EP2358502A1 - Switchable planetary gear set in a handheld machine tool - Google Patents

Switchable planetary gear set in a handheld machine tool

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Publication number
EP2358502A1
EP2358502A1 EP09736979A EP09736979A EP2358502A1 EP 2358502 A1 EP2358502 A1 EP 2358502A1 EP 09736979 A EP09736979 A EP 09736979A EP 09736979 A EP09736979 A EP 09736979A EP 2358502 A1 EP2358502 A1 EP 2358502A1
Authority
EP
European Patent Office
Prior art keywords
gear
stage
planetary
ring gear
switching ring
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
EP09736979A
Other languages
German (de)
French (fr)
Other versions
EP2358502B1 (en
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
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 EP2358502A1 publication Critical patent/EP2358502A1/en
Application granted granted Critical
Publication of EP2358502B1 publication Critical patent/EP2358502B1/en
Active 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
    • 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.
  • the planetary gearbox reduces the relatively high engine speed into a useful speed range of the work spindle for the application.
  • Such planetary transmissions are typically designed with two ratios which allow a choice between low speed, high torque, and higher torque with lower torque.
  • the shifting between the gear stages takes place with the aid of a slide switch, which is manually adjusted in the axial direction and in this case displaces a switching ring gear between a housing-fixed latching position and a non-latching position, wherein in the non-latching position the switching ring gear is connected to a planet carrier 1.
  • Stage of the planetary gear is rotatably connected and rotates together with the planet carrier. In the housing-fixed detent position, however, 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 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 gear spread can be achieved.
  • the embodiment according to the invention is a switchable piano-type transmission in a hand-held power tool, for example in a battery-powered
  • Screwdriver wherein 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 switching 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 ratio 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 goes with a high torque in the slow
  • 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 planetary carrier of the adjacent stage has the same outer diameter as the cylindrical envelope end about the planet wheels of the second and third stages.
  • 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 expediently designed as a slide switch det, 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.
  • Example of the first stage is rotationally coupled, there is expediently also a coupling between the switching ring gear and the planet gears of both the second and the third stage. Due to the rotation between the adjacent planet carrier and the switching ring gear, the Wegrad 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.
  • Locking position and a non-latching position is to be adjusted axially.
  • the power 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 gearbox 3 for driving a spindle 6 rotatably mounted in the gearbox housing.
  • 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 1 1, which form the first, second, third and fourth stage and which planetary gears 12, 13, 14 and 15 associated with corresponding stages.
  • the Plantetentenis 8 to 1 1 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 between the illustrated non-latching position and a housing fixed
  • Locking position to adjust axially in which the switching ring gear 16 is in locking engagement with a locking ring 17 arranged fixed to the housing.
  • the illustrated axial position of the Heidelberghohlrades 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 latching position in which a latching engagement between the switching ring gear 16th and the detent ring 17, the transmission is in the second speed 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 latching contour in the form of a toothing, with which the Weghohlrad 13 is rotatably coupled in the illustrated first gear stage with the planet carrier 8 first stage, so that the switching ring gear 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.
  • the switching ring gear 14 is moved from the illustrated position in which the switching ring gear is in non-latching position with the locking ring 17, axially in an engaged position with the locking ring, so that the switching ring gear 16 is in a housing-fixed locking position. In this detent position there is no more rotary coupling between the planet carrier 8 first stage and the switching ring gear 16. In contrast, 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)

Abstract

A switchable planetary gear set in a handheld machine tool (1) has a plurality of planet carriers (8, 9, 10) with associated planet gears (12, 13, 14) and can be adjusted between at least two gear stages, wherein the gear stages can be engaged by means of an adjustable switching ring gear (16). At least three planet carriers (8, 9, 10) with associated planet gears (12, 13, 14) are provided so as to be situated axially one behind the other, wherein in a position in which it is fixed with respect to a housing, the switching ring gear (16) is rotationally coupled to the planet gears on the planet carrier of the second stage (13) and simultaneously to the planet gears on the planet carrier of the third stage (14).

Description

Beschreibung description
Titeltitle
Schaltbares Planetengetriebe in einer HandwerkzeugmaschineSwitchable planetary gear in a hand tool
Die Erfindung bezieht sich auf ein schaltbares Planetengetriebe in einer Handwerkzeugmaschine nach dem Oberbegriff des Anspruches 1.The invention relates to a switchable planetary gear in a hand tool according to the preamble of claim 1.
Stand der TechnikState of the art
Aus der DE 10 2004 058 809 A1 ist eine als Akku-Schrauber ausgeführte Handwerkzeugmaschine bekannt, die als Antriebseinheit einen elektrischen Antriebsmotor aufweist, der über ein mehrstufiges Planetengetriebe eine im Gehäuse drehbar gelagerte Werkzeugaufnahme zur Aufnahme eines Werkzeugs antreibt.From DE 10 2004 058 809 A1 a executed as a cordless screwdriver hand tool is known, which has an electric drive motor as a drive unit, which drives a rotatably mounted in the housing tool holder for receiving a tool via a multi-stage planetary gear.
Das Planetengetriebe untersetzt die verhältnismäßig hohe Motordrehzahl in einen für die Anwendung sinnvollen Drehzahlbereich der Arbeitsspindel. Derartige Planetengetriebe sind typischerweise mit zwei Gangstufen ausgeführt, die eine Wahl zwischen langsamer Umdrehungsgeschwindigkeit mit hohem Drehmoment und höherer Umdrehungsgeschwindigkeit mit geringerem Drehmoment erlaubt. Das Schalten zwischen den Gangstufen erfolgt mithilfe eines Schaltschiebers, der manuell in Achsrichtung verstellt wird und hierbei ein Schalthohlrad zwischen einer gehäusefesten Rastposition und einer Außerrastposition verschiebt, wobei in der Außerrastposition das Schalthohlrad mit einem Planetenträger 1 . Stufe des Planetengetriebes drehverbunden ist und gemeinsam mit dem Planetenträger umläuft. In der gehäusefesten Rastposition stehen dagegen das Schalthohlrad und der Planetenträger 1. Stufe außer Eingriff, zugleich ist das Schalthohlrad mit Planetenrädern eines Planetenträgers zweiter Stufe drehgekoppelt.The planetary gearbox reduces the relatively high engine speed into a useful speed range of the work spindle for the application. Such planetary transmissions are typically designed with two ratios which allow a choice between low speed, high torque, and higher torque with lower torque. The shifting between the gear stages takes place with the aid of a slide switch, which is manually adjusted in the axial direction and in this case displaces a switching ring gear between a housing-fixed latching position and a non-latching position, wherein in the non-latching position the switching ring gear is connected to a planet carrier 1. Stage of the planetary gear is rotatably connected and rotates together with the planet carrier. In the housing-fixed detent position, however, 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.
Offenbarung der Erfindung Von diesem Stand der Technik ausgehend liegt der Erfindung die Aufgabe zu Grunde, ein schaltbares Planetengetriebe in einer Handwerkzeugmaschine mit einfachen konstruktiven Maßnahmen so auszubilden, dass eine große Gang- spreizung erzielt werden kann.Disclosure of the invention Based on this prior art, 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 gear spread can be achieved.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruches 1 gelöst. Die Unteransprüche geben zweckmäßige Weiterbildungen an.This object is achieved with the features of claim 1. The dependent claims indicate expedient developments.
Bei der erfindungsgemäßen Ausführung handelt es sich um ein schaltbares PIa- netengetriebe in einer Handwerkzeugmaschine, beispielsweise in einem Akku-The embodiment according to the invention is a switchable piano-type transmission in a hand-held power tool, for example in a battery-powered
Schrauber, wobei das Planetengetriebe axial hintereinanderliegend mindestens drei Planetenträger mit zugeordneten Planetenrädern aufweist, die mithilfe eines axial verstellbaren Schalthohlrades in mindestens zwei verschiedenen Gangstufen zu koppeln sind. In einer ersten Gangstufe ist das Schalthohlrad mit einem Planetenträger erster Stufe drehgekoppelt, wohingegen in der zweiten Gangstufe das Schalthohlrad gehäusefest verrastet ist. In dieser gehäusefesten Position ist das Schalthohlrad mit den Planetenrädern auf dem Planetenträger zweiter Stufe und zugleich mit den Planetenrädern dritter Stufe drehgekoppelt.Screwdriver, wherein 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 switching ring gear in at least two different gear ratios. 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.
Da sich innerhalb des Schalthohlrades und gekoppelt mit diesem in der Rastposition mindestens zwei Planetenstufen befinden, zum Beispiel die zweite und die dritte Planetenstufe, ist im Vergleich zu Ausführungen aus dem Stand der Technik eine größere Gangspreizung möglich. Es kann insbesondere eine Gangsprei- zung größer als 5 erzielt werden, so dass die Untersetzung des langsamen Gan- ges mindestens das fünffache der Untersetzung des schnellen Ganges beträgt.Since at least two planetary stages, for example the second and the third planetary stage, are located within the switching ring gear and coupled to it in the latching position, a larger gear spread is possible in comparison with embodiments of the prior art. In particular, a gear ratio 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.
Des Weiteren ist es möglich, die Untersetzung des langsamen Ganges in Abhängigkeit von der Motorauslegung so zu wählen, dass die Spindeldrehzahl der Handwerkzeugmaschine im Leerlauf kleiner ist als 100 U/min.Furthermore, it is possible to choose the reduction ratio of the slow gear depending on the engine design so that the spindle speed of the power tool at idle is less than 100 U / min.
Die Gangspreizung geht mit einer Erzielung hoher Drehmomente im langsamenThe girth spread goes with a high torque in the slow
Gang einher. Ein weiterer Vorteil ist darin zu sehen, dass die Gangspreizung auch bei einem kleinen Durchmesser der Planetenstufe zu realisieren ist und außerdem nur verhältnismäßig wenig Bauteile erforderlich sind. Außerdem erlaubt die große Gangspreizung den Einsatz kleinerer bzw. schwächerer Antriebsmoto- ren. Schließlich ist auch auf Grund der langsameren Umdrehungsgeschwindigkeiten in der kleineren Gangstufe eine bessere Kontrolle über das Arbeitsergeb- nis möglich, da der Arbeitsfortschritt zwischen der Stoppbetätigung und dem tatsächlichen Stopp der Bearbeitung reduziert ist.Gang accompanied. 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 output is also possible. This is possible because the work progress between the stop operation and the actual stop of machining is reduced.
Die Getriebeuntersetzung bzw. die Gangspreizung kann über die Auslegung der Planetenträger, insbesondere der Planetenträger zweiter und dritter Stufe einschließlich der zugeordneten Planetenräder festgelegt werden. Hierbei kommen sowohl gleichartige Planetenträger und Planetenräder in der zweiten und dritten Stufe in Betracht, was insbesondere den Vorteil hat, dass das Schalthohlrad auf der Innenseite eine einheitliche Verzahnungsgeometrie für den Eingriff sowohl mit den Planetenrädern zweiter Stufe als auch den Planetenrädern dritter Stufe aufweisen kann. Möglich ist aber auch eine unterschiedliche Auslegung der zweiten und dritten Planetenstufe, beispielsweise dergestalt, dass unterschiedliche Durchmesser vorgesehen sind, wobei in diesem Fall das Schalthohlrad zweigeteilt ist und in den beiden Abschnitten einen unterschiedlichen Innendurchmesser aufweist, um einen Eingriff mit den jeweiligen Planetenrädern zweiter und dritterThe 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. In this case, 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. However, it is also possible a different interpretation of the second and third planetary stage, for example, such that different diameters are provided, in which case the switching ring gear is divided into two and has a different inner diameter in the two sections to engage with the respective planet gears second and third
Stufe zu ermöglichen. Darüber hinaus ist es auch denkbar, dass bei gleichem oder unterschiedlichem Durchmesser verschiedene Verzahnungsgeometrien in den Planetenträgern bzw. den zugeordneten Planetenrädern vorgesehen sind und auch dementsprechend auf der Innenseite des Schalthohlrades eine jeweils korrespondierende Verzahnungsgeometrie ausgebildet ist. Über die Verzahnungsgeometrien können unterschiedliche Untersetzungsverhältnisse eingestellt werden.Level to allow. In addition, it is also conceivable that with the same or different diameter different tooth geometries in the planetary carriers or the associated planetary gears are provided and also correspondingly on the inside of the switching ring gear a corresponding toothing geometry is formed. Different gear reduction ratios can be set via the gear geometry.
In einer konstruktiv besonders einfachen Ausführung ist das hohlzylindrische Schalthohlrad auf seiner Innenseite mit einer einheitlichen Rastkontur bzw. Verzahnungsgeometrie versehen, mit der sowohl ein verrastender Eingriff mit dem benachbarten Planetenträger als auch mit den Planetenrädern zweiter und dritter Stufe realisierbar ist. In dieser Ausführung besitzt der Planetenträger der benachbarten Stufe den gleichen Außendurchmesser wie die zylindrische Einhül- lende um die Planetenräder zweiter und dritter Stufe.In a structurally particularly simple embodiment, the hollow cylindrical Schaltthohlrad 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. In this embodiment, the planetary carrier of the adjacent stage has the same outer diameter as the cylindrical envelope end about the planet wheels of the second and third stages.
Das Schalthohlrad ist axial zwischen den Gangstufen zu verstellen. Hierfür ist zweckmäßigerweise ein aus dem Gehäuse radial herausragendes Betätigungselement vorgesehen, welches zweckmäßigerweise als Schaltschieber ausgebil- det ist, beispielsweise dergestalt, dass der Schaltschieber in eine auf der Außenseite des Schalthohlrades umlaufende Nut eingreift und bei einer Bewegung des Schaltschiebers das Schalthohlrad axial zwischen den Schaltpositionen verstellt wird.The shift ring gear must be adjusted axially between the gear steps. For this purpose, a radially projecting from the housing actuating element is expediently provided, which is expediently designed as a slide switch det, 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.
In der ersten Gangstufe, in der das Schalthohlrad bezogen auf das Gehäuse sich in der Außerrastposition befindet und mit dem benachbarten Planetenträger zumIn the first gear, in which the switching ring gear relative to the housing is in the non-latching position and with the adjacent planet carrier for
Beispiel der ersten Stufe drehgekoppelt ist, besteht zweckmäßigerweise auch eine Kopplung zwischen dem Schalthohlrad und zu den Planetenrädern sowohl der zweiten als auch der dritten Stufe. Auf Grund der Verdrehsicherung zwischen dem benachbarten Planetenträger und dem Schalthohlrad dreht sich das Schalt- hohlrad relativ zum Gehäuse mit der gleichen Drehzahl wie der Planetenträger.Example of the first stage is rotationally coupled, there is expediently also a coupling between the switching ring gear and the planet gears of both the second and the third stage. Due to the rotation between the adjacent planet carrier and the switching ring gear, the Schalthalrad rotates relative to the housing at the same speed as the planet carrier.
Die zweite und die dritte Stufe sind auf Grund der Verriegelung über das Schalthohlrad stillgelegt.The second and the third stage are shut down due to the lock on the switching ring gear.
Wird dagegen das Schalthohlrad in die zweite Gangstufe versetzt, in der das Schalthohlrad gehäusefest verrastet ist, so befinden sich das Schalthohlrad und der benachbarte Planetenträger in einem Außereingriff. Zugleich können die Planetenräder zweiter und dritter Stufe an der Innenkontur des Schalthohlrades umlaufen.If, however, 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.
Um die Verrastung des Schalthohlrades realisieren zu können, ist zweckmäßigerweise ein fest mit dem Gehäuse verbundener Rastring vorgesehen. Schalthohlrad und Rastring besitzen zueinander korrespondierende Rastelemente, die in Rasteingriff gelangen, wenn das Schalthohlrad axial in Richtung auf den Rastring bewegt wird, wodurch das Schalthohlrad seine Raststellung einnimmt.In order to realize the locking of the switching ring gear, a fixedly connected to the housing locking ring is advantageously provided. Schalthohlrad 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.
Weitere Vorteile und zweckmäßige Ausführungen sind den weiteren Ansprüchen, der Figurenbeschreibung und der Zeichnung zu entnehmen, die einen Schnitt in Längsrichtung durch eine Handwerkzeugmaschine im Bereich eines schaltbaren Getriebes zeigt, welches als Planetengetriebe ausgeführt ist, wobei zum Schal- ten zwischen zwei Gangstufen ein Schalthohlrad zwischen einer gehäusefestenFurther advantages and expedient embodiments can be taken from the further claims, the description of the figures and the drawing, which shows a section in the longitudinal direction by a hand-held power tool in the region of a shiftable transmission, which is designed as a planetary gear, wherein for shifting between two gear stages a shift-ring gear between a housing-proof
Rastposition und einer Außerrastposition axial zu verstellen ist.Locking position and a non-latching position is to be adjusted axially.
Die Handwerkzeugmaschine 1 , beispielsweise ein Akkuschrauber, umfasst einen nur schematisch dargestellten elektrischen Antriebsmotor 2, dessen Motorwelle mit einem Planetengetriebe 4 in einem Getriebegehäuse 3 gekoppelt ist zum Antrieb einer im Getriebegehäuse drehbar gelagerten Spindel 6. Das Getriebege- häuse 4 kann gegebenenfalls Teil des Motorgehäuses sein. Die freie Stirnseite der Spindel 6 ist mit einem Außengewinde 7 zur Befestigung eines Bohrfutters ausgestattet, in das ein Werkzeug eingespannt werden kann.The power 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 gearbox 3 for driving a spindle 6 rotatably mounted in the gearbox housing. 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.
Das Planetengetriebe 4 ist vierstufig ausgeführt und kann zwischen zwei Gangstufen zur Änderung des Untersetzungs- und Drehmomentverhältnisses geschaltet werden. Das Planetengetriebe 4 umfasst Planetenträger 8, 9, 10 und 1 1 , die die erste, zweite, dritte bzw. vierte Stufe bilden und denen Planetenräder 12, 13, 14 und 15 entsprechender Stufen zugeordnet sind. Die Plantetenträger 8 bis 1 1 liegen koaxial zur Längsachse der Motorwelle 5 sowie der Spindel 6.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 1 1, which form the first, second, third and fourth stage and which planetary gears 12, 13, 14 and 15 associated with corresponding stages. The Plantetenträger 8 to 1 1 are coaxial with the longitudinal axis of the motor shaft 5 and the spindle. 6
Zum Schalten zwischen den beiden Gangstufen mit unterschiedlicher Umdrehungsgeschwindigkeit und unterschiedlichem Drehmomentverhältnis ist ein Schalthohlrad 16 im Gehäuse 3 axial verschieblich gelagert. Das Schalthohlrad 16 ist zwischen der dargestellten Außerrastposition und einer gehäusefestenFor switching between the two gear ratios with different rotational speed and different torque ratio, a switching ring gear 16 is mounted axially displaceably in the housing 3. The switching ring gear 16 is between the illustrated non-latching position and a housing fixed
Rastposition axial zu verstellen, in der das Schalthohlrad 16 mit einem gehäusefest angeordneten Rastring 17 in Rasteingriff steht. Die dargestellte axiale Position des Schalthohlrades 16, in der kein Rasteingriff mit dem Rastring 17 besteht, stellt die erste Gangstufe mit hoher Umdrehungsgeschwindigkeit und geringem Drehmoment der Spindel dar. In der demgegenüber axial verschobenen gehäu- seseitigen Rastposition, in der ein Rasteingriff zwischen dem Schalthohlrad 16 und dem Rastring 17 besteht, befindet sich das Getriebe in der zweiten Gangstufe mit niedriger Umdrehungsgeschwindigkeit und höherem Drehmoment.Locking position to adjust axially in which the switching ring gear 16 is in locking engagement with a locking ring 17 arranged fixed to the housing. The illustrated axial position of the Schalthohlrades 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. In contrast, axially displaced housing-side latching position in which a latching engagement between the switching ring gear 16th and the detent ring 17, the transmission is in the second speed stage with low rotational speed and higher torque.
Das Schalthohlrad 16 umgreift den Planetenträger 8 erster Stufe sowie die Planetenräder 13 und 14 zweiter bzw. dritter Stufe, die auf den entsprechenden Planetenträger 9 und 10 zweiter bzw. dritter Stufe angeordnet sind. Das Schalthohlrad 13 weist auf seiner Innenseite eine Rastkontur in Form einer Verzahnung auf, mit der das Schalthohlrad 13 in der dargestellten ersten Gangstufe drehfest mit dem Planetenträger 8 erster Stufe gekoppelt ist, so dass das Schalthohlrad 13 gegenüber dem Gehäuse 3 die gleiche Drehbewegung wie der Planetenträger 8 ausübt. Zugleich besteht eine Kopplung zu den Planetenrädern 13 und 14 zweiter bzw. dritter Stufe, die über die Verriegelung mit dem Schalthohlrad stillgelegt sind, da die Sonnenräder der Planetenträger 8 und 9 die gleiche Drehbewegung wie das Schalthohlrad 16 durchführen. Der Planetenträger 8 erster Stufe besitzt den gleichen Außendurchmesser wie eine Einhüllende um die Planetenräder 13 und 14 zweiter bzw. dritter Stufe. Dies ermöglicht es, ein hohlzylindrisch ausgebildetes Schalthohlrad 16 mit zylindrischem Innenmantel vorzusehen, der zweckmäßigerweise mit einer über die axia- Ie Länge des Schalthohlrades gleichbleibenden axialen Rastkontur bzw. Rastverzahnung versehen ist, welche mit einer entsprechenden Verzahnung am Planetenträger 8 bzw. den Planetenrädern 13 und 14 in Eingriff steht.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 Schalthohlrad 13 has on its inside a latching contour in the form of a toothing, with which the Schalthohlrad 13 is rotatably coupled in the illustrated first gear stage with the planet carrier 8 first stage, so that the switching ring gear 13 relative to the housing 3, the same rotational movement as the planet carrier 8 exercises. At the same time there is a coupling to the planetary gears 13 and 14 second and third stage, which are shut down on the lock with the switching ring gear, since the sun gears of the planet carrier 8 and 9 perform the same rotational movement as the switching ring gear 16. 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 switching ring gear 16 with a cylindrical inner jacket, which is expediently provided with a constant over the axia- Ie 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 14th engaged.
Zur Überführung in die zweite Gangstufe wird das Schalthohlrad 14 aus der dar- gestellten Position, in der das Schalthohlrad in Außerraststellung mit dem Rastring 17 steht, axial in eine Eingriffsposition mit dem Rastring verstellt, so dass sich das Schalthohlrad 16 in einer gehäusefesten Raststellung befindet. In dieser Raststellung besteht keine Drehkopplung mehr zwischen dem Planetenträger 8 erster Stufe und dem Schalthohlrad 16. Dagegen befindet sich das Schalthohlrad 16 nach wie vor ein einer Eingriffsstellung mit den Planetenrädern 13 und 14 zweiter bzw. dritter Stufe, die jedoch auf Grund der gehäusefesten Verrastung des Schalthohlrades 16 an der Innenseite des Schalthohlrades umlaufen. For transfer to the second gear stage, the switching ring gear 14 is moved from the illustrated position in which the switching ring gear is in non-latching position with the locking ring 17, axially in an engaged position with the locking ring, so that the switching ring gear 16 is in a housing-fixed locking position. In this detent position there is no more rotary coupling between the planet carrier 8 first stage and the switching ring gear 16. In contrast, 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.

Claims

Ansprüche claims
1 . Schaltbares Planetengetriebe in einer Handwerkzeugmaschine (1 ), das mehrere Planetenträger (8, 9, 10) mit zugeordneten Planetenrädern (12, 13, 14) aufweist und zwischen mindestens zwei Gangstufen zu verstellen ist, wobei die Gangstufen über ein verstellbares Schalthohlrad (16) einzulegen sind, wobei in einer ersten Gangstufe das Schalthohlrad (16) mit einem PIa- netenträger (8) drehgekoppelt und in einer zweiten Gangstufe das Schalthohlrad (16) gehäusefest verrastet ist, dadurch gekennzeichnet, dass sich axial hintereinander liegend mindestens zwei Planetenstufen (13, 14) innerhalb des Schalthohlrades (16) befinden.1 . Switchable planetary gear in a hand tool (1) having a plurality of planet carrier (8, 9, 10) with associated planetary gears (12, 13, 14) and is to be adjusted between at least two gear ratios, the gear stages via an adjustable Schalthohlrad (16) insert are in a first gear, the Schalthohlrad (16) rotatably coupled to a planet carrier (8) and in a second gear, the Schalthohlrad (16) fixed to the housing, characterized in that axially one behind the other lying at least two planetary stages (13, 14 ) are located within the switching ring gear (16).
2. Planetengetriebe nach Anspruch 1 , dadurch gekennzeichnet, dass die Innenseite des Schalthohlrades (16) mit einer Rastkontur zur Verrastung mit dem Planetenträger 1. Stufe (8) und den Planetenrädern 2. und 3. Stufe (13, 14) versehen ist.2. Planetary gear according to claim 1, characterized in that the inside of the switching ring gear (16) with a latching contour for locking with the planet carrier 1st stage (8) and the planet gears 2nd and 3rd stage (13, 14) is provided.
3. Planetengetriebe nach Anspruch 2, dadurch gekennzeichnet, dass die Rastkontur des Schalthohlrades (16) zur Verrastung mit den Planetenrädern 2. Stufe (13) identisch ist mit der Rastkontur zur Verrastung mit den Planetenrädern 3. Stufe (14).3. Planetary gear according to claim 2, characterized in that the latching contour of the switching ring gear (16) for latching with the planetary gears 2nd stage (13) is identical to the latching contour for locking with the planetary gears 3rd stage (14).
4. Planetengetriebe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Rastkontur des Schalthohlrades (16) zur Verrastung mit dem Planetenträger 1 . Stufe (8) identisch ist mit der Rastkontur zur Verrastung mit den Planetenrädern 2. oder 3. Stufe (13, 14).4. Planetary gear according to claim 2 or 3, characterized in that the latching contour of the switching ring gear (16) for latching to the planet carrier. 1 Stage (8) is identical to the locking contour for locking with the planetary gears 2nd or 3rd stage (13, 14).
5. Planetengetriebe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Planetenträger 2. und 3. Stufe (9, 10) und die zugeordneten Planetenräder (13, 14) das gleiche Untersetzungsverhältnis aufweisen.5. Planetary gear according to one of claims 1 to 4, characterized in that the planet carrier 2nd and 3rd stage (9, 10) and the associated planet gears (13, 14) have the same reduction ratio.
6. Planetengetriebe nach einem der Ansprüche 1 bis 5, dadurch gekennzeich- net, dass die Planetenträger 2. und 3. Stufe (9, 10) und die zugeordneten Planetenräder (13, 14) unterschiedliche Untersetzungsverhältnisse aufweisen.6. Planetary gear according to one of claims 1 to 5, characterized marked, that the planet carrier 2nd and 3rd stage (9, 10) and the associated Planet wheels (13, 14) have different reduction ratios.
7. Planetengetriebe nach einem der Ansprüche 1 bis 6, dadurch gekennzeich- net, dass in der ersten Gangstufe, in der das Schalthohlrad (16) mit dem benachbarten Planetenträger (8) drehgekoppelt ist, auch eine Kopplung des Schalthohlrades (16) zu den Planetenrädern 2. und 3. Stufe (13, 14) besteht.7. Planetary gear according to one of claims 1 to 6, characterized marked, that in the first gear stage, in which the switching ring gear (16) is rotationally coupled to the adjacent planet carrier (8), also a coupling of the switching ring gear (16) to the planetary gears 2nd and 3rd stage (13, 14).
8. Planetengetriebe nach einem der Ansprüche 1 bis 7, dadurch gekennzeich- net, dass in der ersten Gangstufe das Schalthohlrad (16) mit dem Planetenträger (8) 1. Stufe drehgekoppelt ist.8. Planetary gear according to one of claims 1 to 7, characterized marked, that in the first gear, the switching ring gear (16) is rotationally coupled to the planet carrier (8) 1st stage.
9. Planetengetriebe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass in der ersten Gangstufe das Schalthohlrad (16) mit dem Planeten- träger (10) 3. Stufe drehgekoppelt ist.9. planetary gear according to one of claims 1 to 7, characterized in that in the first gear stage, the switching ring gear (16) with the planet carrier (10) 3rd stage is rotationally coupled.
10. Planetengetriebe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass zur Durchführung der axialen Schaltbewegung ein aus dem Gehäuse (3) herausragender, mit dem Schalthohlrad (16) verbundener Schalt- Schieber vorgesehen ist.10. Planetary gear according to one of claims 1 to 9, characterized in that for carrying out the axial switching movement from the housing (3) outstanding, with the switching ring gear (16) connected switching slide is provided.
1 1 . Planetengetriebe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass das Schalthohlrad (16) in der gehäusefesten Raststellung mit einem Rastring (17) verrastet ist, der fest mit dem Gehäuse (3) verbunden ist.1 1. Planetary gear according to one of claims 1 to 10, characterized in that the switching ring gear (16) is latched in the housing-fixed locking position with a locking ring (17) which is fixedly connected to the housing (3).
12. Handwerkzeugmaschine mit einem Planetengetriebe (4) nach einem der Ansprüche 1 bis 1 1 . 12. Hand tool with a planetary gear (4) according to one of claims 1 to 1 1.
EP09736979.7A 2008-11-17 2009-10-21 Switchable planetary gear set in a handheld machine tool Active EP2358502B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008043795A DE102008043795A1 (en) 2008-11-17 2008-11-17 Switchable planetary gear in a hand tool
PCT/EP2009/063776 WO2010054916A1 (en) 2008-11-17 2009-10-21 Switchable planetary gear set in a handheld machine tool

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EP2358502A1 true EP2358502A1 (en) 2011-08-24
EP2358502B1 EP2358502B1 (en) 2018-05-23

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US (1) US8545363B2 (en)
EP (1) EP2358502B1 (en)
CN (1) CN102216033A (en)
DE (1) DE102008043795A1 (en)
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WO (1) WO2010054916A1 (en)

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RU2011124151A (en) 2012-12-27
EP2358502B1 (en) 2018-05-23
CN102216033A (en) 2011-10-12
US20110275471A1 (en) 2011-11-10
WO2010054916A1 (en) 2010-05-20
DE102008043795A1 (en) 2010-05-20
US8545363B2 (en) 2013-10-01

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