gear stages are preferably as switchable gear stages designed.
  • the central gear stages are switchable, as neighboring planet carrier in each case with respect to the second gear stage of the following in the drive direction planet carrier, ie the planet carrier of the first stage of the adjacent planet carrier, and in terms of the third stage the downstream in the output direction, here the planet carrier of the third stage, the adjacent planet carrier to the ring gear of the third stage.
  • the ring gears of the switchable gear stages have the same outer diameter.
  • the mountability can be achieved by the continuous design of the housing wall, which is possible with simultaneous shiftability of the gear stages.
  • the ring gears of the switchable gear stages have substantially the same outer diameter as the planetary carrier adjacent to the ring gears, so that the switching process by simply moving the switching means and engaging with the planet carriers in particular third and the first stage can be done.
  • the planet carriers of the first and third stages have an outer diameter substantially corresponding to the outer diameters of the second and third stage ring gears.
  • the switching means can be configured so that they can cooperate with the outer diameter of the ring gears of the switchable stage and the adjacent planetary carriers at the same time to couple the ring gears with the planetary carriers.
  • the ring gears of the first and fourth gear stage may be larger or smaller than those of the second and third gear stage, depending on the required connection of the transmission and installation situation.
  • the switching means are held axially displaceable on the respective ring gear of the shiftable gear stage.
  • the switching means are designed as switching rings, which have a shift gate, and the switching means are in particular coupled together.
  • a switching handle is provided, which acts on both switching means via corresponding connecting means.
  • a switching handle can be preferably provided either a rotary or a slide switch.
  • the planet carrier of a gear stage are formed by regions of the sun gear of a downstream in the output direction gear stage.
  • the drive-side gear stage has a device for adjusting a torque, wherein the configuration of the device for torque adjustment of a design, as shown in the EP 1 787 757 A1 is described, and wherein the content of this document is incorporated herein by reference also in the disclosure.
  • the ring gear of the drive-side gear stage has radially inwardly spring-biased detent body and the locking body are displaced radially outward when a Abschaltmosmoments is exceeded, so that the ring gear is rotatable relative to the housing and the drive shaft is no longer driven, said
  • extended in the circumferential direction of the ring gear leaf springs are provided, the lever arm length for generating various bending forces acting on a respective detent body and are adjustable in the circumferential direction.
  • adjusting the effective spring length is achieved that the springs release the locking body at different output torques, which can be formed in particular as a cylinder, and the ring gear is no longer fixed in the housing.
  • a maximum limit torque can be achieved by selecting a predetermined spring length of the means for adjusting the torque, so that thereby an overload protection z. B. at 40 Nm or 44 Nm of the engine can be achieved.
  • an actuator is provided on the housing, which allows the adjustment in incremental detent positions or continuously.
  • the locking body are cylindrical and the leaf spring has a trapezoidal development.
  • the actuator or adjusting means can press radially inward against the leaf springs and thus pretend their Hebelarmhey.
  • the locking body can be latched into recesses of the ring gear of the corresponding gear stage, wherein a respective recess may be limited to one side by a protruding beyond the outer periphery of the ring gear increase.
  • each detent body is assigned a circumferentially extending leaf spring, on the one hand a maximum torque can be proportionately distributed over several detent bodies, and each detent body can be adjusted by adjusting the Hebelarmin a relevant deflection force to be overcome for the detent body and thus a maximum torque for a tool drive shaft.
  • the torque pre-selection can be almost powerless by the lever arm length is variable, by turning an adjusting element, which specifies the hinge point for a respective leaf spring, in the circumferential direction. It must therefore be overcome to adjust the torque no significant force, which may prove to be complicated and uncomfortable for a user or at least uncomfortable.
  • the bearing of the output shafts can, as in PCT / EP / 2007/007328 described, be provided, whose related disclosure content is thus included here.
  • the invention comprises an electric hand tool device comprising a drive motor, a shiftable transmission, a device housing and a tool holder for a rotationally drivable tool, which is arranged on an output shaft, wherein the transmission is a planetary gear described above.
  • the electric hand tool device comprises a Klemmgesperre, which allows for drive-side drive a rotary drive of the output shaft and blocked at output side rotary drive the output shaft. In this way it can be achieved that a one-handed clamping of a tool is possible without the tool chuck and thus the output shaft must be manually blocked with a second hand, is needed.
  • the electric hand tool which may be in particular a screwdriver, drill, a drill or a hammer drill, is operable in both directions of rotation. In this way, in addition to screwing, for example, unscrewing operations can be performed.
  • FIG. 1 shows a section through a gear housing, which is provided in its entirety by the reference numeral 10, an electric hand tool device, in particular a screwdriver, with an axial direction 12 and a driven-side end 14, which has a receptacle 16 for a tool chuck (not shown).
  • the output-side end 14 has for rotating the drive of a tool which is received in the tool chuck, an output shaft 18 which is connected via a planetary gear 20 with a drive shaft, not shown, which is driven by an electric motor, this either by means of a cable or can be supplied with electrical energy via accumulators.
  • the planetary gear 20 in this case comprises four planetary gear stages, denoted by the reference numerals 22, 24, 26 and 28 in FIG. 1 are designated.
  • Each gear stage has its own sun gear 30, 32, 34 and 36, on the respective planet 38, 40, 42 and 44 rotate.
  • each of the gear stages has a ring gear 46, 48, 50 and 52, wherein the ring gears 48 and 50 of the second and third gear stage have the same outer diameter.
  • the planet carrier 54, 56 and 58 of the first to third gear stage are hereby formed by extensions of the suns of the second, third and fourth gear stage.
  • the outer diameters of the planet carriers 54 of the first gear stage and of the third gear stage 58 substantially correspond to the outer diameters of the ring gears 48 and 50 of the second and third gear stage.
  • switching means 60 and 62 are provided, which are displaceable in the axial direction 12 and connect in one, namely the position shown, the ring gears 50 and 48 with the adjacent planet carriers 54 and 58 of the first and third stage.
  • the switching means 60 and 62 are formed as switching rings with an internal toothing and have a shift gate, by means of which they can be connected to a switch handle, which is arranged on a device housing of an electric hand tool device, and via which an adjustment of the switching means 60 and 62.
  • the planet carrier 68 of the fourth gear stage receives the drive end of the output shaft 18 and the output side planet carrier, so the planetary carrier 68 of the fourth gear stage, is radially mounted in the transmission housing. During storage, this can be a floating bearing.
  • the bearing is provided with the reference numeral 70.
  • a bearing 72 may be provided which receives both radial and axial forces.
  • Klemmgesperre 74 is provided to block a rotation transmission from the side of the output shaft 18 to a drive shaft, wherein the Klemmgesperre 74 is connected downstream of the planetary gear 20.
  • the planet carrier 68 of the fourth gear stage 28 driver 76 has for the Klemmgesperre, which are in particular integrally connected to the planet carrier 68 of the fourth gear stage 28.
  • the drive-side end of the output shaft 18 may be slidably mounted in the planetary gear 68 of the fourth gear stage 28, so there experience only a radial guidance.
  • ball bearings can be used as storage for both the fixed and the floating bearing 70 and 72 deep groove ball bearings. In principle, however, ball or roller bearings can be used. It is particularly preferred if the two bearing points 70 and 72 are as far away from each other on the output shaft 18, and so a possible tilt-free storage of the output shaft 18 can be carried out. In this way, the axial space of a hand-held power tool can be kept low while maintaining stable storage, which is particularly desirable in drills, but also drills and screwdrivers.
  • a corresponding bearing has the advantage that a constant function of the Klemmgesperres 74 can be ensured and the risk that the Klemmgesperre tilted or hitting is reduced since the exact concentricity of the driver 76 is guaranteed.
  • FIG. 2 Now, the circuit of a planetary gear 20 according to FIG. 1 explained in more detail.
  • the transmission here consists of the four stages 22, 24, 26 and 28, wherein FIG. 2 the gear change by means of the switching means 60 and 62 shows, and the circuit is such that in the first gear, the switching means 62 is in engagement with the ring gear 50 of the third gear stage 26 and the housing in the form of the housing contour 64.
  • the first switching means 60 is engaged both with the ring gear 48 of the second gear stage 24 and the planet carrier 54 of the first gear stage 22, wherein the ring gear 48 of the second gear stage 24 can rotate relative to the housing and the second gear stage 24 is inactivated and the third gear stage 26 is in an activated state.
  • both switching means 60 and 62 are now shifted, so that now the switching means 60 is in engagement with the housing (here with the housing contour 64) and the ring gear 48 and the switching means 62, the ring gear 50 with the planet carrier 58, the adjacent Planet carrier is to be considered and also belongs to the third gear 26, connects.
  • the third gear 26 is then inactivated and can rotate relative to the housing. In this case, then the second gear stage 24 in the translation with, resulting in together with the first and the fourth gear stage, the overall ratio.
  • both the second and the third switching stage are bridged, d. H. they are each inactive and coupled to the adjacent planet carrier 54 and 58 with respect to their ring gears 48 and 50 and can rotate freely in the housing, so that the overall ratio of the translation of the first and fourth gear stage 22 and 28 results.
  • FIG. 3 shows a design of the first gear stage 22 in a plan view.
  • the ring gear 46 of the first gear stage 22 is not identical to the outer diameters of the ring gears 48 and 50 by the choice of a different housing diameter at this point, but can to the switching means 60 and 62, in the radial direction to the ring gears 48 and 50th connect, be made larger.
  • the first gear stage 22 comprises three planets 38, which rotate in a ring gear 46 and on a sun 30.
  • the first gear stage 22 has a device for torque adjustment, which in the EP 1 787 757 A1 may correspond to and described in FIG. 7 will be explained in more detail.
  • the first gear stage 22 is not switchable and its sun 30 is mounted on the output spindle of a motor, which is also referred to as the drive shaft.
  • a motor which is also referred to as the drive shaft.
  • the speed and torque output values of an engine are the input values of the first gear stage 22.
  • FIG. 4 shows a plan view of the second gear stage, which is a switchable gear stage.
  • the second gear 24 only affects the ratio in the second gear, in which the second gear is active.
  • a low gear ratio is selected.
  • the second gear stage 22 comprises a sun 32 and a ring gear 48, wherein planets 40 are provided between the sun 32 and the ring gear, and in contrast to the first gear stage 22, four planets 40 are arranged in the ring gear 48.
  • the ring gear 48 In addition to its inner contour, which allows the rolling movement of the toothed planets 40, the ring gear 48 has an outer contour in which the switching means 60 engages with an inner contour, which likewise has an inner and an outer contour and with its outer contour in an inner profile or a Inner contour 64 of the housing engages.
  • the outer contour of the ring gear 48 is designated by the reference numeral 49.
  • the contours may have flattened teeth, as shown. However, it is also basically contours with pointed teeth, as they correspond to the inner contour of the ring gear 48, possible.
  • the selection is such that a slight displacement movement in the axial direction is made possible.
  • the third gear stage 26 is in FIG. 5 illustrated, wherein the third gear stage also includes four planets 42, which rotate on a sun 34 and in a ring gear 50.
  • the ring gear 50 here also has an outer contour 51, which is analogous to the outer contour 49 of the second gear stage 24, which cooperates with the inner contour of a switching means 62, which in turn engages with its outer contour in an inner contour of the housing 10.
  • the representation of the second gear stage 24 and the third gear stage 26 in the FIGS. 4 and 5 takes place in each case in the active state in which the ring gears 48 and 50 are locked to the housing 10.
  • FIG. 6 shows the fourth gear stage, which has, in contrast to the second and third gear stages, five planets 44 which revolve in a ring gear 52 and mesh with a sun 36.
  • the ring gear 52 of the fourth gear 28 is fixed in the housing 10 and has for this purpose an outer contour 53, which cooperates with a corresponding contour of the housing 10.
  • the locking of the ring gear 52 with the housing 10 here has no switching function, but a fixing function that takes place both axially and radially.
  • FIG. 7 shows a sectional view through a gear stage 22 of an electric hand tool device according to the invention, which is here alternatively equipped with four planets 38 which are driven by a sun gear 30, not shown.
  • the axes 39 of the planet gears are connected to the planet carrier 54, not shown.
  • the planets 38 roll against the internal teeth of the ring gear 46, the axes 39 move on a circular line and thus drive the Planet carrier 54 on.
  • the ring gear 46 is locked fixed to the housing.
  • the ring gear 46 on its outer periphery recesses 80, in which preferably cylindrical locking body 82 engage.
  • the locking body 82 project through radial passage openings 84 in a housing-fixed ring or flange which surrounds the ring gear 46 concentrically and is provided with the reference numeral 86.
  • the ring gear 46 is coupled via the plurality, preferably three detent body 16 to the housing-fixed ring 86.
  • the locking body 82 are biased radially inwardly by means of leaf springs 88. These leaf springs 88 are in the circumferential direction 90, that is concentric with the housing-fixed ring 86 and the ring gear 46, extends.
  • each of the three leaf springs 88 abuts against a latching body 82 with one end radially outward and presses it radially inward.
  • the aforementioned actuator 92 presses with a radially inwardly projecting projection 94 against the respective leaf spring 88 and thus fixes the hinge point, so that there is an effective spring arm between this hinge point and the free end 96 of the respective leaf spring 88.
  • the Hebelarmzel can be varied by adjusting the actuator 92 in the circumferential direction 90.
  • the above components thus form a Drehmomenteinstell- or If the respective projection 94 comes to lie radially outside of the respective latching body 82, then the torque limitation is quasi deactivated, since the latching body 82 does not come out of the coupling position in such a case.
  • the Drehmomenteinstell Stein 98 is designed so that the torque limiter can be varied continuously or in steps of, for example, 0.5 Nm as the lowest torque limit to a final value as the largest torque limit.
  • an overload protection of at least 40 Nm, preferably 44 Nm can be realized.
  • a respective recess 80 is bounded to one side by an increase 100, which projects radially slightly beyond the other outer circumference of the ring gear 46. In this way, that flank 102 which abuts against the relevant latching body 82 is increased, so that a uniform introduction of force into the latching body 82 is possible with less surface stress and less wear.
  • the planetary gears 38 roll over the internal teeth of the ring gear 46, wherein the ring gear 46 is fixed by the locking body 82 fixed to the housing fixed to the ring 86 non-rotatable.
  • the rotation of the axles 39 of the planet gears 38 is transmitted to the following gear stage 24 via a not-shown, in particular disc-shaped coupling element, namely the planet carrier 54.
  • the ring gear 46 or its respective depressions 80 for the locking body 82 delimiting flanks loading against the respective latching body 82 and results in a respective latching body 82 radially outwardly urging force.
  • the ring gear 46 relative to the housing-fixed ring 86 remains non-rotatable. However, if the opposing force exerted by the leaf springs 86 is exceeded, then the detent body 82 is pushed radially outward from the depression 80 and the ring gear 46 is rotated relative to the housing-fixed ring 86 until it engages the next depression 80 under the pressure of the leaf spring 88 or even this depression 80 skips. In this way, a torque limitation, ie a limitation of the force exerted on the workpiece by the tool torque is achieved. Particularly advantageous here, the leaf springs 88 may be designed trapezoidal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
EP08003434A 2008-02-26 2008-02-26 Train épicycloïdal pour une machine-outil électrique et machine-outil portative électrique Withdrawn EP2095909A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200820017689 DE202008017689U1 (de) 2008-02-26 2008-02-26 Planetengetriebe für ein Elektrohandwerkzeuggerät sowie Elektrohandwerkzeuggerät
EP08003434A EP2095909A1 (fr) 2008-02-26 2008-02-26 Train épicycloïdal pour une machine-outil électrique et machine-outil portative électrique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08003434A EP2095909A1 (fr) 2008-02-26 2008-02-26 Train épicycloïdal pour une machine-outil électrique et machine-outil portative électrique

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010034565A1 (fr) * 2008-09-29 2010-04-01 Robert Bosch Gmbh Machine-outil manuelle équipée d'une broche destinée à recevoir un outil
WO2011135076A1 (fr) * 2010-04-29 2011-11-03 Tomactech A/S Outil électrique
US8262533B2 (en) 2006-04-30 2012-09-11 Tomatech A/S Transmission
EP2631038A2 (fr) * 2012-02-27 2013-08-28 Black & Decker Inc. Outil à transmission planétaire composé à plusieurs vitesses
EP3032141A1 (fr) * 2014-12-12 2016-06-15 Hua Yong Machine Industry Co., Ltd. Appareil doté d'un moyen de décalage de puissance à multiples étages appliqué à une machine-outil

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19902187A1 (de) 1998-03-04 1999-09-16 Scintilla Ag Gangumschaltbares Planetengetriebe
EP1190817A2 (fr) 2000-09-26 2002-03-27 Shanghai Xing Te Hao Industrial Co., Ltd. Boíte de vitesse à trois vitesses pour un outil à moteur
DE20209356U1 (de) * 2002-06-15 2002-10-02 Schelb Bernhard Getriebe für Elektrowerkzeuge
EP1426989A1 (fr) * 2002-11-14 2004-06-09 Black & Decker Inc. Outil à main à moteur électrique
US6796921B1 (en) * 2003-05-30 2004-09-28 One World Technologies Limited Three speed rotary power tool
EP1364138B1 (fr) 2001-01-23 2006-09-27 BLACK & DECKER INC. Transmission d'outil electrique a vitesses multiples
EP1787757A1 (fr) 2005-11-18 2007-05-23 Metabowerke GmbH Tournevis ou perceuse à moteur électrique avec engrenage planétaire

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19902187A1 (de) 1998-03-04 1999-09-16 Scintilla Ag Gangumschaltbares Planetengetriebe
EP1190817A2 (fr) 2000-09-26 2002-03-27 Shanghai Xing Te Hao Industrial Co., Ltd. Boíte de vitesse à trois vitesses pour un outil à moteur
EP1364138B1 (fr) 2001-01-23 2006-09-27 BLACK & DECKER INC. Transmission d'outil electrique a vitesses multiples
EP1707847A2 (fr) 2001-01-23 2006-10-04 Black & Decker, Inc. Transmission d'outil électrique à vitesses multiples
DE20209356U1 (de) * 2002-06-15 2002-10-02 Schelb Bernhard Getriebe für Elektrowerkzeuge
EP1426989A1 (fr) * 2002-11-14 2004-06-09 Black & Decker Inc. Outil à main à moteur électrique
US6796921B1 (en) * 2003-05-30 2004-09-28 One World Technologies Limited Three speed rotary power tool
EP1787757A1 (fr) 2005-11-18 2007-05-23 Metabowerke GmbH Tournevis ou perceuse à moteur électrique avec engrenage planétaire

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8262533B2 (en) 2006-04-30 2012-09-11 Tomatech A/S Transmission
US8955617B2 (en) 2008-09-29 2015-02-17 Robert Bosch Gmbh Hand-held power tool comprising a spindle for receiving a tool
WO2010034565A1 (fr) * 2008-09-29 2010-04-01 Robert Bosch Gmbh Machine-outil manuelle équipée d'une broche destinée à recevoir un outil
WO2011135076A1 (fr) * 2010-04-29 2011-11-03 Tomactech A/S Outil électrique
US10391623B2 (en) 2010-04-29 2019-08-27 Hilti Aktiengesellschaft Power tool
US9233461B2 (en) 2012-02-27 2016-01-12 Black & Decker Inc. Tool having multi-speed compound planetary transmission
EP2631038A3 (fr) * 2012-02-27 2013-09-25 Black & Decker Inc. Outil à transmission planétaire composé à plusieurs vitesses
US9604354B2 (en) 2012-02-27 2017-03-28 Black & Decker Inc. Tool having multi-speed compound planetary transmission
US10195731B2 (en) 2012-02-27 2019-02-05 Black & Decker Inc. Tool having compound planetary transmission
EP2631038A2 (fr) * 2012-02-27 2013-08-28 Black & Decker Inc. Outil à transmission planétaire composé à plusieurs vitesses
US10926398B2 (en) 2012-02-27 2021-02-23 Black & Decker Inc. Tool having compound planetary transmission
US11738439B2 (en) 2012-02-27 2023-08-29 Black & Decker Inc. Power tool with planetary transmission
EP3032141A1 (fr) * 2014-12-12 2016-06-15 Hua Yong Machine Industry Co., Ltd. Appareil doté d'un moyen de décalage de puissance à multiples étages appliqué à une machine-outil

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