EP3147078B1 - Machine-outil portative - Google Patents

Machine-outil portative Download PDF

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Publication number
EP3147078B1
EP3147078B1 EP16189706.1A EP16189706A EP3147078B1 EP 3147078 B1 EP3147078 B1 EP 3147078B1 EP 16189706 A EP16189706 A EP 16189706A EP 3147078 B1 EP3147078 B1 EP 3147078B1
Authority
EP
European Patent Office
Prior art keywords
gear
ring
ring gear
planet carrier
toothing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16189706.1A
Other languages
German (de)
English (en)
Other versions
EP3147078A1 (fr
Inventor
Jochen Erhardt
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.)
Hilti AG
Original Assignee
Hilti AG
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 Hilti AG filed Critical Hilti AG
Publication of EP3147078A1 publication Critical patent/EP3147078A1/fr
Application granted granted Critical
Publication of EP3147078B1 publication Critical patent/EP3147078B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • 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 present invention relates to a handheld power tool, in particular an electric screwdriver according to the preamble of claim 1 and as shown in FIG EP 2 631 038 A1 known.
  • the hand machine tool according to the invention is equipped with the features according to claim 1. Further modifications can be found in the subclaims.
  • the planetary gear with the switching ring can be built compactly.
  • Fig. 1 shows an electric screwdriver 1 as an example of a handheld power tool.
  • the electric screwdriver 1 has a tool holder 2 in which a rotating tool 3, for example a drill or a screwdriver bit, can be inserted and locked.
  • An electric motor 4 drives the tool holder 2 about a working axis 5 .
  • the electric motor 4 is arranged in a machine housing 6 to which a handle 7 for holding and guiding the electric screwdriver 1 is attached during operation.
  • the user can put the electric screwdriver 1 into operation by means of a system switch 8.
  • the electric motor 4 is supplied with power when the user operates the system switch 8.
  • a The power source can be a battery pack 9 attached to the machine housing 6 or the handle 7 or a mains connection.
  • a switchable planetary gear 10 is arranged in the drive train between the electric motor 4 and the tool holder 2.
  • a slide 11 outside the machine housing 6 actuates the planetary gear 10.
  • the slide 11 can be shifted by the user into a first switching position or a second switching position.
  • the slide 11 can be moved along the transmission axis 12 or transversely to the transmission axis 12 , in the latter case a shift gate converts the circumferential movement into an axial movement.
  • the planetary gear 10 changes its reduction ratio depending on the switching position of the slide 11.
  • the planetary gear 10 has a sun gear 13, a planet carrier 14 with several planet gears 15 and a first ring gear 16 arranged on a gear axis 12.
  • the sun gear 13 is preferably arranged on the drive side; the first ring gear 16 is arranged on the output side.
  • the sun gear 13 can, for example, be coupled directly to the electric motor 4.
  • On the exemplary first ring gear 16 a gear 17 is arranged, which meshes with a further gear.
  • the planet carrier 14 has three shafts 18 or bearings, on each of which a planet gear 15 is rotatably mounted about the axis of the shaft 18.
  • the number of planet gears 15 is exemplary and is preferably in the range between three and seven planet gears 15.
  • the planet gears 15 each have two different toothings 19, 20.
  • the first toothing 19 has a larger diameter than the second toothing 20.
  • the number of teeth of the first toothing 19 and the second toothing 20 is the same.
  • the first toothing 19 meshes with the sun gear 13 and the first ring gear 16.
  • a width of the first toothing 19 is preferably equal to a width of the sun gear 13 and the toothing of the first ring gear 16. The width specifies the dimension along the transmission axis 12 .
  • the second toothing 20 can be wider than the first toothing 19 .
  • the second toothing 20 meshes neither with the sun gear 13 nor with the first ring gear 16.
  • a second ring gear 21 is also arranged coaxially on the transmission axis 12.
  • the second ring gear 21 is freely rotatable with respect to the first ring gear 16.
  • the first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance.
  • the second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15.
  • the second ring gear 21 is preferably as wide as the second toothing 20.
  • An outer diameter of the second ring gear 21 is smaller than an outer diameter of the first ring gear 16.
  • the outer diameter of the second ring gear 21 and an outer diameter of the planetary carrier 14 can advantageously be identical.
  • the second ring gear 21 and the planet carrier 14 are arranged adjacent along the gear axis 12 at a fixed, unchangeable distance.
  • the planetary gear 10 is arranged in a gear housing 22 which is fastened in the machine housing 6 or is formed by the machine housing 6 .
  • the planetary gear 10 has a switching ring 23 which is displaceable along the gear axis 12.
  • the switching ring 23 is coupled to the slide 11 in such a way that the switching ring 23 is in a first position ( Figs. 2, 4 and 5 ) reaches when the slide 11 is in the first switching position and the second position ( Figures 6, 7 and 8 ) arrives when the slide 11 is in the second switching position.
  • the connection of the switching ring 23 to the slide 11 can take place via a rigid linkage or via tracking springs.
  • the switching ring 23 is prevented from rotating about the transmission axis 12 in the transmission housing 22 .
  • the switching ring 23 can have radial projections 24 which engage in axially extending grooves 25 in the gear housing 22.
  • the radial projections 24 have, for example, a semi-cylindrical cross section, but their cross section can also have a different shape, for example prismatic, rectangular.
  • the grooves 25 have a corresponding complementary cross section, and to allow a guide along the transmission axis 12 of rotation in order to inhibit the transmission axis 12th
  • the switching ring 23 can have axially extending grooves and the gear housing can have radial projections which engage in one another analogously.
  • the switching ring 23 overlaps along the gear axis 12 with the planet carrier 14; In the second position, the shift ring 23 overlaps along the gear axis 12 with the second ring gear 21.
  • the shift ring 23 which is prevented from rotating, blocks either the planet carrier 14 or the second ring gear 21 from rotating about the gear axis 12. The reduction of the planetary gear 10 changes accordingly .
  • the exemplary switching ring 23 has claws 26 projecting radially inward.
  • the second ring gear 21 has recesses 27 complementary to the claws 26 and the planetary carrier 14 has recesses 28 complementary to the claws 26 .
  • the switching ring 23 engages with the claws 26 either exclusively in the second ring gear 21 or in the planet carrier 14 .
  • the shape of the claws 26 and associated recesses 27, 28 are designed in such a way that a sufficient form fit is formed for transmitting a torque from the switching ring 23 to the second ring gear 21 or the planet carrier 14 .
  • the exemplary jaws 26 have one semi-cylindrical cross-section, the cross-section can also be prismatic, rectangular, etc.
  • the switching ring 23 can be provided with cutouts, into which claws of the second ring gear 21 and claws of the planet carrier 14 engage.
  • the switching ring 23 is arranged between the second ring gear 21 and the planet carrier 14 and engages either with end-shaped claws 26 in the second ring gear 21 or in the planet carrier 14 to keep one of the two elements rotating to prevent the transmission axis 12 .
  • FIGS. 9 to 12 show an embodiment of a planetary gear 29.
  • the planetary gear 29 has on a transmission axis 12 is arranged a sun gear 13, a planet carrier 14 having a plurality of planet gears 15 and a first ring gear 16.
  • the planet carrier 14 has four shafts 18 and bearings, on each of which a planetary gear 15 to the axis of the shaft 18 is rotatably mounted.
  • the planet gears 15 each have two different toothings 19, 20.
  • the first toothing 19 has a larger diameter than the second toothing 20.
  • the number of teeth of the first toothing 19 and the second toothing 20 is the same.
  • the first toothing 19 meshes with the sun gear 13 and the first ring gear 16.
  • a second ring gear 21 is arranged coaxially on the transmission axis 12.
  • the second ring gear 21 is freely rotatable with respect to the first ring gear 16.
  • the first ring gear 16 and the second ring gear 21 are arranged adjacently along the transmission axis 12 and at a fixed, unchangeable distance.
  • the second ring gear 21 permanently meshes with the second toothing 20 of the planetary gears 15.
  • the planetary gear 29 has a switching ring 30 which is displaceable along the gear axis 12.
  • the switching ring 23 is prevented from rotating by cams 31 engaging in the gear housing 22.
  • the switching ring 30 is coupled to the slide 11 in such a way that the switching ring 30 reaches a first position when the slide 11 is in the first switching position and that moves into a second position when the slide 11 is in the second switching position.
  • the switching ring 23 has a first spur toothing 32 which, in the first position, engages in a spur toothing 33 of the second ring gear 21.
  • the switching ring 23 has a second spur toothing 34 which, in the second position, engages in a spur toothing 35 of the planet carrier 14.
  • the switching ring 23 is accordingly arranged between the second ring gear 21 and the planet carrier 14 or their spur teeth 33, 35 . In the first position, the switching ring 23 inhibits the second ring gear 21 from rotating and releases the planet carrier 14 to rotate; In the second position, the switching ring 23 prevents the planet carrier 14 from rotating and releases the second ring gear 21 to rotate.

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

Claims (4)

  1. Machine-outil portative (1) comprenant
    un porte-outil (2) prévu pour fixer un outil,
    un moteur électrique (4) pour entraîner le porte-outil (2),
    une transmission planétaire commutable (10) qui est commutée dans un boîtier de transmission (22) entre le porte-outil (2) et le moteur électrique (4),
    la transmission planétaire (10) présentant une roue solaire (13), un porte-satellites (14), un ensemble de pignons planétaires (15) qui sont supportés sur le porte-satellites (14), une première couronne dentée (16) et une deuxième couronne dentée (21), les pignons planétaires (15) présentant une première denture (19) s'engrenant avec la première couronne dentée (16) et la roue solaire (13) et une deuxième denture (20) s'engrenant avec la deuxième couronne dentée (21),
    une bague de commutation (23) qui est déplaçable axialement dans le boîtier de transmission (22) entre une première position et une deuxième position, la bague de commutation (23), dans la première position, s'engageant dans la deuxième couronne dentée (21), la bague de commutation (23) étant disposée de manière solidaire en rotation dans le boîtier de transmission (22),
    un élément d'actionnement (11) pouvant être actionné manuellement, lequel, dans une première position, force la bague de commutation dans la première position et lequel, dans une deuxième position, force la bague de commutation dans la deuxième position,
    la première denture (19) présentant un premier diamètre et la deuxième denture (20) présentant un deuxième diamètre, le premier diamètre étant plus grand que le deuxième diamètre,
    caractérisée en ce que la bague de commutation (23), dans la deuxième position, s'engage dans le porte-satellites (14) et
    la deuxième denture (19) et la première denture (20) présentent le même nombre de dents.
  2. Machine-outil portative selon la revendication 1, caractérisée en ce que la bague de commutation (23) est disposée entre la deuxième couronne dentée (21) et le porte-satellites (14) et dans la première position, s'engage dans la deuxième couronne dentée (21), et dans la deuxième position, s'engage dans le porte-satellites (14).
  3. Machine-outil portative selon la revendication 2, caractérisée en ce que la bague de commutation (23) présente une première denture frontale (32) tournée vers la deuxième couronne dentée (21) et une deuxième denture frontale (34) tournée vers le porte-satellites (14), la deuxième couronne dentée (21) présentant une denture frontale (33) complémentaire de la première denture frontale (32) et le porte-satellites (14) présentant une denture frontale (35) complémentaire de la deuxième denture frontale (34).
  4. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une distance axiale entre la première couronne dentée (16) et la deuxième couronne dentée (21) est invariable.
EP16189706.1A 2015-09-22 2016-09-20 Machine-outil portative Active EP3147078B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15186196.0A EP3147077A1 (fr) 2015-09-22 2015-09-22 Machine-outil portative

Publications (2)

Publication Number Publication Date
EP3147078A1 EP3147078A1 (fr) 2017-03-29
EP3147078B1 true EP3147078B1 (fr) 2021-02-24

Family

ID=54196834

Family Applications (2)

Application Number Title Priority Date Filing Date
EP15186196.0A Withdrawn EP3147077A1 (fr) 2015-09-22 2015-09-22 Machine-outil portative
EP16189706.1A Active EP3147078B1 (fr) 2015-09-22 2016-09-20 Machine-outil portative

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP15186196.0A Withdrawn EP3147077A1 (fr) 2015-09-22 2015-09-22 Machine-outil portative

Country Status (1)

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EP (2) EP3147077A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017119807A1 (de) * 2017-08-29 2019-02-28 Festool Gmbh Hand-Werkzeugmaschine
DE102017119808A1 (de) * 2017-08-29 2019-02-28 Festool Gmbh Hand-Werkzeugmaschine
DE102018131747A1 (de) 2018-12-11 2020-06-18 Schaeffler Technologies AG & Co. KG Planetengetriebe mit über Planetenräder schaltbaren Planetenstufen
DE102019220245A1 (de) * 2019-12-19 2021-06-24 Robert Bosch Gmbh Handwerkzeugmaschine mit einem Planetengetriebe
CN113446364B (zh) * 2021-03-25 2022-03-08 深圳市汇能达塑料有限公司 一种用于台式料理机的行星齿轮箱结构

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8460153B2 (en) * 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
TWM419843U (en) * 2011-04-14 2012-01-01 Trinity Prec Technology Co Ltd Multi-stage speed change mechanism
TWM420614U (en) * 2011-07-18 2012-01-11 Trinity Prec Technology Co Ltd Multi-stage gear shifting device
US9233461B2 (en) * 2012-02-27 2016-01-12 Black & Decker Inc. Tool having multi-speed compound planetary transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3147077A1 (fr) 2017-03-29
EP3147078A1 (fr) 2017-03-29

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