EP2358502B1 - Engrenage planétaire commutable dans une machine-outil portative - Google Patents

Engrenage planétaire commutable dans une machine-outil portative Download PDF

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Publication number
EP2358502B1
EP2358502B1 EP09736979.7A EP09736979A EP2358502B1 EP 2358502 B1 EP2358502 B1 EP 2358502B1 EP 09736979 A EP09736979 A EP 09736979A EP 2358502 B1 EP2358502 B1 EP 2358502B1
Authority
EP
European Patent Office
Prior art keywords
gear
stage
ring gear
planetary gear
planetary
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
EP09736979.7A
Other languages
German (de)
English (en)
Other versions
EP2358502A1 (fr
Inventor
Heiko Roehm
Dietmar Saur
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
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Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2358502A1 publication Critical patent/EP2358502A1/fr
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Publication of EP2358502B1 publication Critical patent/EP2358502B1/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 invention relates to a switchable planetary gear in a hand tool according to the preamble of claim 1.
  • Shifting between the gear stages takes place by means of a slide switch which is manually adjusted in the axial direction and in this case shifts a shift ring gear between a housing-fixed latching position and a non-latching position, wherein in the non-latching position, the shift ring gear is rotatably connected to a planet carrier 1st stage of the planetary gear and together with the planet carrier circulates.
  • the switching ring gear and the planet carrier 1st stage are out of engagement, at the same time the switching ring gear is rotationally coupled with planet gears of a planetary carrier second stage.
  • the EP 1 813 395 A1 shows a switchable planetary gear in a hand tool according to the preamble of claim 1.
  • the invention is based on the object, a switchable planetary gear in a hand tool with simple design measures in such a way that a large gap spread can be achieved.
  • the planetary gear in a hand tool, for example in a cordless screwdriver, the planetary gear axially one behind the other at least three planet carrier having associated planetary gears, which are to be coupled by means of an axially adjustable shift ring gear in at least two different gear ratios.
  • the shift ring gear In a first gear stage, the shift ring gear is rotationally coupled to a first-order planet carrier, whereas in the second gear step, the shift ring gear is latched fixed to the housing. In this housing-fixed position, the switching ring gear is rotationally coupled to the planetary gears on the planet carrier second stage and at the same time with the planetary gears third stage.
  • a larger gear spread is possible in comparison with embodiments of the prior art.
  • a gear spread greater than 5 can be achieved, so that the reduction of the slow gear is at least five times the reduction of the fast gear.
  • the girth spread is accompanied by the achievement of high torques in the slow gear. Another advantage is the fact that the gear spread can be realized even with a small diameter of the planetary stage and also only relatively few components are required. In addition, the large gear spread allows the use of smaller or weaker drive motors. Finally, due to the slower rotational speeds in the lower gear ratio, better control over the work result possible because the work progress between the stop operation and the actual stop of machining is reduced.
  • the gear reduction or the gear spread can be set on the design of the planet carrier, in particular the planet carrier second and third stage including the associated planetary gears.
  • both similar planet carrier and planetary gears in the second and third stage come into consideration, which in particular has the advantage that the switching ring gear on the inside of a uniform tooth geometry for engagement with both the planetary gears of the second stage and the planet gears third stage may have.
  • the hollow cylindrical Wegthohlrad is provided on its inside with a uniform locking contour or tooth geometry, with both a latching engagement with the adjacent planetary carrier and with the planetary gears second and third stage can be realized.
  • the planet carrier of the adjacent stage has the same outer diameter as the cylindrical envelope around the second and third stage planetary gears.
  • the shift ring gear must be adjusted axially between the gear steps.
  • a radially projecting from the housing actuating element is expediently provided, which is suitably designed as a slide switch, for example, such that the slide switch engages in a circumferential on the outside of the switching ring gear groove and during a movement of the Shift slide the switching ring gear is adjusted axially between the switching positions.
  • the switching ring gear In the first gear, in which the switching ring gear is located in the non-latching position with respect to the housing and is rotationally coupled to the adjacent planet carrier, for example, the first stage, there is also expediently a coupling between the switching ring and the planetary gears of both the second and the third Step. Due to the rotation between the adjacent planet carrier and the switching ring gear, the switching ring gear rotates relative to the housing at the same speed as the planet carrier. The second and the third stage are shut down due to the lock on the switching ring gear.
  • the shift ring gear is shifted into the second gear step in which the shift ring gear is latched fixed to the housing, then the shift ring gear and the adjacent planet carrier are in disengagement. At the same time, the planet gears of the second and third stages can rotate on the inner contour of the switching ring gear.
  • a fixedly connected to the housing locking ring is advantageously provided.
  • Heidelberghohlrad and locking ring have mutually corresponding locking elements which engage in locking engagement when the switching ring gear is moved axially in the direction of the locking ring, whereby the switching ring gear assumes its detent position.
  • the hand tool 1 for example a cordless screwdriver, comprises an electric drive motor 2, shown only schematically, whose motor shaft is coupled to a planetary gear 4 in a gear housing 3 for driving a spindle 6 rotatably mounted in the gear housing 4 may optionally be part of the motor housing.
  • the free end face of the spindle 6 is equipped with an external thread 7 for fixing a chuck into which a tool can be clamped.
  • the planetary gear 4 is made in four stages and can be switched between two gear ratios to change the reduction and torque ratio.
  • the planetary gear 4 includes planetary carrier 8, 9, 10 and 11, which form the first, second, third and fourth stage and which planetary gears 12, 13, 14 and 15 associated with corresponding stages.
  • the Plantetentennam 8 to 11 are coaxial with the longitudinal axis of the motor shaft 5 and the spindle. 6
  • a switching ring gear 16 is mounted axially displaceably in the housing 3.
  • the switching ring gear 16 is to be adjusted axially between the non-latching position shown and a housing-fixed latching position in which the switching ring gear 16 is in latching engagement with a latching ring 17 arranged fixed to the housing.
  • the illustrated axial position of the GmbHhohlrades 16, in which there is no latching engagement with the locking ring 17, represents the first gear stage with high rotational speed and low torque of the spindle.
  • axially displaced housing-side locking position in which a latching engagement between the switching ring gear 16 and the Rastring 17 is the transmission is in the second gear stage with low rotational speed and higher torque.
  • the switching ring gear 16 surrounds the planet carrier 8 first stage and the planetary gears 13 and 14 second and third stage, which are arranged on the corresponding planet carrier 9 and 10 second and third stage.
  • the Heidelberghohlrad 13 has on its inside a locking contour in the form of a toothing, with which the Heidelberghohlrad 13 is rotatably coupled in the illustrated first gear stage with the planet carrier 8 first stage, so that the Weghohlrad 13 relative to the housing 3, the same rotational movement as the planet carrier 8 exercises.
  • the planetary carrier 8 first stage has the same outer diameter as an envelope around the planet gears 13 and 14 second and third stage. This makes it possible to provide a hollow cylindrical trained Wegohlrad 16 with cylindrical inner jacket, which is suitably provided with a constant over the axial length of the switching ring gear axial locking contour or locking teeth, which with a corresponding toothing on the planet carrier 8 and the planetary gears 13 and 14 into engagement stands.
  • the shift ring gear 14 is moved axially from the position shown in which the shift ring gear is in non-latching position with the locking ring 17 in an engaged position with the locking ring, so that the switching ring gear 16 is in a housing-fixed locking position.
  • this detent position there is no more rotary coupling between the planet carrier 8 first stage and the switching ring gear 16.
  • the switching ring gear 16 is still an engaged position with the planetary gears 13 and 14 second and third stage, however, due to the housing-locking of the Circulating hollow wheel 16 rotate on the inside of the switching ring gear.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Claims (13)

  1. Engrenage planétaire commutable dans une machine-outil portative (1), qui présente plusieurs porte-satellites (8, 9, 10) avec des satellites associés (12, 13, 14) et qui peut être réglé entre au moins deux rapports de vitesses, les rapports de vitesses pouvant être enclenchés par le biais d'une couronne dentée de commutation réglable (16), la couronne dentée de commutation (16), dans un premier rapport de vitesse, étant accouplée en rotation à un porte-satellites (8), et la couronne dentée de commutation (16), dans un deuxième rapport de vitesse, étant encliquetée de manière fixée au boîtier, au moins deux étages planétaires (13, 14) situés axialement l'un derrière l'autre se trouvant à l'intérieur de la couronne dentée de commutation (16), caractérisé en ce que dans le deuxième rapport de vitesse, la couronne dentée de commutation (16) est accouplée en rotation aux satellites du deuxième et du troisième étage (13, 14) .
  2. Engrenage planétaire selon la revendication 1, caractérisé en ce que le côté intérieur de la couronne dentée de commutation (16) est pourvu d'un contour d'encliquetage pour l'encliquetage avec le porte-satellites du premier étage (8) et les satellites du deuxième et du troisième étage (13, 14).
  3. Engrenage planétaire selon la revendication 2, caractérisé en ce que le contour d'encliquetage de la couronne dentée de commutation (16) pour l'encliquetage avec les satellites du deuxième étage (13) est identique au contour d'encliquetage pour l'encliquetage avec les satellites du troisième étage (14).
  4. Engrenage planétaire selon la revendication 2 ou 3, caractérisé en ce que le contour d'encliquetage de la couronne dentée de commutation (16) pour l'encliquetage avec le porte-satellites du premier étage (8) est identique au contour d'encliquetage pour l'encliquetage avec les satellites du deuxième ou du troisième étage (13, 14).
  5. Engrenage planétaire selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les porte-satellites du deuxième et du troisième étage (9, 10) et les satellites associés (13, 14) présentent le même rapport de démultiplication.
  6. Engrenage planétaire selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les porte-satellites du deuxième et du troisième étage (9, 10) et les satellites associés (13, 14) présentent des rapports de démultiplication différents.
  7. Engrenage planétaire selon l'une quelconque des revendications 1 à 6, caractérisé en ce que dans le premier rapport de vitesse dans lequel la couronne dentée de commutation (16) est accouplée en rotation au porte-satellite adjacent (8), il est également établi un accouplement de la couronne dentée de commutation (16) avec les satellites du deuxième et du troisième étage (13, 14) .
  8. Engrenage planétaire selon l'une quelconque des revendications 1 à 7, caractérisé en ce que dans le premier rapport de vitesse, la couronne dentée de commutation (16) est accouplée en rotation au porte-satellites (8) du premier étage.
  9. Engrenage planétaire selon l'une quelconque des revendications 1 à 7, caractérisé en ce que dans le premier rapport de vitesse, la couronne dentée de commutation (16) est accouplée en rotation au porte-satellites (10) du troisième étage.
  10. Engrenage planétaire selon l'une quelconque des revendications 1 à 9, caractérisé en ce que pour réaliser le mouvement de commutation axial, il est prévu un coulisseau de commutation connecté à la couronne dentée de commutation (16), faisant saillie hors du boîtier (3).
  11. Engrenage planétaire selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la couronne dentée de commutation (16) est encliquetée dans la position d'encliquetage fixée au boîtier avec une bague d'encliquetage (17) qui est connectée fixement au boîtier (3).
  12. Engrenage planétaire selon l'une quelconque des revendications 1 à 11, caractérisé en ce que la démultiplication de la vitesse lente vaut au moins cinq fois la démultiplication de la vitesse rapide.
  13. Machine-outil portative comprenant un engrenage planétaire (4) selon l'une quelconque des revendications 1 à 12.
EP09736979.7A 2008-11-17 2009-10-21 Engrenage planétaire commutable dans une machine-outil portative Active EP2358502B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008043795A DE102008043795A1 (de) 2008-11-17 2008-11-17 Schaltbares Planetengetriebe in einer Handwerkzeugmaschine
PCT/EP2009/063776 WO2010054916A1 (fr) 2008-11-17 2009-10-21 Engrenage planétaire commutable dans une machine-outil portative

Publications (2)

Publication Number Publication Date
EP2358502A1 EP2358502A1 (fr) 2011-08-24
EP2358502B1 true EP2358502B1 (fr) 2018-05-23

Family

ID=41445408

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09736979.7A Active EP2358502B1 (fr) 2008-11-17 2009-10-21 Engrenage planétaire commutable dans une machine-outil portative

Country Status (6)

Country Link
US (1) US8545363B2 (fr)
EP (1) EP2358502B1 (fr)
CN (1) CN102216033A (fr)
DE (1) DE102008043795A1 (fr)
RU (1) RU2011124151A (fr)
WO (1) WO2010054916A1 (fr)

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DE102009054927A1 (de) * 2009-12-18 2011-06-22 Robert Bosch GmbH, 70469 Handwerkzeugmaschine, insbesondere Akkuhandwerkzeugmaschine
DE102009054931A1 (de) * 2009-12-18 2011-06-22 Robert Bosch GmbH, 70469 Handgeführtes Elektrowerkzeug mit einer Drehmomentkupplung
DE202011110376U1 (de) * 2011-01-03 2014-01-17 Robert Bosch Gmbh Planetengetriebe für eine Werkzeugmaschine
CA3012253A1 (fr) * 2011-03-11 2012-12-13 Stanley D. Winnard Dispositif d'entrainement portable
DE102011081661B4 (de) 2011-08-26 2023-11-30 Robert Bosch Gmbh Schaltbares Getriebe für eine Handwerkzeugmaschine
US9283667B2 (en) 2012-01-11 2016-03-15 Black & Decker Inc. Power tool with torque clutch
US9233461B2 (en) 2012-02-27 2016-01-12 Black & Decker Inc. Tool having multi-speed compound planetary transmission
US9108312B2 (en) * 2012-09-11 2015-08-18 Milwaukee Electric Tool Corporation Multi-stage transmission for a power tool
WO2014062868A1 (fr) 2012-10-19 2014-04-24 Milwaukee Electric Tool Corporation Marteau-perforateur
DE102015110504A1 (de) * 2015-06-30 2017-01-19 Festool Gmbh Hand-Werkzeugmaschine
DE102017211779A1 (de) * 2016-07-11 2018-01-11 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
DK3496900T3 (da) * 2016-08-08 2021-01-04 Hytorc Division Unex Corp Apparat til stramning af gevindfastgørelse
CN109027147B (zh) * 2018-08-23 2023-11-17 浙江皇冠电动工具制造有限公司 手持式工具机的传动装置
US11565394B2 (en) 2019-10-28 2023-01-31 Snap-On Incorporated Double reduction gear train
CN115882661A (zh) * 2021-09-29 2023-03-31 杭州九阳小家电有限公司 一种运行稳定的食品加工机

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Also Published As

Publication number Publication date
WO2010054916A1 (fr) 2010-05-20
CN102216033A (zh) 2011-10-12
US8545363B2 (en) 2013-10-01
DE102008043795A1 (de) 2010-05-20
RU2011124151A (ru) 2012-12-27
US20110275471A1 (en) 2011-11-10
EP2358502A1 (fr) 2011-08-24

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