EP2358502B1 - Switchable planetary gear set in a handheld machine tool - Google Patents
Switchable planetary gear set in a handheld machine tool Download PDFInfo
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- 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
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- gear
- stage
- ring gear
- planetary gear
- planetary
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- 239000000969 carrier Substances 0.000 claims description 4
- 230000008878 coupling Effects 0.000 claims description 4
- 238000010168 coupling process Methods 0.000 claims description 4
- 238000005859 coupling reaction Methods 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 230000004323 axial length Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
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Classifications
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- 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
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- 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.
Description
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.
Aus der
Die
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 Gangspreizung erzielt werden kann.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 gap 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 Planetengetriebe in einer Handwerkzeugmaschine, beispielsweise in einem Akku-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.In the embodiment according to the invention is a switchable 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. 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 Gangspreizung größer als 5 erzielt werden, so dass die Untersetzung des langsamen Ganges mindestens das fünffache der Untersetzung des schnellen Ganges beträgt. 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.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 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. 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 langsamen 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 Antriebsmotoren. Schließlich ist auch auf Grund der langsameren Umdrehungsgeschwindigkeiten in der kleineren Gangstufe eine bessere Kontrolle über das Arbeitsergebnis möglich, da der Arbeitsfortschritt zwischen der Stoppbetätigung und dem tatsächlichen Stopp der Bearbeitung reduziert ist.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.
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 dritter 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.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. 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 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 Einhüllende 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 planet carrier of the adjacent stage has the same outer diameter as the cylindrical envelope around the second and third stage planetary gears.
Das Schalthohlrad ist axial zwischen den Gangstufen zu verstellen. Hierfür ist zweckmäßigerweise ein aus dem Gehäuse radial herausragendes Betätigungselement vorgesehen, welches zweckmäßigerweise als Schaltschieber ausgebildet 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 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.
In der ersten Gangstufe, in der das Schalthohlrad bezogen auf das Gehäuse sich in der Außerrastposition befindet und mit dem benachbarten Planetenträger zum 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 Schalthohlrad relativ zum Gehäuse mit der gleichen Drehzahl wie der Planetenträger. Die zweite und die dritte Stufe sind auf Grund der Verriegelung über das Schalthohlrad stillgelegt.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.
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 Schalten zwischen zwei Gangstufen ein Schalthohlrad zwischen einer gehäusefesten Rastposition und einer Außerrastposition axial zu verstellen ist.Further advantages and expedient embodiments can be found in the further claims, the description of the figures and the drawing, which shows a section in the longitudinal direction by a hand tool in the field of a switchable transmission, which is designed as a planetary gear, wherein for switching between two gear stages a switching ring gear between a housing 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 Getriebegehäuse 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 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
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 11, 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 11 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
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 gehäusefesten 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 gehäuseseitigen 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.For switching between the two gear ratios with different rotational speed and different torque ratio, a switching
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.The switching
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 axiale 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
Zur Überführung in die zweite Gangstufe wird das Schalthohlrad 14 aus der dargestellten 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, the
Claims (13)
- Shiftable planetary gear mechanism in a portable power tool (1), said gear mechanism having a plurality of planet carriers (8, 9, 10) with associated planet gears (12, 13, 14) and being intended to be adjusted between at least two gear stages, wherein the gear stages are selectable via an adjustable shifting ring gear (16), wherein, in a first gear stage, the shifting ring gear (16) is rotationally coupled to a planet carrier (8) and, in a second gear stage, the shifting ring gear (16) is latched in a manner fixed to a housing, wherein at least two planetary stages (13, 14) are located axially one after another within the shifting ring gear (16), characterized in that, in the second gear stage, the shifting ring gear (16) is rotationally coupled to the 2nd- and 3rd-stage planet gears (13, 14).
- Planetary gear mechanism according to Claim 1, characterized in that the inner side of the shifting ring gear (16) is provided with a latching contour for latching with the lst-stage planet carrier (8) and the 2nd- and 3rd-stage planet gears (13, 14).
- Planetary gear mechanism according to Claim 2, characterized in that the latching contour of the shifting ring gear (16) for latching with the 2nd-stage planet gears (13) is identical to the latching contour for latching with the 3rd-stage planet gears (14).
- Planetary gear mechanism according to Claim 2 or 3, characterized in that the latching contour of the shifting ring gear (16) for latching with the lst-stage planet carrier (8) is identical to the latching contour for latching with the 2nd- or 3rd-stage planet gears (13, 14).
- Planetary gear mechanism according to one of Claims 1 to 4, characterized in that the 2nd- and 3rd-stage planet carriers (9, 10) and the associated planet gears (13, 14) have the same reduction ratio.
- Planetary gear mechanism according to one of Claims 1 to 5, characterized in that the 2nd- and 3rd-stage planet carriers (9, 10) and the associated planet gears (13, 14) have different reduction ratios.
- Planetary gear mechanism according to one of Claims 1 to 6, characterized in that, in the first gear stage, in which the shifting ring gear (16) is rotationally coupled to the adjacent planet carrier (8), coupling of the shifting ring gear (16) to the 2nd- and 3rd-stage planet gears (13, 14) also exists.
- Planetary gear mechanism according to one of Claims 1 to 7, characterized in that, in the first gear stage, the shifting ring gear (16) is rotationally coupled to the 1st-stage planet carrier (8).
- Planetary gear mechanism according to one of Claims 1 to 7, characterized in that, in the first gear stage, the shifting ring gear (16) is rotationally coupled to the 3rd-stage planet carrier (10).
- Planetary gear mechanism according to one of Claims 1 to 9, characterized in that, in order to carry out the axial shifting movement, a shifting slide that projects out of the housing (3) and is connected to the shifting ring gear (16) is provided.
- Planetary gear mechanism according to one of Claims 1 to 10, characterized in that, in the latched position fixed to the housing, the shifting ring gear (16) is latched with a latching ring (17) which is firmly connected to the housing (3) .
- Planetary gear mechanism according to one of Claims 1 to 11, characterized in that the reduction of the slow gear is at least five times the reduction of the fast gear.
- Portable power tool having a planetary gear mechanism (4) according to one of Claims 1 to 12.
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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP2358502A1 EP2358502A1 (en) | 2011-08-24 |
| EP2358502B1 true EP2358502B1 (en) | 2018-05-23 |
Family
ID=41445408
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP09736979.7A Active EP2358502B1 (en) | 2008-11-17 | 2009-10-21 | Switchable planetary gear set in a handheld machine tool |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US8545363B2 (en) |
| EP (1) | EP2358502B1 (en) |
| CN (1) | CN102216033A (en) |
| DE (1) | DE102008043795A1 (en) |
| RU (1) | RU2011124151A (en) |
| WO (1) | WO2010054916A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009054927A1 (en) * | 2009-12-18 | 2011-06-22 | Robert Bosch GmbH, 70469 | Hand tool machine, in particular cordless hand tool machine |
| DE102009054931A1 (en) * | 2009-12-18 | 2011-06-22 | Robert Bosch GmbH, 70469 | Hand-held power tool with a torque coupling |
| DE202011110376U1 (en) * | 2011-01-03 | 2014-01-17 | Robert Bosch Gmbh | Planetary gear for a machine tool |
| CN103402707B (en) * | 2011-03-11 | 2016-06-22 | S·D·温纳德 | Hand-held drive device |
| DE102011081661B4 (en) * | 2011-08-26 | 2023-11-30 | Robert Bosch Gmbh | Switchable gearbox for a hand-held machine tool |
| 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 |
| US9908228B2 (en) | 2012-10-19 | 2018-03-06 | Milwaukee Electric Tool Corporation | Hammer drill |
| DE102015110504A1 (en) * | 2015-06-30 | 2017-01-19 | Festool Gmbh | The handheld machine tool |
| DE102017211779A1 (en) * | 2016-07-11 | 2018-01-11 | Robert Bosch Gmbh | Hand machine tool device |
| DK3496900T3 (en) * | 2016-08-08 | 2021-01-04 | Hytorc Division Unex Corp | THREAD TIGHTENING APPARATUS |
| CN109027147B (en) * | 2018-08-23 | 2023-11-17 | 浙江皇冠电动工具制造有限公司 | Transmission device of hand-held machine tool |
| US11565394B2 (en) | 2019-10-28 | 2023-01-31 | Snap-On Incorporated | Double reduction gear train |
| CN115882661A (en) * | 2021-09-29 | 2023-03-31 | 杭州九阳小家电有限公司 | Food preparation machine with stable operation |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1404063A (en) | 1972-05-24 | 1975-08-28 | Desoutter Brothers Ltd | Power driven rotary tool |
| DE3525208A1 (en) | 1984-07-16 | 1986-01-23 | Japan Strage Battery Co. Ltd., Kyoto | REDUCTION GEARBOX |
| US5339908A (en) * | 1990-10-02 | 1994-08-23 | Ryobi Limited | Power tool |
| DE19900766A1 (en) * | 1998-01-17 | 1999-07-22 | Weck Manfred Prof Dr Ing Dr In | Automotive planetary gear formed of an assembly of cogs dispensing |
| JP3872897B2 (en) * | 1998-06-17 | 2007-01-24 | 株式会社マキタ | Electric tool |
| CN2441614Y (en) * | 2000-09-26 | 2001-08-08 | 上海星特浩企业有限公司 | Three speed gear box for electric tool |
| JP4132005B2 (en) | 2000-11-17 | 2008-08-13 | 株式会社マキタ | Electric tool |
| US6431289B1 (en) * | 2001-01-23 | 2002-08-13 | Black & Decker Inc. | Multi-speed power tool transmission |
| US6676557B2 (en) * | 2001-01-23 | 2004-01-13 | Black & Decker Inc. | First stage clutch |
| US7101300B2 (en) * | 2001-01-23 | 2006-09-05 | Black & Decker Inc. | Multispeed power tool transmission |
| AUPR272101A0 (en) * | 2001-01-24 | 2001-02-22 | Bayly Design Associates Pty Ltd | Power tool |
| JP3963323B2 (en) * | 2003-02-07 | 2007-08-22 | 株式会社マキタ | Electric tool |
| US6796921B1 (en) * | 2003-05-30 | 2004-09-28 | One World Technologies Limited | Three speed rotary power tool |
| DE202004014986U1 (en) * | 2004-09-25 | 2006-02-02 | A & M Electric Tools Gmbh | Planetary gear |
| DE102004055268A1 (en) * | 2004-11-17 | 2006-05-18 | Robert Bosch Gmbh | Hand tool |
| DE102004058809A1 (en) | 2004-12-07 | 2006-06-08 | Robert Bosch Gmbh | Hand tool with a torque limiting unit |
| DE102006025538A1 (en) | 2006-06-01 | 2007-12-06 | Metabowerke Gmbh | Electric hand tool |
| CN102148548B (en) * | 2010-02-09 | 2015-05-06 | 德昌电机(深圳)有限公司 | Motor component used for medical appliance |
-
2008
- 2008-11-17 DE DE102008043795A patent/DE102008043795A1/en not_active Withdrawn
-
2009
- 2009-10-21 US US13/129,695 patent/US8545363B2/en active Active
- 2009-10-21 CN CN2009801459271A patent/CN102216033A/en active Pending
- 2009-10-21 WO PCT/EP2009/063776 patent/WO2010054916A1/en active Application Filing
- 2009-10-21 EP EP09736979.7A patent/EP2358502B1/en active Active
- 2009-10-21 RU RU2011124151/02A patent/RU2011124151A/en not_active Application Discontinuation
Non-Patent Citations (1)
| Title |
|---|
| None * |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2011124151A (en) | 2012-12-27 |
| EP2358502A1 (en) | 2011-08-24 |
| CN102216033A (en) | 2011-10-12 |
| US20110275471A1 (en) | 2011-11-10 |
| DE102008043795A1 (en) | 2010-05-20 |
| WO2010054916A1 (en) | 2010-05-20 |
| US8545363B2 (en) | 2013-10-01 |
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