EP2655021A1 - Système de transmission pour un outil électrique et outil électrique - Google Patents

Système de transmission pour un outil électrique et outil électrique

Info

Publication number
EP2655021A1
EP2655021A1 EP11782444.1A EP11782444A EP2655021A1 EP 2655021 A1 EP2655021 A1 EP 2655021A1 EP 11782444 A EP11782444 A EP 11782444A EP 2655021 A1 EP2655021 A1 EP 2655021A1
Authority
EP
European Patent Office
Prior art keywords
gear
additional
toothing
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.)
Granted
Application number
EP11782444.1A
Other languages
German (de)
English (en)
Other versions
EP2655021B1 (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
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 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

Links

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 gear 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 planetary gear supported 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.
  • 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.
  • 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.
  • it is under the
  • Transmission ratio IPx a planetary gear stage in particular a so-called state translation, i. understood the negative transmission ratio between the ring gear and the sun gear of the planetary gear stage.
  • state translation i. understood the negative transmission ratio between the ring gear and the sun gear of the planetary gear stage.
  • Ratios of the number of teeth of the ring gear relative to the sun gear are to be understood as meaning in particular axial or lateral extensions in the range between a few millimeters to a few centimeters, preferably axially between 3 and 20 mm or laterally between 1 and 15 cm.
  • the parallel alignment of the input and output shaft usually has an axial-serial, one behind the other arrangement of engine and
  • the axial-serial arrangement proves to be disadvantageous, from an ergonomic point of view, in particular with regard to mass distribution.
  • 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 an angular gear, preferably a crown gear.
  • an additional gear is understood in particular a gear, which is not part of a planetary gear set.
  • the additional gear on an axis of rotation, which is aligned at an angle Wl 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.
  • Gear arrangement with a planetary gear stage and the angle gear lies between 2.8 and 52, in particular between 3.5 and 32.
  • the gear assembly of 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 assembly in relation to a Utilization unit of the power tool.
  • the additional gear is designed as a crown wheel.
  • the toothing of the additional gear is formed as a crown toothing and the additional toothing of the member 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.
  • Gear in particular the relative axial position of the planetary gear relative to the axis of rotation of the additional gear.
  • 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.
  • 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 planetary carrier or a sun gear, relative to an outer rest system can be fixed.
  • Under an external 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.
  • the skilled person knows this a number of suitable non-positive and / or positive-working brake and / or
  • Coupling devices such as friction brakes, friction clutches, claws or detent couplings, 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, then it is possible with the planetary gearset according to the invention
  • a power tool in particular an electric hand tool, with an electric drive unit for generating a rotational movement of a
  • Drive shaft and a rotationally driven output shaft of a use unit can be the rotational movement of the drive shaft to the output shaft by means of a
  • Fig. 1 is a schematic view of a first embodiment
  • FIG. 2 shows a schematic view of a second embodiment as a variant of the embodiment according to FIG. 1
  • Fig. 3 is a schematic view of a third embodiment 4 shows a schematic view of a fourth exemplary embodiment as a variant of the embodiment according to FIG. 3
  • Fig. 5 is a schematic view of a fifth embodiment
  • Fig. 6 is a schematic view of a sixth embodiment
  • Fig. 7 is a schematic view of a seventh embodiment with a 2-stage planetary gear
  • FIG. 8 shows a schematic view of an eighth exemplary embodiment as a variant of the embodiment according to FIG. 7
  • Fig. 9 is a schematic view of a ninth embodiment
  • FIG. 10 shows a schematic view of a tenth embodiment as a variant of the embodiment according to FIG. 9
  • FIG. 11 is a schematic view of an electric hand tool with a
  • FIG. 1 shows a schematic view of a first exemplary embodiment of a gear arrangement 10 according to the invention for a power tool, in particular for an electric hand tool, which has a planetary gear 12 and a planetary gear 12
  • Planetary gear 12 operatively connected angular gear 14 includes.
  • 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 of FIG. 1 on 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 26th and a ring gear 30, which is in operative connection with the planetary gears 26 via an inner active surface 28, wherein the planet carrier 20, the sun gear 18 and the ring gear 30 form the members 32 of a planetary gear stage 34.
  • 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 26th and a ring gear 30, which is in operative connection with the planetary gears 26 via an inner active surface 28, wherein the planet carrier 20, the sun gear 18 and the ring gear 30 form the members 32 of a planetary gear stage 34.
  • Design of the planetary gear 16 may have only one or three or more planetary gears 26.
  • the active surfaces 22, 24 and 28 of the respective wheels bear toothings, preferably serrations 36a, 36b, 36c, via which the active compounds are produced for transmitting rotational movement between the respective members of the planetary gear set 16.
  • 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 set 16 is arranged in the embodiment of FIG. 1 about a first axis of rotation 38 rotatably mounted on a sun gear 40 and forms an input or output side 42, 43 of the transmission assembly 10 of the invention is preferably the sun gear shaft 40 in a storage device 44th , For example, a sliding, needle and / or roller bearing, supported supporting forces against occurring.
  • the bearing device 44 is shown in dashed lines in Fig. 1, 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 stationary element 48, for example, a gear assembly 10 at least partially comprising 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 toothing 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 of FIG. 1 in this case 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 Wl, in particular is aligned substantially perpendicular to this.
  • the additional toothing 58 is formed in the embodiment of FIG. 1 as a straight or helical spur gear teeth 59, which meshes with a correspondingly formed crown gear teeth 63 as teeth 62 of the additional gear 64.
  • the additional gear 64 may therefore also be referred to as crown gear 70.
  • 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.
  • Ratio IW of the angular gear 14 is calculated from the ratio of the number of teeth of the additional teeth 58 relative to the teeth 62nd
  • a total ratio of the gear arrangement according to FIG. 1 thus results from the product of (1-IP1) and IW, where IP1 is the state translation of the one
  • FIG. 2 illustrates a variant of the first
  • the additional gear 64 which meshes with the additional teeth 58, 59, designed as a conical crown gear 72, wherein an opening angle WK of the conical crown gear 72 twice the angle Wl between the rotation axis 60 and the angular gear shaft 68 corresponds.
  • angles Wl between 10 ° and 80 ° are preferred, more preferably between 50 ° and 80 °.
  • the gear arrangement 10 according to FIG. 2 otherwise corresponds to the embodiment according to FIG. 1, to the description of which reference is made at this point.
  • FIG. 3 a further modification of the embodiment of FIG. 1 is shown as a third embodiment.
  • the embodiment of Fig. 3 the embodiment of Fig. 3, the
  • Planet carrier 20 no wave-like nose on, but the additional teeth 58 is as a spur gear 59 on an outer circumferential surface 74 of the
  • Gear wheel 64 which is formed as in the example of FIG. 1 as a crown wheel, substantially perpendicular to the axis of rotation 60 of the planet carrier 20.
  • FIG. 3 it may also be advantageous embodiment of FIG. 3 with a conical crown gear 72, as shown in FIG to combine such that the angle Wl the
  • Rotary axes 60, 66 between 10 ° and 80 °, more preferably between 50 ° to 80 °.
  • the crown gear 76 is provided to mesh with a spur gear teeth designed as a toothed 62 of the additional gear 64, 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 Wl between 10 ° and 90 ° - Fig. 4 shows the orientation at 90 °.
  • Gear ratios IW of the angular gear 14 without strong intervention in example space parameters of the gear assembly 10 realize.
  • 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 on the wave-like nose 56 a wheel-shaped structure 82 supporting the additional toothing 62 is supported.
  • the wheel-shaped structure 82 carries the additional toothing 62 on an outer surface 84 which is conical in this example which as
  • the additional gear 64 is formed as a spur gear 80 analogous to FIG.
  • 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 Wl, which corresponds to half of the opening angle WK of the conical outer surface 84.
  • the angle Wl 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 additional toothing 58 is provided on a peripheral surface 92 of the ring gear 30.
  • the ring gear 30 is rotatable relative to the rest system 50, in particular freely rotatably mounted.
  • Coupling device 94 for releasably securing the planet carrier 20 against the rotational movement 46 by means of braking and / or blocking effect as a fixing means 52 is provided. If the planet carrier 20 is braked or preferably fixed in relation to the stationary element 48, 49, the ring gear 30 is brought to a rotational movement 46 via the meshing teeth 36b, 36c
  • 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 teeth 58 on the ring gear 30 is preferably formed as shown in FIG. 6 as a straight or helical spur toothing 98 and is in
  • Fig. 7 shows a building on the first embodiment of FIG. 1
  • the second planetary gear stage 34a includes a sun gear 18a, a
  • Planet gears 26a supporting planet carrier 20a and a ring gear 30a.
  • the ring gear 34a is connected to the stationary element 48, 49 as a rest system 50.
  • the planet carrier 20a in turn has a wave-shaped nose 56a, which forms the sun gear 18 of the planetary gear stage 34.
  • Transmission arrangement 10 according to Fig. 7 only in so far from the embodiment of FIG. 1, as 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 combines essential features of the embodiments according to FIGS. 6 and 7.
  • the planetary gear stage 34 as is known from Fig. 6, a second planetary gear stage 34a shown in FIG. 7 upstream, the operation within the meaning of the invention, however, remains
  • fastening means 52 shown in FIGS. 7 and 8 as substantially rigid connections with the stationary element 48, 49 may also be a combination with at least one brake and / or clutch device 94 may be advantageous, as is known from Fig. 6.
  • Fig. 9 shows a further, fundamental variant of an inventive
  • the additional toothing 58 is provided on the sun gear shaft 40.
  • the additional toothing 58 is formed as a straight or helical spur toothing 59, which with the complementary crown gear 63rd
  • the additional toothing 58 is designed as a conical crown wheel toothing 100 similar to that of FIG. 5, for example.
  • 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 Wl, 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 gear arrangement 10 according to the invention in an electric hand tool 200, in particular an electric screwdriver, a drill, a percussion drill, a
  • the electric hand tool 200 comprises in a housing 201 a
  • Drive rotational axis 210 extends.
  • 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.
  • Tool holder 220 forms together with a tool 222 and the
  • 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 gear assembly 10 according to the invention in the application example of FIG. 11 corresponds to the embodiment of FIG. 2, wherein the sun gear 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 on the drive shaft 206 associated side of the transmission assembly 10 is arranged.
  • the additional gear 68 is rotatably connected to the output shaft 212 in the example of FIG. 11.
  • Gear arrangement 12 is arranged.

Landscapes

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

Abstract

L'invention concerne un système de transmission (10) pour le transfert d'un mouvement de rotation dans un outil électrique, en particulier un outil électrique à main, comprenant un engrenage planétaire (12) doté d'un jeu de satellites (16) et une roue dentée (64) supplémentaire. Selon l'invention, au moins un organe (18, 20, 30; 32) de l'engrenage planétaire (12) porte une denture (58) supplémentaire destinée à s'engrener dans une denture (62) de la roue dentée (64) supplémentaire, l'organe (18, 20, 30; 32) et la roue dentée (64) supplémentaire formant un engrenage angulaire (14).
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 true EP2655021A1 (fr) 2013-10-30
EP2655021B1 EP2655021B1 (fr) 2014-10-29

Family

ID=44971037

Family Applications (1)

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

Country Status (4)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
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

Family Cites Families (4)

* 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
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012084350A1 *

Also Published As

Publication number Publication date
RU2013133711A (ru) 2015-01-27
EP2655021B1 (fr) 2014-10-29
DE102010063623A1 (de) 2012-06-21
WO2012084350A1 (fr) 2012-06-28

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