EP2655021B1 - Système de transmission pour un outil électrique et outil électrique - Google Patents

Système de transmission pour un outil électrique et outil électrique Download PDF

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Publication number
EP2655021B1
EP2655021B1 EP11782444.1A EP11782444A EP2655021B1 EP 2655021 B1 EP2655021 B1 EP 2655021B1 EP 11782444 A EP11782444 A EP 11782444A EP 2655021 B1 EP2655021 B1 EP 2655021B1
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EP
European Patent Office
Prior art keywords
gear
additional
toothing
transmission arrangement
planetary gear
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.)
Not-in-force
Application number
EP11782444.1A
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German (de)
English (en)
Other versions
EP2655021A1 (fr
Inventor
Andre Ullrich
Holger Ruebsaamen
Andreas Schlegel
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
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2655021A1 publication Critical patent/EP2655021A1/fr
Application granted granted Critical
Publication of EP2655021B1 publication Critical patent/EP2655021B1/fr
Not-in-force 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
    • 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 transmission arrangement for a power tool, in particular an electric hand tool according to the preamble of the independent claim.
  • gear arrangements for transmitting a rotary motion are already known, which are preferably arranged between a drivable by a drive unit for generating a rotary drive shaft to an output shaft of a utility unit, wherein the gear arrangement comprises a planetary gear with at least one planetary gear set.
  • the planetary gearset includes a sun gear, at least one planet gear carried by a planet carrier or land, and a ring gear as members of a planetary gear stage, wherein due to the construction, an axis of rotation of an input shaft of the planetary gear is aligned parallel to a rotation axis of an output shaft of the planetary gear.
  • Such gear arrangements offer gear ratios IPx per planetary gear stage between 2.8 and 13, preferably between 3.5 and 8, at the same time compact, axial and lateral dimensions, which makes their use particularly in compact electric hand tools with small, high-speed motors as drive units seem favorable ,
  • IPx of a planetary gear stage in particular a so-called stationary translation, i.
  • the parallel alignment of the input and output shaft usually has an axial-serial, one behind the other arrangement of the engine and transmission arrangement for Series, which restricts the free space in the design of the power tool.
  • the axial-axial arrangement proves to be disadvantageous from an ergonomic point of view, in particular as regards the mass distribution.
  • a hand tool gearbox is particularly known for an angle grinder with a rotatably mounted and driven by an electric motor drive shaft and a rotatably mounted output shaft for driving a tool, wherein a planetary gear with an upstream bevel gear is provided for torque transmission from the drive shaft to the output shaft.
  • the gear ratio of the planetary gear is in the range of 1.8 to 4.5, that of the bevel gear in the range of 3 to 4.5, so that the overall result is a total ratio in the range of 5.4 to 20.25.
  • a corresponding arrangement for an angle drill, but with the planetary gear downstream bevel gear, can be found in the US 2001/0031179 A1 ,
  • the transmission arrangement according to the invention has the advantage of combining the high transmission ratio in a compact design of a planetary gear with the performance of a larger engine in an ergonomically favorable manner.
  • the gear arrangement according to the invention comprises a planetary gear with at least one planetary gear, wherein a member of the planetary gear carries a toothing for engagement in a toothing of an additional gear, wherein the member and the additional gear form a crown gear.
  • the toothing of the additional gear as a crown toothing and the additional toothing of the member are formed as a spur toothing.
  • Such an arrangement is particularly tolerant of an axial clearance between the planetary gear and the axis of rotation of the additional gear, in particular the relative axial position of the planetary gear relative to the axis of rotation of the additional gear.
  • an additional gear is understood in particular a gear, which is not part of a planetary gear set.
  • the additional has Gear on a rotational axis, which is aligned at an angle W1 greater than 0 °, preferably between 10 ° and 80 ° relative to the axes of rotation of the input and output shafts of the planetary gear.
  • the angle gear preferably has a gear ratio IW between 1 and 4.
  • a preferred overall ratio for a transmission arrangement according to the invention with a planetary gear stage and the bevel gear lies between 2.8 and 52, in particular between 3.5 and 32.
  • the gear arrangement according to the invention thus opens up at least one additional degree of freedom in the selection and ergonomic arrangement of drive unit, in particular motor and gear arrangement in relation to a power unit of the power tool.
  • a particularly advantageous ergonomic view arrangement freedom, especially between a drive and a utility unit is achieved when the planet carrier of the planetary gear carries the additional teeth.
  • This can be arranged both on a provided on the planet carrier wave-like nose, which in particular allows higher transmission ratio IW for the angular gear, or even be provided on a surface, in particular a front or side surface of the planet carrier.
  • the additional toothing itself may be formed as a crown gear, wherein the additional gear then preferably forms a pinion and is designed in particular as a front or worm wheel.
  • possibly advantageous low transmission ratios can be achieved particularly easily if a ring gear of the planetary gear carries the additional teeth, in particular if the additional toothing is arranged on an outer peripheral surface of the ring gear. However, it can also be provided to attach the additional teeth on an end face of the ring gear. With such arrangements can be easily angular gear, in particular crown gear with gear ratios in the range of about 1 produced.
  • a sun gear of the planetary gear carries the additional toothing.
  • the additional toothing of the sun gear may be a crown gear toothing.
  • At least one fixing means is provided, with which a member of the planetary gear, in particular a ring gear or a planet carrier or a sun gear, relative to an outer rest system can be fixed.
  • a member of the planetary gear in particular a ring gear or a planet carrier or a sun gear
  • an outer rest system is in particular a relation to the rotational movement and Preferably also understood a translational movement of the gear assembly resting, stationary system.
  • This may preferably be a coordinate system defined by a housing of the power tool.
  • the fixing means can be carried out both as a cost, substantially rigid connection between the member and a reference point of the rest system as well as be formed by a brake and / or coupling means for releasably securing the member, wherein the rotational movement of the member relative to the rest system at least braked, is preferably blockable.
  • a brake and / or coupling means for releasably securing the member, wherein the rotational movement of the member relative to the rest system at least braked, is preferably blockable.
  • suitable non-positive and / or positive-working brake and / or clutch devices such as friction brakes, friction clutches, claw or detent clutches, which are advantageously used in the context of the invention.
  • the meshing teeth of the additional gear and the member are formed as straight or helical teeth.
  • the planetary gearset comprises two or more planetary gear sets, in particular two or more planetary gear stages, slightly higher gear ratios can be achieved with the gearbox arrangement according to the invention with an acceptable additional space requirement.
  • a power tool in particular an electric hand tool, with an electric drive unit for generating a rotational movement on a drive shaft and a rotatably driven output shaft of a use unit
  • the rotational movement of the drive shaft to the output shaft by means of a gear assembly according to the invention ergonomically and moderately favorable production with respect to a relative arrangement of drive unit and use unit transfer.
  • Fig. 1 shows a schematic view of a first embodiment of a transmission assembly 10 according to the invention for a power tool, in particular for an electric hand tool, which comprises a planetary gear 12 and a standing with the planetary gear 12 in operative context bevel gear 14.
  • Such gear arrangements typically have axial and lateral dimensions of a few centimeters to a maximum of approximately two decimetres.
  • the planetary gear 12 has in the schematic representation Fig. 1 a planetary gear 16, which a sun gear 18, two arranged on a planet carrier 20 and rotatably mounted relative to the planet carrier 20, with the sun gear 18 via active surfaces 22, 24 operatively connected planetary gears 26 and an inner active surface 28 with the planetary gears 26 in Actively connected ring gear 30 comprises, wherein the planet carrier 20, the sun gear 18 and the ring gear 30 form the members 32 of a planetary gear stage 34.
  • the planetary gear 16 may have only one or three or more planetary gears 26.
  • Fig. 1 carry the active surfaces 22, 24 and 28 of the respective gears gears, preferably spur gears 36a, 36b, 36c, via which the active compounds for transmitting a rotational movement between the respective members of the planetary gear set 16 are made.
  • the skilled person are beyond other possibilities for producing such an operative connection such as Reibradtellen and / or alternative gearing known, which can be advantageously used in a planetary gear of a gear assembly according to the invention, without departing from the spirit.
  • the sun gear 18 of the planetary gear 16 is in the embodiment according to Fig. 1 Rotatable about a first axis of rotation 38 on a sun gear 40 and forms an input or output side 42, 43 of the transmission assembly 10 according to the invention
  • the sun gear shaft 40 in a storage device 44, for example, a sliding, needle and / or roller bearing opposite stored forces occurring supporting.
  • the bearing device 44 is in Fig. 1 shown only dashed, since it is not central to the inventive effect of the gear assembly 10 and the skilled person can easily implement alternative storage concepts that do not affect the inventive idea.
  • a rotational movement 46 of the sun gear shaft 40 is transmitted via the toothing 36a of the sun gear 18 and the toothing 36b of the planet gears 26.
  • the ring gear 30 is fixed by means of a substantially rigid connection with a relative to the rotational movement 46 of the sun gear 40 substantially resting element 48, for example, a gear assembly 10 at least partially comprehensive housing 49.
  • the connection of the ring gear 30 with the element 48 is an example of a fixing means 52. Further embodiments of a suitable fixing means 52 are described in subsequent embodiments and can easily be made by the skilled person to this first Embodiment of a transmission arrangement according to the invention are transmitted.
  • the teeth 36b of the planet gears 26 are based on the teeth 36c of the ring gear 30 from that the planet carrier 20 is caused to a rotational movement 46 rectified rotational movement 54.
  • the Planet carrier 20 of the embodiment according to Fig. 1 has a wave-like nose 56, which carries an additional toothing 58.
  • the wave-like nose 56 preferably extends around an axis of rotation 60 of the planet carrier 20, which is aligned substantially parallel, preferably coaxially with the axis of rotation 38.
  • the additional gear 58 is operatively connected to a toothing 62 of an additional gear 64.
  • the additional gear 64 is rotatably mounted about an axis of rotation 66 on an angle gear shaft 68, wherein the axis of rotation 66 of the additional gear 64 with the axis of rotation 60 of the wave-like nose 56 below includes a non-zero angle W1, in particular is aligned substantially perpendicular to this.
  • the additional teeth 58 is in the embodiment according to Fig. 1 formed as a straight or helical spur gear teeth 59 which meshes with a correspondingly formed crown gear teeth 63 as a toothing 62 of the additional gear 64.
  • the additional gear 64 may therefore also be referred to as crown gear 70.
  • angle gear shaft 68 is supported by a bearing device 44.
  • the wave-like nose 56 with its additional teeth 58, 59 forms with the teeth 62, 63 of the additional gear 64, the angle gear 14 of the transmission assembly 10 according to the invention, wherein the angular gear shaft 68 forms an output or input side 43, 42 of the gear assembly 10.
  • a transmission ratio IW of the angle gear 14 is calculated from the ratio of the number of teeth of the additional toothing 58 with respect to the toothing 62.
  • a total translation of the gear arrangement after Fig. 1 results from the product of (1 - IP1) and IW, where IP1 is the state translation of a planetary gear stage 34, wherein the rotation is deflected by the angle W1 and reversed in rotation.
  • the additional gear 64 which meshes with the additional teeth 58, 59, formed as a conical crown gear 72, wherein an opening angle WK of the conical crown wheel 72 twice the angle W1 between the rotation axis 60 and the Angle gear shaft 68 corresponds. Preference is given to angle W1 between 10 ° and 80 °, more preferably between 50 ° to 80 °.
  • the gear assembly 10 corresponds to Fig. 2 otherwise according to the embodiment Fig. 1 , to the description of which reference is made at this point.
  • Fig. 3 is a further modification of the embodiment according to Fig. 1 shown as a third embodiment.
  • the planet carrier 20 has no wave-like nose, but the additional toothing 58 is arranged as a spur gear toothing 59 on an outer peripheral surface 74 of the planet carrier 20.
  • the additional toothing 58 is arranged as a spur gear toothing 59 on an outer peripheral surface 74 of the planet carrier 20.
  • axis of rotation 66 of the additional gear 64 which as in the example according to Fig. 1 is designed as a crown wheel, substantially perpendicular to the axis of rotation 60 of the planet carrier 20.
  • a conical crown wheel 72 like out Fig. 2 known to combine such that the angle W1 of the axes of rotation 60, 66 between 10 ° and 80 °, more preferably between 50 ° to 80 °.
  • a fourth exemplary embodiment of a transmission arrangement 10 is obtained Arrangement of the additional teeth 58 as a straight or helical crown gear teeth 76 on a side surface 78, in particular on a side facing away from the planetary gear 34 side surface 78 of the planet carrier 20.
  • the crown gear 76 is provided with a designed as a spur gear teeth 62 62 of the additional gear 64th combing, wherein the axis of rotation 66 of the additional gear 62 analogous to the embodiments described above with the axis of rotation 60 of the planet carrier 20 includes an angle W1 between 10 ° and 90 ° - Fig. 4 shows the orientation below 90 °.
  • transmission assembly 10 can on the one hand by adjusting a radius or number of teeth of the laterally mounted crown gear 76 on the planet carrier and / or corresponding change of the toothing 80 of the additional gear preferred ratios IW of the angular gear 14 without strong interference in example space parameters of Implement gear arrangement 10.
  • such an arrangement is tolerant of variations in the lateral position of the additional gear 64 along the angular gear axis 66.
  • Fig. 5 shows a further modification of the embodiment according to Fig. 1 in which at the wave-like nose 56 a the additional toothing 62 carrying wheel-shaped structure 82.
  • the wheel-shaped structure 82 carries on one, in this example conical outer surface 84, the additional teeth 62, which is formed as Kronradvertechnikung 86.
  • the additional gear 64 is formed as a spur gear 80.
  • the angular gear shaft 68 extending about the rotation axis 66 is designed as a motor shaft 88 of an electric motor 91 forming a drive unit 90.
  • the axis of rotation 66 and the axis of rotation 60 of the planet carrier 20 in turn enclose an angle W1, which corresponds to half of the opening angle WK of the conical outer surface 84.
  • the angle W1 is between 10 ° and 80 °, more preferably between 50 ° to 80 °.
  • the angular gear shaft 66 forms the input side 42 and the sun gear shaft 40, the output side 43 of the transmission assembly 10 of the invention.
  • the additional toothing 58 is provided on a circumferential surface 92 of the ring gear 30.
  • the ring gear 30 is rotatable relative to the rest system 50, in particular freely rotatably mounted.
  • a brake and / or clutch device 94 for releasably securing the planet carrier 20 relative to the rotational movement 46 by means of braking and / or blocking effect as a fixing means 52 is provided on the planet carrier 20. If the planet carrier 20 is braked or preferably fixed relative to the stationary element 48, 49, the ring gear 30 is driven via the meshing teeth 36b, 36c to a rotational movement 96 opposite the rotational movement 46.
  • the brake and / or clutch device 94 can bring about force and / or positive connection with the stationary element 48, 49.
  • suitable non-positive and / or positive-working brake and / or clutch devices 94 are known, such as friction brakes, friction clutches, claw or locking clutches, which are advantageously used in the context of the invention.
  • the fixing means 52 is formed as a simple, preferably rigid connection between the planetary carrier 20 and the stationary element 48, 49.
  • the additional toothing 58 on the ring gear 30 is according to Fig. 6 preferably formed as a straight or helical spur gear teeth 98 and is operatively connected to the toothing 62 of the additional gear 64, which is arranged on the angular gear shaft 68.
  • the toothing 62 is formed as complementary to the spur gearing 98 crown gear 100.
  • the axis of rotation 66 of the angular gear shaft 68 encloses an angle W1 between 10 ° and 90 ° with the axis of rotation 38 of the sun gear 18 in an analogous manner to already known exemplary embodiments - Fig. 6 shows the orientation below 90 °.
  • Fig. 7 shows a in the first embodiment according to Fig. 1 constructive development of a transmission assembly according to the invention 10. It is the Planetary gear stage 34 of the planetary gear 12 upstream of a second planetary gear stage 34a.
  • the second planetary gear stage 34a comprises a sun gear 18a, a planet carrier 20a carrying planet gears 26a and a ring gear 30a.
  • the planet carrier 20a in turn has a wave-shaped nose 56a, which forms the sun gear 18 of the planetary gear stage 34.
  • the design of the transmission assembly 10 according to the invention differs Fig. 7 only so far from the execution Fig. 1 than that the planetary gear 12 is a two-stage transmission with a corresponding larger possible transmission ratio, but it does not depart from the gist of the invention.
  • Fig. 8 shows a further embodiment, which essential features of the embodiments according to Fig. 6 and 7 combined.
  • the planetary gear stage 34 as they are made Fig. 6 is known
  • a second planetary gear 34a according to Fig. 7 upstream the operation within the meaning of the invention, however, remains unchanged.
  • fixing means 52 as a substantially rigid connections with the resting element 48, 49 may also be a combination with at least one brake and / or clutch device 94 may be advantageous, as they are made Fig. 6 is known.
  • Fig. 9 shows a further, fundamental variant of a transmission arrangement 10 according to the invention.
  • the additional toothing 58 is provided on the sun gear shaft 40.
  • Analogous to the embodiment according to Fig. 1 is the additional teeth 58 formed as a straight or helical spur gear teeth 59 which meshes with the toothing 62 formed as complementary Zronenradvertechnikung 62 of the additional gear 64.
  • the additional teeth 58 as a conical crown gear 100 similar, for example, according to Fig. 5 is trained.
  • the sprocket provided with the spur gear 80 meshes with the motor shaft 88 with the conical Kornradvertechnikung 100, so that the motor shaft 88 with the sun gear 40 includes an angle W1, which is related in a known manner with the opening angle of the cone WK of the crown gear 100.
  • Fig. 11 shows a simple application example of a transmission assembly 10 according to the invention in an electric hand tool 200, in particular an electric screwdriver, a drill, a percussion drill, a hammer drill or similar power tool.
  • an electric hand tool 200 in particular an electric screwdriver, a drill, a percussion drill, a hammer drill or similar power tool.
  • the electric hand tool 200 comprises in a housing 201 a drive unit 204 which is preferably designed as an electric motor 202 and has a motor shaft 208 which acts as a drive shaft 206 and which extends along a drive rotational axis 210.
  • the drive unit 202, 204 is provided to drive an output shaft 212 of a use unit 214 at least rotationally, wherein the output shaft 212 extends along an output rotational axis 216.
  • a tool holder 220 Arranged on an end-side end region 218 of the housing 201 is a tool holder 220 which can be driven at least in a rotatable manner and which is connectable, in particular connected, to the output shaft 212 to form a rotary drive.
  • the tool holder 220 forms, together with a tool 222 and the output shaft, the use unit 214 of the electric hand tool 200.
  • the drive shaft 206 and the output shaft 212 for transmitting the rotational movement of the drive shaft 206 to the output shaft 212 of the use unit 214 via a gear assembly 10 according to the invention with each other operatively connected.
  • the drive rotational axis 210 of the drive shaft 206 and the output rotational axis 216 of the output shaft 212 are non-parallel aligned with each other, in particular, they include an angle W2 between 10 ° and 80 °, preferably between 50 ° and 80 °.
  • the gear assembly 10 according to the invention in the application example Fig. 11 corresponds to the embodiment according to Fig. 2 , wherein the Finradwelle 40 forms the input side 42 of the gear assembly 10 and the angular gear axis 68, the output side 43.
  • the planetary gear 12 is disposed on the drive shaft 206 associated side of the gear assembly 10.
  • the additional gear 68 is in the example after Fig. 11 rotatably connected to the output shaft 212.
  • the additional gear 68 is arranged on the side of the gear arrangement 12 assigned to the drive shaft 206.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Claims (13)

  1. Système de transmission (10) pour la transmission d'un mouvement de rotation dans un outil électrique, en particulier dans un outil électrique à main, comportant une transmission planétaire (12) comprenant un train planétaire (16) et une roue dentée supplémentaire (64), au moins un organe (18, 20, 30 ; 32) de la transmission planétaire (12) portant une denture supplémentaire (58) pour l'engrènement avec une denture (62) de la roue dentée supplémentaire (64), l'organe (18, 20, 30 ; 32) et la roue dentée supplémentaire (64) formant un engrenage de chant (14), caractérisé en ce que la denture (62) de la roue dentée supplémentaire (64) est réalisée sous forme de denture de chant (63), et la denture supplémentaire (58) de l'organe (18, 20, 30 ; 32) est réalisée sous forme de denture droite (59).
  2. Système de transmission (10) selon la revendication 1, caractérisé en ce qu'un porte-planétaire (20) de la transmission planétaire (12) porte la denture supplémentaire (58).
  3. Système de transmission (10) selon la revendication 2, caractérisé en ce que le porte-planétaire (20) comporte un ergot (56) de type arbre sur lequel est disposée la denture supplémentaire (58).
  4. Système de transmission (10) selon la revendication 1, caractérisé en ce qu'une couronne (30) du train planétaire (12) porte la denture supplémentaire (58), en particulier en ce que la denture supplémentaire (58) est disposée sur une surface périphérique extérieure de la couronne (30).
  5. Système de transmission (10) selon la revendication 1, caractérisé en ce qu'une roue solaire (18) de la transmission planétaire (12) porte la denture supplémentaire (58), en particulier en ce que la denture supplémentaire (58) est une denture de chant (86).
  6. Système de transmission (10) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un moyen de fixation (52) est prévu, à l'aide duquel un organe de la transmission planétaire (12), en particulier une couronne (30) ou un porte-planétaire (20) ou une roue solaire (18), peut être fixé par rapport à un référentiel au repos extérieur (50).
  7. Système de transmission (10) selon la revendication 5, caractérisé en ce que le moyen de fixation (52) est réalisé sous la forme d'un dispositif de freinage et/ou d'accouplement (94), lequel peut au moins freiner, de préférence empêcher, un mouvement de rotation de l'organe (18, 20, 30 ; 32) par rapport à un boîtier (49) formant le référentiel au repos (50).
  8. Système de transmission (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que les dentures (58, 62) en engrènement de la roue dentée supplémentaire (64) ainsi que de l'organe (18, 20, 30 ; 32) sont réalisées sous forme de denture droite ou hélicoïdale.
  9. Système de transmission (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la transmission planétaire (12) comporte deux ou plus de deux trains planétaires (16, 16a), en particulier deux ou plus de deux étages de transmission planétaire (34, 34a).
  10. Outil électrique, en particulier outil électrique à main (200), comprenant une unité d'entraînement électrique (202, 204) pour générer un mouvement de rotation au niveau d'un arbre d'entraînement (206, 208) et un système de transmission (10) selon l'une quelconque des revendications précédentes pour la transmission du mouvement de rotation à un arbre de sortie (212) d'une unité d'utilisation (214).
  11. Outil électrique selon la revendication 10, caractérisé en ce qu'un axe de rotation d'entraînement (210) de l'arbre d'entraînement (206, 208) et un axe de rotation de sortie (216) du système de transmission (10) sont orientés de manière non parallèle l'un à l'autre.
  12. Outil électrique selon la revendication 10 ou 11, caractérisé en ce que la transmission planétaire (12) est disposée sur un côté du système de transmission (10) associé à l'arbre d'entraînement (206, 208) .
  13. Outil électrique selon la revendication 10 ou 11, caractérisé en ce que la roue dentée supplémentaire (64) est disposée sur un côté du système de transmission (10) associé à l'arbre d'entraînement (206, 208).
EP11782444.1A 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique Not-in-force EP2655021B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010063623 DE102010063623A1 (de) 2010-12-21 2010-12-21 Getriebeanordnung für ein Elektrofahrzeug und Elektrowerkzeug
PCT/EP2011/070275 WO2012084350A1 (fr) 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique

Publications (2)

Publication Number Publication Date
EP2655021A1 EP2655021A1 (fr) 2013-10-30
EP2655021B1 true EP2655021B1 (fr) 2014-10-29

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EP11782444.1A Not-in-force EP2655021B1 (fr) 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique

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EP (1) EP2655021B1 (fr)
DE (1) DE102010063623A1 (fr)
RU (1) RU2013133711A (fr)
WO (1) WO2012084350A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN109834582B (zh) * 2019-02-18 2020-02-07 浙江机电职业技术学院 一种防弯曲同步对称自动磨床装置及使用方法
US11565394B2 (en) * 2019-10-28 2023-01-31 Snap-On Incorporated Double reduction gear train

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4489525A (en) * 1983-08-11 1984-12-25 Black & Decker Inc. Replaceable spindle lock system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3525208A1 (de) * 1984-07-16 1986-01-23 Japan Strage Battery Co. Ltd., Kyoto Untersetzungsgetriebe
US6102632A (en) * 1998-04-23 2000-08-15 Black & Decker Inc. Two speed right angle drill
DE10258863A1 (de) * 2002-12-17 2004-07-08 Robert Bosch Gmbh Handwerkzeugmaschinengetriebe und Handwerkzeugmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4489525A (en) * 1983-08-11 1984-12-25 Black & Decker Inc. Replaceable spindle lock system

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DE102010063623A1 (de) 2012-06-21
EP2655021A1 (fr) 2013-10-30
WO2012084350A1 (fr) 2012-06-28
RU2013133711A (ru) 2015-01-27

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